Patent Publication Number: US-9897360-B2

Title: Refrigeration apparatus

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This U.S. National stage application claims priority under 35 U.S.C. § 119(a) to Japanese Patent Application No. 2013-046882, filed in Japan on Mar. 8, 2013, the entire contents of which are hereby incorporated herein by reference. 
     TECHNICAL FIELD 
     The present invention relates to a refrigeration apparatus, and particularly to a refrigeration apparatus comprising a compressor having a structure in which refrigerant compressed by a compression element is sent out of a casing after being discharged into an internal space of the casing in which an oil sump for collecting refrigerator oil is formed, a heater for heating the refrigerator oil collected in the oil sump, and a controller for controlling the heater. 
     BACKGROUND ART 
     Conventionally, refrigeration apparatuses have included air-conditioning apparatuses used to cool and heat room interiors of buildings or the like by performing a vapor-compression refrigeration cycle. 
     In this type of refrigeration apparatus, when the temperature of the refrigerator oil is low while the refrigeration apparatus has stopped and the pressure of refrigerant in the compressor is under a certain condition, the amount of refrigerant dissolved in the refrigerator oil in the compressor increases. When there is an overlap of conditions such as the refrigeration apparatus being out of operation for a long period of time and/or a change in the refrigerant temperature (or the outdoor temperature), it causes a phenomenon known as stagnation, and a large amount of refrigerant dissolves in the refrigerator oil inside the compressor. When the refrigerant stagnates in the refrigerator oil and the concentration of the refrigerator oil decreases, there is a risk that the viscosity of the refrigerator oil will decrease and the compressor will not be sufficiently lubricated. 
     In conventional practice, to prevent refrigerant stagnation in the compressor, a countermeasure has been employed in which a heater is attached to the outer periphery of the compressor, and the refrigerator oil inside the compressor is heated while the refrigeration apparatus has stopped to ensure that the refrigerant does not stagnate. There are also cases in which the refrigerator oil inside the compressor is heated by open-phase current conduction to the motor. 
     However, when current is conducted to the heater in order to heat the refrigerator oil inside the compressor while the refrigeration apparatus has stopped, a certain amount of power is consumed as standby power, and the amount of power consumed by the refrigeration apparatus is increased. 
     SUMMARY 
     To reduce such standby power of the refrigeration apparatus, for example, Japanese Laid-open Patent Application No. 2001-73952 and Japanese Patent Publication No. 4111246 disclose the specifics of controlling a heater while a compressor is stopped (i.e, while a refrigeration apparatus is stopped) on the basis of refrigerant temperature and/or outside air temperature. Japanese Laid-open Patent Application No. H9-170826 discloses the specifics of controlling a heater while a refrigeration apparatus is stopped on the basis of the concentration of refrigerator oil inside a compressor. 
     With heater control such as Japanese Laid-open Patent Application No. 2001-73952, Japanese Patent Publication No. 4111246 and Japanese Laid-open Patent Application No. H9-170826, standby power can be reduced more than in cases in which refrigerator oil inside a compressor is constantly heated while a refrigeration apparatus is stopped. 
     However, under the condition of a low outside air temperature, even if the concentration (viscosity) of refrigerator oil while the refrigeration apparatus is stopped can be maintained by heater control such as Japanese Laid-open Patent Application No. 2001-73952, Japanese Patent Publication No. 4111246 and Japanese Laid-open Patent Application No. H9-170826, because the temperature of refrigerator oil inside the compressor and/or the temperature of the compressor casing are low, the occurrence of in-dome condensation is prominent, in which refrigerant that has been discharged into the internal space of the casing from a compression element for compressing refrigerant is condensed in the internal space before being sent out of the casing when the refrigeration apparatus starts operating. In-dome condensation occurs when the compressor is structured such that refrigerant compressed by the compression element is sent out of the casing after being discharged into the internal space of the casing in which an oil sump for collecting refrigerator oil is formed, and is a phenomenon in which refrigerant discharged from the compression element into the internal space of the casing at the start of operation of the air-conditioning apparatus is cooled to a state of saturation in the channel leading out of the casing, and the refrigerant condenses on the surface of refrigerator oil collected in the oil sump and/or on the surrounding wall surface of the casing. When the liquid refrigerant produced by such in-dome condensation then dissolves in the refrigerator oil collected in the oil sump, there is a risk that when the refrigeration apparatus starts operating, the concentration (viscosity) of the refrigerator oil will decrease, the compressor will not be sufficiently lubricated, and the compressor will be unreliable. 
     As a solution to such in-dome condensation, Japanese Laid-open Patent Application No. 2000-130865 discloses the specifics of providing a wall-surface heating passage for channeling refrigerant discharged from a compressor to a wall surface of a compressor casing, and channeling the refrigerant discharged from the compressor to the wall-surface heating passage to heat the wall surfaces of the casing when the compressor is started up (i.e. when the refrigeration apparatus starts operating). However, because the refrigerant discharged from the compressor at the start of operation of the air-conditioning apparatus is low in temperature and near a state of saturation, providing the wall-surface heating passage still does not yield heating capacity sufficient to heat the wall surface of the casing at the start of operation of the air-conditioning apparatus, and it is difficult to suppress decreases in refrigerator oil concentration (viscosity) caused by in-dome condensation. 
     An object of the present invention is to provide a refrigeration apparatus that can minimize the standby power of the refrigeration apparatus as well as improve the reliability of the compressor while taking into account the decrease in refrigerator oil concentration (viscosity) caused by in-dome condensation. 
     A refrigeration apparatus according to a first aspect comprises a compressor having a structure in which refrigerant compressed by a compression element is sent out of a casing after being discharged into an internal space of the casing in which an oil sump for collecting refrigerator oil is formed, a heater for heating the refrigerator oil collected in the oil sump, and a controller for controlling the heater. In a compressor having a single-stage compression element, the phrase “a structure in which refrigerant compressed by a compression element is sent out of a casing after being discharged into an internal space of the casing in which an oil sump for collecting refrigerator oil is formed” herein means a structure referred to as a “high-pressure dome” in which refrigerant compressed by a compression element is sent out of a casing after being discharged into an internal space of the casing in which an oil sump is formed. In a compressor having a multiple-stage compression element, this phrase means an “intermediate-pressure dome” or a “high-pressure dome” in which refrigerant compressed by an intermediate-stage and/or a final-stage compression element is sent out of a casing after being discharged into an internal space of the casing in which an oil sump is formed. The term “heater” means a crank case heater for heating refrigerator oil collected in the oil sump from the external periphery of the casing, and/or a motor for driving the compression element when open-phase current conduction is used to heat the refrigerator oil collected in the oil sump. The controller controls the heater while the refrigeration apparatus is stopped so that the temperature of the refrigerator oil collected in the oil sump reaches a first oil temperature target value for keeping a condensation amount of the refrigerant equal to or less than an allowable condensation amount at which the concentration or viscosity of the refrigerator oil needed to lubricate the compressor can be maintained, the refrigerant condensation amount being caused by in-dome condensation at the start of operation of the refrigeration apparatus. The term “in-dome condensation” herein means a phenomenon in which the refrigerant discharged from the compression element into the internal space at the start of operation of the refrigeration apparatus is condensed in the internal space before being sent out of the casing. 
     While the refrigeration apparatus is stopped, the refrigerator oil collected in the oil sump is heated herein so that the temperature of the refrigerator oil reaches a first oil temperature target value accounting for the decrease in the refrigerator oil concentration (viscosity) caused by in-dome condensation at the start of operation of the refrigeration apparatus, whereby the refrigerator oil concentration (viscosity) needed to lubricate the compressor can be maintained at the start of operation of the refrigeration apparatus even if in-dome condensation occurs. The power consumption of the heater, and consequently the standby power of the refrigeration apparatus, can be reduced by limiting the extent of the heating of the refrigerator oil collected in the oil sump to the first oil temperature target value. 
     It is thereby possible herein to minimize the standby power of the refrigeration apparatus as well as improve the reliability of the compressor while taking into account the decrease in the concentration (viscosity) of the refrigerator oil caused by in-dome condensation. 
     A refrigeration apparatus according to a second aspect is the refrigeration apparatus according to the first aspect, wherein the controller decides the allowable condensation amount on the basis of the amount of the refrigerator oil collected in the oil sump while the refrigeration apparatus is stopped, and decides the first oil temperature target value so that the refrigerant condensation amount caused by the in-dome condensation is equal to or less than the allowable condensation amount. 
     The extent of the decrease in the concentration (viscosity) of refrigerator oil caused by in-dome condensation is determined on the basis of the amount of refrigerator oil collected in the oil sump while the refrigeration apparatus is stopped, and the refrigerant condensation amount caused by in-dome condensation. 
     In view of this, as described above, the allowable condensation amount is decided on the basis of the amount of refrigerator oil collected in the oil sump while the refrigeration apparatus is stopped, and the first oil temperature target value is decided so that the refrigerant condensation amount caused by in-dome condensation is equal to or less than the allowable condensation amount. 
     An appropriate first oil temperature target value can thereby be obtained herein. 
     A refrigeration apparatus according to a third aspect is the refrigeration apparatus according to the first or second aspect, wherein while the refrigeration apparatus is stopped, the controller decides a second oil temperature target value at which the concentration or viscosity of the refrigerator oil collected in the oil sump in a state of solution equilibrium can be maintained at a concentration or viscosity of the refrigerator oil needed to lubricate the compressor, and controls the heater so that the temperature of the refrigerator oil collected in the oil sump reaches the higher value of the first oil temperature target value and the second oil temperature target value. The term “a state of solution equilibrium” herein means a state in which the refrigerant in the refrigerator oil collected in the oil sump reaches saturation solubility at the pressure of the refrigerant in the internal space of the casing. 
     While the refrigeration apparatus is stopped, the refrigerator oil collected in the oil sump is heated until the temperature of the refrigerator oil reaches the oil temperature target value (i.e., the higher value of the first oil temperature target value and the second oil temperature target value) which takes into account the decrease in refrigerator oil concentration (viscosity) while the refrigeration apparatus is stopped as well as the decrease in refrigerator oil concentration (viscosity) caused by in-dome condensation at the start of operation of the refrigeration apparatus, whereby the concentration or viscosity of the refrigerator oil needed to lubricate the compressor can be maintained throughout the stopping of the refrigeration apparatus and the start of operation of the refrigeration apparatus. 
     It is thereby possible to minimize the standby power of the refrigeration apparatus as well as improve the reliability of the compressor while taking into account the decrease in refrigerator oil concentration (viscosity) caused by in-dome condensation and the decrease in refrigerator oil concentration (viscosity) while the refrigeration apparatus is stopped. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a schematic structural diagram of an air-conditioning apparatus as an embodiment of a refrigeration apparatus according to the present invention; 
         FIG. 2  is a schematic longitudinal cross-sectional view of a compressor; 
         FIG. 3  is a control block diagram of the air-conditioning apparatus; 
         FIG. 4  is a graph showing the change over time in the concentration (viscosity) of the refrigerator oil collected in the oil sump at the start of operation of the air-conditioning apparatus (at startup of the compressor); 
         FIG. 5  is a flowchart of heating control (deciding the first oil temperature target value) of the refrigerator oil inside the compressor, accounting for in-dome condensation; 
         FIG. 6  is a flowchart of heating control (heater control while the air-conditioning apparatus is stopped) of the refrigerator oil inside the compressor, accounting for in-dome condensation; 
         FIG. 7  is a graph showing the change over time in the concentration (viscosity) of the refrigerator oil collected in the oil sump during heating control of the refrigerator oil inside the compressor, accounting for in-dome condensation; 
         FIG. 8  is a flowchart of heating control (deciding a first oil temperature target value and a second oil temperature target value) of the refrigerator oil inside the compressor in Modification 1; and 
         FIG. 9  is a flowchart of heating control (heater control while the air-conditioning apparatus is stopped) of the refrigerator oil inside the compressor in Modification 1. 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     An embodiment and modification of a refrigeration apparatus according to the present invention is described below on the basis of the drawings. The specific configuration of the refrigeration apparatus according to the present invention is not limited to the following embodiment and modification, and can be changed within a range that does not deviate from the scope of the invention. 
     (1) Basic Configuration of Refrigeration Apparatus 
       FIG. 1  is a schematic structural diagram of an air-conditioning apparatus  1  as an embodiment of the refrigeration apparatus according to the present invention. The air-conditioning apparatus  1  is an apparatus used to cool and heat the room interior of a building or the like by performing a vapor-compression refrigeration cycle. The air-conditioning apparatus  1  has primarily one outdoor unit  2 , a plurality (two in this case) of indoor units  5 ,  6 , and a liquid refrigerant communication pipe  7  and gas refrigerant communication pipe  8  connecting the outdoor unit  2  and the indoor units  5 ,  6 . Specifically, a vapor-compression refrigerant circuit  10  of the air-conditioning apparatus  1  is configured by connecting the outdoor unit  2 , the indoor units  5 ,  6 , the liquid refrigerant communication pipe  7 , and the gas refrigerant communication pipe  8 . The number of indoor units  5 ,  6  is not limited to two, and may be one, three, or more. 
     &lt;Indoor Unit&gt; 
     The indoor units  5 ,  6  are installed by being embedded in or suspended from ceilings in rooms of a building or the like, or by being mounted on wall surfaces in rooms, or by some other manner. The indoor units  5 ,  6  are connected to the outdoor unit  2  via the liquid refrigerant communication pipe  7  and the gas refrigerant communication pipe  8 , constituting part of the refrigerant circuit  10 . 
     Next, the configuration of the indoor units  5 ,  6  shall be described. Because the indoor unit  5  and the indoor unit  6  have the same configuration, only the configuration of the indoor unit  5  is described herein, the configuration of the indoor unit  6  is denoted by symbols in the sixties instead of the symbols in the fifties that represent the components of the indoor unit  5 , and the components of the indoor unit  6  are not described. 
     The indoor unit  5  has primarily an indoor expansion valve  51  and an indoor heat exchanger  52 . 
     The indoor expansion valve  51  is a device for adjusting the pressure, flow rate, and other characteristics of the refrigerant flowing through the indoor unit  5 . The indoor expansion valve  51  is connected at one end to the liquid side of the indoor heat exchanger  52 , and connected at the other end to the liquid refrigerant communication pipe  7 . An electric expansion valve is used herein as the indoor expansion valve  51 . 
     The indoor heat exchanger  52  is a heat exchanger that functions as an evaporator of refrigerant to cool indoor air during an air-cooling operation, and functions as a condenser of refrigerant to heat indoor air during an air-warming operation. The indoor heat exchanger  52  is connected on the liquid side to the indoor expansion valve  51 , and connected on the gas side to the gas refrigerant communication pipe  8 . 
     The indoor unit  5  has an indoor fan  53  for drawing indoor air into the indoor unit  5 , and supplying the air as supply air into the room after the air has undergone heat exchange with the refrigerant in the indoor heat exchanger  52 . A centrifugal fan, multiblade fan, or the like driven by an indoor fan motor  53   a  is used herein as the indoor fan  53 . 
     The indoor unit  5  has an indoor-side controller  54  for controlling the actions of the components constituting the indoor unit  5 . The indoor-side controller  54 , which has a computer, memory, and the like for controlling the indoor unit  5 , is configured to be able to exchange control signals and the like with a remote controller (not shown) for separately operating the indoor unit  5 , and to be able to exchange control signals and the like with the outdoor unit  2  via a transmission line  9   a.    
     &lt;Outdoor Unit&gt; 
     The outdoor unit  2  is installed on the outside of a building or the like. The outdoor unit  2  is connected to the indoor units  5 ,  6  via the liquid refrigerant communication pipe  7  and the gas refrigerant communication pipe  8 , constituting part of the refrigerant circuit  10 . 
     Next, the configuration of the outdoor unit  2  shall be described. The outdoor unit  2  has primarily a compressor  21 , a switching mechanism  22 , an outdoor heat exchanger  23 , and an outdoor expansion valve  24 . 
     The compressor  21  is a device for compressing low-pressure refrigerant in the refrigeration cycle to a high pressure. The compressor  21  has a hermetically sealed structure in which a positive displacement compression element  21   b  accommodated inside a casing  21   a  is rotatably driven by a compressor motor  21   c . A first gas refrigerant pipe  25   a  is connected to an intake side of the compressor  21 , and a second gas refrigerant pipe  25   b  is connected to a discharge side. The first gas refrigerant pipe  25   a  is a refrigerant pipe connecting the intake side of the compressor  21  and a first port  22   a  of the switching mechanism  22 . The second gas refrigerant pipe  25   b  is a refrigerant pipe connecting the discharge side of the compressor  21  and a second port  22   b  of the switching mechanism  22 . The compressor  21  is provided with a configuration for controlling the heating of the refrigerator oil inside the compressor  21  while the air-conditioning apparatus  1  is stopped, but the detailed structure of the compressor  21  including the configuration for controlling the heating of the refrigerator oil shall be described hereinafter. 
     The switching mechanism  22  is a mechanism for switching the direction of refrigerant flow in the refrigerant circuit  10 . During the air-cooling operation, the switching mechanism  22  performs a switch that causes the outdoor heat exchanger  23  to function as a condenser of refrigerant compressed in the compressor  21 , and causes the indoor heat exchangers  52 ,  62  to function as evaporators of refrigerant condensed in the outdoor heat exchanger  23 . Specifically, during the air-cooling operation, the switching mechanism  22  performs a switch that interconnects the second port  22   b  and a third port  22   c , and interconnects the first port  22   a  and a fourth port  22   d . The discharge side of the compressor  21  (the second gas refrigerant pipe  25   b  herein) and the gas side of the outdoor heat exchanger  23  (a third gas refrigerant pipe  25   c  herein) are thereby connected (refer to the solid lines of the switching mechanism  22  in  FIG. 1 ). Moreover, the intake side of the compressor  21  (the first gas refrigerant pipe  25   a  herein) and the gas refrigerant communication pipe  8  side (a fourth gas refrigerant pipe  25   d  herein) are connected (refer to the solid lines of the switching mechanism  22  in  FIG. 1 ). During the air-warming operation, the switching mechanism  22  performs a switch that causes the outdoor heat exchanger  23  to function as an evaporator of refrigerant condensed in the indoor heat exchangers  52 ,  62 , and causes the indoor heat exchangers  52 ,  62  to function as condensers of refrigerant compressed in the compressor  21 . Specifically, during the air-warming operation, the switching mechanism  22  performs a switch that interconnects the second port  22   b  and the fourth port  22   d , and interconnects the first port  22   a  and the third port  22   c . The discharge side of the compressor  21  (the second gas refrigerant pipe  25   b  herein) and the gas refrigerant communication pipe  8  side (the fourth gas refrigerant pipe  25   d  herein) are thereby connected (refer to the dashed lines of the switching mechanism  22  in  FIG. 1 ). Moreover, the intake side of the compressor  21  (the first gas refrigerant pipe  25   a  herein) and the gas side of the outdoor heat exchanger  23  (the third gas refrigerant pipe  25   c  herein) are connected (refer to the dashed lines of the switching mechanism  22  in  FIG. 1 ). The third gas refrigerant pipe  25   c  is a refrigerant pipe connecting the third port  22   c  of the switching mechanism  22  and the gas side of the outdoor heat exchanger  23 . The fourth gas refrigerant pipe  25   d  is a refrigerant pipe connecting the fourth port  22   d  of the switching mechanism  22  and the gas refrigerant communication pipe  8  side. The switching mechanism  22  herein is a four-way switching valve. The configuration of the switching mechanism  22  herein is not limited to a four-way switching valve, and may be a configuration in which, e.g., a plurality of electromagnetic valves or the like are connected so as to fulfill the switching functions described above. 
     The outdoor heat exchanger  23  is a heat exchanger that functions as a condenser of refrigerant during the air-cooling operation, and functions as an evaporator of refrigerant during the air-warming operation. The liquid side of the outdoor heat exchanger  23  is connected to a liquid refrigerant pipe  25   e , and the gas side is connected to the third gas refrigerant pipe  25   c . The liquid refrigerant pipe  25   e  is a refrigerant pipe connecting the liquid side of the outdoor heat exchanger  23  and the liquid refrigerant communication pipe  7  side. 
     The outdoor expansion valve  24  is a device for adjusting the pressure, flow rate, and/or other characteristics of the refrigerant flowing through the outdoor unit  2 . The outdoor expansion valve  24  is provided to the liquid refrigerant pipe  25   e . An electric expansion valve is used herein as the outdoor expansion valve  24 . 
     The outdoor unit  2  has an outdoor fan  26  for drawing outdoor air into the outdoor unit  2 , and discharging the air out of the outdoor unit  2  after the air has undergone heat exchange with the refrigerant in the outdoor heat exchanger  23 . An axial flow fan or the like driven by an outdoor fan motor  26   a  is used herein as the outdoor fan  26 . 
     The outdoor unit  2  has an outdoor-side controller  27  for controlling the actions of the components constituting the outdoor unit  2 . The outdoor-side controller  27 , which has a microcomputer, memory, and the like for controlling the outdoor unit  2 , is configured to be able to exchange control signals and the like with the indoor units  5 ,  6  (i.e. the indoor-side controllers  54 ,  64 ) via the transmission line  9   a . The outdoor unit  2  is also provided with various sensors used for purposes such as controlling the heating of refrigerator oil inside the compressor  21  while the air-conditioning apparatus  1  is stopped, but these sensors shall be described hereinafter. 
     &lt;Refrigerant Communication Pipes&gt; 
     The refrigerant communication pipes  7 ,  8  are refrigerant pipes that are constructed on site when the air-conditioning apparatus  1  is installed in a building or another location of installation, and pipes having various lengths and/or diameters are used in accordance with the location of installation, the combination of outdoor units and indoor units, and other conditions of installation. 
     As described above, the refrigerant circuit  10  of the air-conditioning apparatus  1  is configured by connecting the outdoor unit  2 , the indoor units  5 ,  6 , and the refrigerant communication pipes  7 ,  8 . 
     &lt;Controller&gt; 
     The air-conditioning apparatus  1  is designed so that control of the devices of the outdoor unit  2  and the indoor unit  4  can be performed by a controller  9  configured from the indoor-side controllers  54 ,  64  and the outdoor-side controller  27 . Specifically, a controller  9  for controlling the operation of the air-conditioning apparatus  1  is configured by the indoor-side controllers  54 ,  64 , the outdoor-side controller  27 , and the transmission line  9   a  connecting the controllers  27 ,  54 ,  64 . By switching the switching mechanism  22  to the state shown by the solid lines in  FIG. 1  and circulating refrigerant sequentially through the compressor  21 , the outdoor heat exchanger  23 , the outdoor expansion valve  24 , the indoor expansion valves  51 ,  61 , and the indoor heat exchangers  52 ,  62 , the air-cooling operation can be performed. By switching the switching mechanism  22  to the state shown by the dashed lines in  FIG. 1  and circulating refrigerant sequentially through the compressor  21 , the indoor heat exchangers  52 ,  62 , the indoor expansion valves  51 ,  61 , the outdoor expansion valve  24 , and the outdoor heat exchanger  23 , the air-warming operation can be performed. 
     (2) Detailed Structure of Compressor and Configuration for Controlling Heating of Refrigerator Oil Inside Compressor 
     Next,  FIGS. 1 to 3  are used to describe the detailed structure of the compressor  21  and the configuration for controlling the heating of the refrigerator oil inside the compressor  21 .  FIG. 2  herein is a schematic longitudinal cross-sectional view of the compressor  21 .  FIG. 3  is a control block diagram of the air-conditioning apparatus  1 . 
     &lt;Basic Structure of Compressor&gt; 
     The compressor  21  has a casing  21   a  in the shape of an oblong cylinder. The casing  21   a  is a pressure container configured from a casing main body  31   a , an upper wall part  31   b , and a bottom wall part  31   c , the interior of which is hollow. The casing main body  31   a  is a cylindrical barrel part having a vertically extending axis. The upper wall part  31   b  is welded airtight and integrally bonded to the top end of the casing main body  31   a , and is a bowl-shaped portion having a convex surface protruding upward. The bottom wall part  31   c  is welded airtight and integrally bonded to the bottom end of the casing main body  31   a , and is a bowl-shaped portion having a convex surface protruding downward. 
     The interior of the casing  21   a  accommodates the compression element  21   b  for compressing refrigerant, and the compressor motor  21   c  disposed below the compression element  21   b . The compression element  21   b  and the compressor motor  21   c  are linked by a drive shaft  32  disposed so as to extend vertically inside the casing  21   a.    
     The compression element  21   b  has a housing  33 , a fixed scroll  34  disposed in close contact with the top of the housing  33 , and a movable scroll  35  meshed with the fixed scroll  34 . The housing  33  is press-fitted to the casing main body  31   a  in the external peripheral surface through the entire circumferential direction. Specifically, the casing main body  31   a  and the housing  33  are in close airtight contact through their entire peripheries. The inside of the casing  21   a  is divided to a lower high-pressure space  36   a  of the housing  33  and an upper low-pressure space  36   b  of the housing  33 . Formed in the housing  33  are a housing concave part  33   a  indented in the middle of the upper surface, and a bearing part  33   b  extending downward from the middle of the lower surface. A bearing hole  33   c  passing through the lower-end surface of the bearing part  33   b  and the bottom surface of the housing concave part  33   a  is formed in the housing  33 , and the drive shaft  32  is rotatably fitted into the bearing hole  33   c  via a bearing  33   d.    
     In the upper wall part  31   b  of the casing  21   a , an intake pipe  37  is fitted in an airtight manner for allowing the refrigerant of the refrigerant circuit  10  (the first gas refrigerant pipe  25   a  herein) to flow from the exterior of the casing  21   a  to the interior and guiding the refrigerant to the compression element  21   b . A discharge pipe  38  for discharging the refrigerant inside the compressor  21  to the outside of the casing  21   a  (the second gas refrigerant pipe  25   b  of the refrigerant circuit  10  herein) is fitted in an airtight matter in the casing main body  31   a . The intake pipe  37  vertically passes through the low-pressure space  36   b , and the inner end is fitted in the fixed scroll  34  of the compression element  21   b.    
     The lower-end surface of the fixed scroll  34  is in close contact with the upper-end surface of the housing  33 . The fixed scroll  34  is fastenably secured to the housing  33  by a bolt (not shown). Sealing the upper-end surface of the housing  33  and the lower-end surface of the fixed scroll  34  ensures that refrigerant of the high-pressure space  36   a  will not leak to the low-pressure space  36   b.    
     The fixed scroll  34  has primarily an end plate  34   a , and a spiraling (involute) lap  34   b  formed on the lower surface of the end plate  34   a . The movable scroll  35  has primarily an end plate  35   a , and a spiraling (involute) lap  35   b  formed on the upper surface of the end plate  35   a . The upper end of the drive shaft  32  is fitted into the movable scroll  35 , and the movable scroll is supported in the housing  33  so as to be able to revolve within the housing  33  without being spun by the rotation of the drive shaft  32 . The lap  34   b  of the fixed scroll  34  and the lap  35   b  of the movable scroll  35  mesh with each other, whereby a compression room  39  is formed between the fixed scroll  34  and the movable scroll  35 . The compression room  39  is configured so as to compress refrigerant by constricting toward the center of the volume between the laps  34   b  and  35   b  along with the revolution of the movable scroll  35 . 
     A discharge port  34   c  interconnected with the compression room  39  and an enlarged concave part  34   d  continuing into the discharge port  34   c  are formed in the end plate  34   a  of the fixed scroll  34 . The fixed scroll  34  is a port for discharging refrigerant that has been compressed by the compression room  39 , and is formed so as to extend vertically in the middle of the end plate  34   a  of the fixed scroll  34 . The enlarged concave part  34   d  is configured from a horizontally widened concave part indented in the upper surface of the end plate  34   a . A chamber cover  40  is fastenably secured so as to close the enlarged concave part  34   d  in the upper surface of the fixed scroll  34 . Covering the enlarged concave part  34   d  with the chamber cover  40  forms a chamber room  41  into which refrigerant flows through the discharge port  34   c  from the compression room  39 , the chamber room being positioned on the upper side of the discharge port  34   c . Specifically, the chamber room  41  is divided from the low-pressure space  36   b  by the chamber cover  40  positioned on the upper side of the discharge port  34   c . The fixed scroll  34  and the chamber cover  40  are sealed by being in close contact via packing (not shown). Also formed in the fixed scroll  34  is an intake port  34   e  for interconnecting the upper surface of the fixed scroll  34  and the compression room  39  and fitting in the intake pipe  37 . 
     A communication flow channel  42  throughout between the fixed scroll  34  and the housing  33  is formed in the compression element  21   b . The communication flow channel  42  is a flow channel for allowing refrigerant to flow out from the chamber room  41  to the high-pressure space  36   a , and is configured from the interconnecting of a scroll-side flow channel  34   f  formed as a recess in the fixed scroll  34 , and a housing-side flow channel  33   e  formed as a recess in the housing  33 . The upper end of the communication flow channel  42 , i.e., the upper end of the scroll-side flow channel  34   f  opens into the enlarged concave part  34   d , and the lower end of the communication flow channel  42 , i.e., the lower end of the housing-side flow channel  33   e  opens into the lower-end surface of the housing  33 . A discharge port  33   f  for allowing the refrigerant in the communication flow channel  42  to flow out to the high-pressure space  36   a  is configured by the lower-end opening of the housing-side flow channel  33   e.    
     The compressor motor  21   c  is disposed in the high-pressure space  36   a , and is configured from a motor having an annular stator  43  secured to a wall surface inside the casing  21   a , and a rotor  44  configured to be free to rotate on the inner peripheral side of the stator  43 . Radially between the stator  43  and the rotor  44 , an annular gap is formed so as to extend vertically, and this gap constitutes an air gap flow channel  45 . A winding coil is fitted on the stator  43 , and above and below the stator  43  are coil ends  43   a.    
     In the external peripheral surface of the stator  43 , core cut parts  43   b  are formed as recesses in a plurality of locations in predetermined gaps in the circumferential direction and from the upper-end surface to the lower-end surface of the stator  43 . Due to the core cut parts  43   b  being formed in the external peripheral surface of the stator  43 , a plurality of vertically extending motor-cooling flow channels  46  are formed radially between the casing main body  31   a  and the stator  43 . 
     The rotor  44  is drivably linked to the movable scroll  35  of the compression element  21   b  via the drive shaft  32  disposed in the axial center of the casing main body  31   a  so as to extend vertically. 
     In the space below the compressor motor  21   c , an oil sump  36   c  for collecting refrigerator oil in the bottom is formed and a pump  47  is set up. The pump  47  is secured to the casing main body  31   a  and attached to the lower end of the drive shaft  32 , and is configured so as to pump up the refrigerator oil collected in the oil sump  36   c . An oil supply channel  32   a  is formed inside the drive shaft  32 , and the refrigerator oil pumped up by the pump  47  is supplied through the oil supply channel  32   a  to sliding components of the compression element  21   b  and the like. 
     A gas guide  48  is provided in the high-pressure space  36   a  so as to join the outlet of the communication flow channel  42  (i.e. the discharge port  33   f ) and part of the motor-cooling flow channels  46  together. The gas guide  48  is a plate-shaped member secured in close contact with the inner wall surface of the casing main body  31   a . The space between the gas guide  48  and the inner wall surface of the casing main body  31   a  is open in the upper and lower ends. A large part of the refrigerant compressed by the compression element  21   b  and flowing out into the high-pressure space  36   a  from the outlet of the communication flow channel  42  (i.e. the discharge port  33   f ) is thereby sent through the space between the gas guide  48  and the inner wall surface of the casing main body  31   a , to the motor-cooling flow channels  46 . The refrigerant sent to the motor-cooling flow channels  46  heads downward while passing through the motor-cooling flow channels  46 , and then arrives in proximity to the oil level of the oil sump  36   c . The refrigerant that has arrived in proximity to the oil level of the oil sump  36   c  passes through the space vertically between the lower end of the compressor motor  21   c  and the oil level of the oil sump  36   c , and the refrigerant is then send to the rest of the motor-cooling flow channels  46  (i.e., the motor-cooling flow channels  46  not joined with the lower end of the gas guide  48 ) and the air gap flow channel  45 . The refrigerant sent to the rest of the motor-cooling flow channels  46  and the air gap flow channel heads upward while passing through the rest of the motor-cooling flow channels  46  and the air gap flow channel  45 , and then arrives at the discharge pipe  38 . Thus, the high-pressure space  36   a  forms a discharge flow channel  49  (herein composed of the gas guide  48 , the motor-cooling flow channels  46 , and the air gap flow channel  45 ) for sending the refrigerant compressed by the compression element  21   b  out of the casing  21   a  after the refrigerant has passed through the space vertically between the lower end of the compressor motor  21   c  and the oil level of the oil sump  36   c.    
     Thus, the compressor  21  has a structure (referred to as a “high-pressure dome type) structure) in which refrigerant compressed by the single-stage compression element  21   b  is sent out of the casing  21   a  after being discharged into an internal space (the high-pressure space  36   a  herein) of the compressor  21  in which the oil sump  36   c  for collecting refrigerator oil is formed. In the compressor  21 , when the compressor motor  21   c  is driven by current conduction during either the air-cooling operation or the air-warming operation, the rotor  44  rotates relative to the stator  43 , whereby the drive shaft  32  rotates. When the drive shaft  32  rotates, the movable scroll  35  only revolves without spinning relative to the fixed scroll  34 . Consequently, low-pressure refrigerant is thereby drawn through the intake pipe  37  into the compression room  39  from the external-peripheral-edge side of the compression room  39 . The refrigerant drawn into the compression room  39  is compressed as the volume of the compression room  39  changes. The refrigerant compressed in the compression room  39  reaches high pressure and flows from the middle of the compression room  39 , through the discharge port  34   c , into the chamber room  41 . The high-pressure refrigerant that has flowed into the chamber room  41  flows from the chamber room  41  into the communication flow channel  42 , through the scroll-side flow channel  34   f  and the housing-side flow channel  33   e , and out from the discharge port  33   f  to the high-pressure space  36   a . The high-pressure refrigerant that has flowed out to the high-pressure space  36   a  passes through the discharge flow channel  49  including the space vertically between the lower end of the compressor motor  21   c  and the oil level of the oil sump  36   c , arriving at the discharge pipe  38  to be discharged out of the casing  21   a . The high-pressure refrigerant discharged out of the casing  21   a  circulates through the refrigerant circuit  10 , and then becomes low-pressure refrigerant which is drawn back into the compressor  21  through the intake pipe  37 . 
     &lt;Configuration for Controlling Heating of Refrigerator Oil Inside Compressor&gt; 
     The compressor  21  is provided with a crank case heater  28  as a heater for heating the refrigerator oil collected in the oil sump  36   c  from the external periphery of the casing  21   a . The crank case heater  28  herein is disposed so as to be wrapped around the bottom wall part  31   c  of the casing  21   a . The crank case heater  28  is not limited to being disposed on the bottom wall part  31   c , and may, for example, be disposed on the lower end part of the casing main body  31   a  or another location. The crank case heater  28 , similar to other devices, is designed to be controlled by the controller  9 . 
     Various sensors, used for purposes such as controlling the heating of refrigerator oil in the compressor  21 , are provided to the air-conditioning apparatus  1 . Specifically, the first gas refrigerant pipe  25   a  is provided with an intake pressure sensor  29   a  for detecting the pressure of refrigerant in the intake side of the compressor  21 , and an intake temperature sensor  29   b  for detecting the temperature of refrigerant in the intake side of the compressor  21 . The second gas refrigerant pipe  25   b  is provided with a discharge pressure sensor  29   c  for detecting the pressure of refrigerant in the discharge side of the compressor  21 , and a discharge temperature sensor  29   d  for detecting the temperature of refrigerant in the discharge side of the compressor  21 . The outdoor unit  2  is also provided with an outside air temperature sensor  29   e  for detecting the temperature of outdoor air (outside air temperature). Furthermore, the compressor  21  is provided with an oil temperature sensor  29   f  for detecting the temperature of the refrigerator oil collected in the oil sump  36   c , and an oil level sensor  29   g  for detecting the oil-level height of the refrigerator oil collected in the oil sump  36   c . These sensors  29   a  to  29   g  are connected to the controller  9  and are designed to be used for purposes such as controlling the heating of the refrigerator oil inside the compressor  21 . The temperature of the refrigerator oil collected in the oil sump  36   c  may also be estimated from the detection values of other sensors rather than being detected by the oil temperature sensor  29   f.    
     Thus, the air-conditioning apparatus  1  has a compressor  21  having a structure in which refrigerant compressed by the compression element  21   b  is sent out of the casing  21   a  after being discharged to the internal space (the high-pressure space  36   a  herein) of the casing  21   a  in which the oil sump  36   c  for collecting refrigerator oil is formed, a heater (the crank case heater  28  herein) for heating the refrigerator oil collected in the oil sump  36   c , and a controller  9  for controlling the crank case heater  28 . 
     (3) Heating Control of Refrigerator Oil Inside Compressor, Accounting for in-Dome Condensation 
     In the air-conditioning apparatus  1 , similar to conventional practice, the controller  9  is designed to use the crank case heater  28  to heat the refrigerator oil inside the compressor  21  (more specifically, inside the oil sump  36   c ) while the air-conditioning apparatus  1  is stopped (i.e. while the compressor  21  is stopped), in order to prevent refrigerant stagnation in the compressor  21 . At this time, when the refrigerator oil inside the oil sump  36   c  is constantly heated while the air-conditioning apparatus  1  is stopped, the standby power of the air-conditioning apparatus  1  increases. Therefore, a conceivable solution for reducing the standby power of the air-conditioning apparatus  1  is that a temperature Toil of the refrigerator oil collected in the oil sump  36   c  be detected by the oil temperature sensor  29   f , and the crank case heater  28  be controlled so that the temperature Toil of the refrigerator oil reaches a predetermined oil temperature target value. The concentration (viscosity) of the refrigerator oil inside the oil sump  36   c  while the air-conditioning apparatus  1  is stopped can thereby be maintained. 
     However, in-dome condensation occurs because the temperature Toil of the refrigerator oil inside the oil sump  36   c  and/or the temperature of the casing  21   a  of the compressor  21  are low in conditions in which the outside air temperature is low, in-dome condensation being when the refrigerant discharged from the compression element  21   b  for compressing refrigerant into the internal space (the high-pressure space  36   a  herein) of the casing  21   a  at the start of operation of the air-conditioning apparatus  1  (i.e. at startup of the compressor  21 ) is condensed in the high-pressure space  36   a  before being sent out of the casing  21   a . As used herein, the phrase in-dome condensation is a phenomenon that occurs when the structure employed for the compressor  21 , such as the high-pressure dome type structure employed herein, is one in which the refrigerant compressed by the compression element  21   b  is sent out of the casing  21   a  after being discharged into the high-pressure space  36   a  of the casing  21   a  in which the oil sump  36   c  for collecting refrigerator oil is formed. In in-dome condensation, the refrigerant discharged from the compression element  21   b  into the high-pressure space  36   a  of the casing  21   a  at the start of operation of the air-conditioning apparatus  1  is cooled to a state of saturation in the channel (the discharge flow channel  49  herein) leading out of the casing  21   a . and the refrigerant condenses on the surface of refrigerator oil collected in the oil sump  36   c  and/or on the surrounding wall surface of the casing  21   a  (refer to the flow of refrigerant inside the compressor  21  in  FIG. 2 ). When the liquid refrigerant produced by such in-dome condensation then dissolves in the refrigerator oil collected in the oil sump  36   c , there are cases in which at the start of operation of the air-conditioning apparatus  1 , the concentration (viscosity) of the refrigerator oil falls below an allowable oil concentration yaoil (allowable oil viscosity μaoil), which is the concentration (viscosity) of refrigerator oil needed to lubricate the compressor  21 , such as the case of the change over time in concentration (viscosity) of the refrigerator oil collected in the oil sump  36   c  at the start of operation of the air-conditioning apparatus  1  (at startup of the compressor  21 ) in  FIG. 4 . When such low-concentration (low-viscosity) refrigerator oil is supplied to the sliding components of the compressor  21  by the pump  47  and the oil supply channel  32   a  (see  FIG. 2 ), there is a risk that the compressor  21  will not be sufficiently lubricated and the compressor  21  will be unreliable. 
     A conceivable solution to such in-dome condensation is, similar to Patent Document 4, to provide a wall-surface heating passage for channeling refrigerant discharged from a compressor  21  to a wall surface of the casing  21   a  of the compressor  21 , and to channel the refrigerant discharged from the compressor  21  to the wall-surface heating passage to heat the wall surface of the casing  21   a  at the start of operation of the air-conditioning apparatus  1 . However, because the refrigerant discharged from the compressor  21  at the start of operation of the air-conditioning apparatus  1  is low in temperature and near a state of saturation, providing the wall-surface heating passage still does not yield heating capacity sufficient to heat the wall surface of the casing  21   a  at the start of operation of the air-conditioning apparatus  1 , and it is difficult to suppress decreases of refrigerator oil concentration (viscosity) caused by in-dome condensation. 
     Thus, a requirement with the air-conditioning apparatus  1  is to make it possible to minimize standby power as well as improve the reliability of the compressor  21  while taking into account the decrease in the concentration (viscosity) of refrigerator oil caused by in-dome condensation at startup of the air-conditioning apparatus  1 . 
     In view of this, the controller  9  herein is designed to control the crank case heater  28  so that while the air-conditioning apparatus  1  is stopped (while the compressor  21  is stopped), the temperature Toil of the refrigerator oil collected in the oil sump  36   c  reaches a first oil temperature target value Ts 1 oil for keeping the refrigerant condensation amount Mref, which is caused by in-dome condensation at the start of operation of the air-conditioning apparatus  1 , equal to or less than an allowable condensation amount Mcref at which the concentration or viscosity of refrigerator oil needed to lubricate the compressor  21  (i.e. the allowable oil concentration yaoil or the allowable oil viscosity μaoil) can be maintained. 
     Next,  FIGS. 1 to 7  are used to describe heating control of the refrigerator oil inside the compressor  21 , accounting for in-dome condensation.  FIG. 5  herein is a flowchart of heating control (deciding the first oil temperature target value Ts 1 oil) of the refrigerator oil inside the compressor  21 , accounting for in-dome condensation.  FIG. 6  is a flowchart of heating control (heater control while the air-conditioning apparatus  1  is stopped) of the refrigerator oil inside the compressor  21 , accounting for in-dome condensation.  FIG. 7  is a graph showing the change over time in the concentration (viscosity) of the refrigerator oil collected in the oil sump  36   c  during heating control of the refrigerator oil inside the compressor  21 , accounting for in-dome condensation. 
     &lt;Step ST 1 : Calculation of Refrigerator Oil Amount Moil&gt; 
     When the air-conditioning apparatus  1  (the compressor  21 ) stops, the controller  9  calculates the refrigerator oil amount Moil collected in the oil sump  36   c  while the air-conditioning apparatus  1  is stopped in step ST 1 . The reason the refrigerator oil amount Moil is calculated is because the extent of the decrease in refrigerator oil concentration (viscosity) caused by in-dome condensation is determined on the basis of the refrigerator oil amount Moil collected in the oil sump  36   c  while the air-conditioning apparatus  1  is stopped, and the refrigerant condensation amount Mref caused by in-dome condensation. The refrigerator oil amount Moil is calculated from the following formula 1-1.
 
 M oil= V oil×ρ× y oil  formula 1-1
 
The term Voil represents the volume of refrigerator oil in the oil sump  36   c  while the air-conditioning apparatus  1  is stopped, and this oil volume is calculated on the basis of the oil-level height Loil of refrigerator oil while the air-conditioning apparatus  1  is stopped in the oil sump  36   c  as detected by the oil level sensor  29   g , and a volume calculation formula obtained from the dimension relationship of the oil sump  36   c . The symbol ρ represents the mixed density of refrigerant and refrigerator oil in the oil sump  36   c  while the air-conditioning apparatus  1  is stopped. Furthermore, the term yoil represents the concentration of refrigerator oil in the oil sump  36   c  while the air-conditioning apparatus  1  is stopped, and this oil concentration is calculated on the basis of the temperature Toil of the refrigerator oil, the refrigerant pressure Pbd in the high-pressure space  36   a  while the air-conditioning apparatus  1  is stopped in the oil sump  36   c  as detected by the intake pressure sensor  29   a  (or the refrigerant saturation temperature Tbd in the high-pressure space  36   a  obtained by converting the refrigerant pressure Pbd to the saturation temperature), and a saturation solubility relational expression of refrigerant relative to refrigerator oil.
 
     The oil level sensor  29   g  is provided to the compressor  21  herein and is used in the calculation of the refrigerator oil amount Moil, but the method of calculating the refrigerator oil amount Moil is not limited to this option. For example, the refrigerator oil amount Moil may be calculated from the change over time in the refrigerator oil temperature Toil while the air-conditioning apparatus  1  is stopped and/or the operation history of the air-conditioning apparatus  1  until stopping, or the refrigerator oil amount Moil may be a fixed amount determined by referencing standards and other factors. The refrigerant pressure detected by the intake pressure sensor  29   a  is used as the refrigerant pressure Pbd in the high-pressure space  36   a  while the air-conditioning apparatus  1  (the compressor  21 ) is stopped, but a pressure sensor that directly detects the refrigerant pressure in the high-pressure space  36   a  may be provided to the compressor  21 . 
     &lt;Step ST 2 : Calculation of Allowable Condensation Amount Mcref&gt; 
     Next, in step ST 2 , the controller  9  calculates the allowable condensation amount Mcref at which the concentration or viscosity of refrigerator oil needed to lubricate the compressor  21  (i.e. the allowable oil concentration yaoil or the allowable oil viscosity μaoil) can be maintained, on the basis of the refrigerator oil amount Moil collected in the oil sump  36   c  while the air-conditioning apparatus  1  is stopped, as obtained in step ST 1 . Specifically, the allowable condensation amount Mcref is calculated from the following formula 2-1.
 
 Mc ref= Ma ref− Mb ref  formula 2-1
 
     The term Maref herein represents the amount of refrigerant present in the oil sump  36   c , relative to the refrigerator oil amount Moil obtained in step ST 1 , when the refrigerant is dissolved so as to yield the allowable oil concentration yaoil (or the allowable oil viscosity μaoil), and this refrigerant amount is calculated from the following formula 2-2.
 
 Ma ref= M oil×(1− ya oil)/ ya oil  formula 2-2
 
     The term Mbref represents the amount of refrigerant present in the oil sump  36   c , relative to the refrigerator oil amount Moil obtained in step ST 1 , at the point in time immediately before the start of operation of the air-conditioning apparatus  1  (i.e. immediately before startup of the compressor  21 ), and this refrigerant amount is calculated from the following formula 2-3.
 
 Mb ref= M oil×(1− yb oil)/ yb oil  formula 2-3
 
     The term yboil represents the refrigerator oil concentration in the oil sump  36   c  at the point in time immediately before the start of operation of the air-conditioning apparatus  1 , and this oil concentration is calculated on the basis of the refrigerator oil temperature Toil in the oil sump  36   c  at the point in time immediately before the start of operation of the air-conditioning apparatus  1 , and the saturation solubility relational expression of refrigerant relative to refrigerator oil. Because heater control while the air-conditioning apparatus  1  is stopped in the hereinafter-described steps ST 7  to ST 10  causes the refrigerator oil temperature Toil in the oil sump  36   c  while the air-conditioning apparatus  1  is stopped to reach the first oil temperature target value Ts 1 oil as an oil temperature target value Tsoil, the refrigerator oil concentration yboil in the oil sump  36   c  at the point in time immediately before the start of operation of the air-conditioning apparatus  1  is the refrigerator oil concentration at the first oil temperature target value Ts 1 oil. The first oil temperature target value Ts 1 oil is a value updated in the processes of step ST 2  and the hereinafter-described steps ST 3  to ST 6 , until the refrigerant condensation amount Mref caused by in-dome condensation at the start of operation of the air-conditioning apparatus  1  coincides with the allowable condensation amount Mcref. In the process of the first step ST 2  after the air-conditioning apparatus  1  has stopped, the outdoor air temperature Ta detected by the outside air temperature sensor  29   e  is set as the initial value of the first oil temperature target value Ts 1 oil. However, the initial value of the first oil temperature target value Ts 1 oil is not limited to the outdoor air temperature Ta. 
     &lt;Step ST 3 : Calculation of Refrigerant Condensation Amount Mref Caused by in-Dome Condensation&gt; 
     Next, in step ST 3 , the controller  9  predictively calculates the refrigerant condensation amount Mref caused by in-dome condensation at the start of operation of the air-conditioning apparatus  1  (at startup of the compressor  21 ). The refrigerant condensation amount Mref is caused by the refrigerant, which is discharged from the compression element  21   b  into the high-pressure space  36   a  at the start of operation of the air-conditioning apparatus  1 , being cooled and condensed when passing through the discharge flow channel  49 . Therefore, a heat radiation model of the refrigerant at the oil level of the oil sump  36   c  is prepared in the form of a transient calculation model, and heat radiation amounts ΔQref for each passage of a predetermined time duration Δt are predictively calculated for the refrigerant at the oil level of the oil sump  36   c  at the start of operation of the air-conditioning apparatus  1 . The amounts ΔMref of refrigerant condensed due to heat radiation are calculated from the predictively calculated heat radiation amounts ΔQref, and the refrigerant condensation amount Mref predicted to be caused by in-dome condensation is calculated by adding up these refrigerant condensation amounts ΔMref. Specifically, the refrigerant condensation amount Mref predicted to be caused by in-dome condensation is calculated from the following formula 3-1.
 
 M ref=ΣΔ M ref  formula 3-1
 
     The symbols ΔMref represent a predicted condensation amount of refrigerant with each passage of a predetermined time duration Δt at the start of operation of the air-conditioning apparatus  1 , and the symbol Σ means that the predicted refrigerant condensation amounts ΔMref of each predetermined time duration Δt are added up. 
     The predicted condensation amount ΔMref of refrigerant of each predetermined time duration Δt is calculated from the following formula 3-2.
 
Δ M ref= G ref×(1− x outref)  formula 3-2
 
     The symbols Gref herein represent the predicted flow rate of refrigerant discharged from the compression element  21   b  into the high-pressure space  36   a  at the start of operation of the air-conditioning apparatus  1 , and this flow rate is calculated from the following formula 3-3.
 
 G ref= Wc×Nc×ρs×kc   formula 3-3
 
     The term Wc represents the displacement of the compression element  21   b , and this displacement is a set value of the compressor  21 . The term Nc represents the rotational speed of the compressor  21  at the start of operation of the air-conditioning apparatus  1 , and this rotational speed is a value determined from a rotational speed setting planned for the start of operation of the air-conditioning apparatus  1 . The symbols ρs represent the density of refrigerant drawn into the compression element  21   b  at the start of operation of the air-conditioning apparatus  1 , and this density herein is calculated on the basis of the refrigerant pressure Pcs detected by the intake pressure sensor  29   a , the refrigerant temperature Tcs detected by the intake temperature sensor  29   b , and a refrigerant pressure-temperature-density relational expression. The term kc represents volumetric efficiency. The term xoutref represents the dryness of the refrigerant that has been discharged from the compression element  21   b  into the high-pressure space  36   a  and has radiated heat at the oil level of the oil sump  36   c  at the start of operation of the air-conditioning apparatus  1 . The enthalpy ioutref of the refrigerant, which has been discharged from the compression element  21   b  into the high-pressure space  36   a  and has radiated heat at the oil level of the oil sump  36   c  at the start of operation of the air-conditioning apparatus  1 , is calculated from the following formula 3-4, and the refrigerant dryness is calculated on the basis of the refrigerant enthalpy ioutref obtained by calculation, the refrigerant pressure Pcd detected by the discharge pressure sensor  29   c  of the air-conditioning apparatus  1 , and a refrigerant pressure-enthalpy-dryness relational equation.
 
 i outref= i inref−Δ Q ref/ G ref  formula 3-4
 
     The term iinref represents the enthalpy of the refrigerant before being discharged from the compression element  21   b  into the high-pressure space  36   a  and radiating heat at the oil level of the oil sump  36   c  at the start of operation of the air-conditioning apparatus  1 , and this enthalpy is calculated on the basis of a refrigerant pressure-temperature-enthalpy relational expression, substituting the refrigerant pressure Pcd detected by the discharge pressure sensor  29   c  of the air-conditioning apparatus  1 , and the refrigerant temperature Tinref detected by the discharge temperature sensor  29   d . The enthalyph iinref may also be estimated using a calculation model for estimating the heat loss in the channel leading from the compression element  21   b  to the oil level of the oil sump  36   c , from the refrigerant intake temperature Tcs. When data of the previous start of operation of the air-conditioning apparatus  1  is available, the enthalpy iinref can be predicted from the refrigerant discharge temperature. 
     The predicted heat radiation amount ΔQref of refrigerant with each predetermined time duration Δt is calculated from the following formulas 3-5 to 3-9.
 
Δ Q ref= k ref× h ref× A ref×( T inref− Ts 1oil)  formula 3-5
 
 h ref= Nu ×λref/ D ref  formula 3-6
 
 Nu=C×Re^α×Pr^β   formula 3-7
 
 Re=D ref× G ref×ρref/μref  formula 3-8
 
 Pr=Cp ref×μref/λref  formula 3-9
 
     The term kref represents a correction coefficient of the heat-transfer coefficient href between refrigerant and refrigerator oil at the oil level of the oil sump  36   c , and this correction coefficient is set appropriately when the dryness xinref is less than 1 (a wet state) of refrigerant yet to be discharged from the compression element  21   b  into the high-pressure space  36   a  and yet to radiate heat at the oil level of the oil sump  36   c  at the start of operation of the air-conditioning apparatus  1 . The refrigerant dryness xinref is calculated on the basis of the refrigerant enthalpy iinref, the refrigerant pressure Pcd detected by the discharge pressure sensor  29   c  of the air-conditioning apparatus  1 , and a refrigerant pressure-enthalpy-dryness relational expression. The heat-transfer coefficient href is calculated by the relational expressions 3-6 to 3-9 of the Nusselt number Nu. Reynolds number Re, and Prandtl number Pr, often used in conventional practice to calculate heat-transfer coefficients. The symbols λref, ρref, μref, and Cpref represent the heat-transfer coefficient, density, viscosity, and constant pressure specific heat of the refrigerant at the oil level of the oil sump  36   c , and these values are calculated on the basis of the refrigerant pressure Pcd detected by the discharge pressure sensor  29   c  of the air-conditioning apparatus  1 , the refrigerant temperature Tcd detected by the discharge temperature sensor  29   d , a refrigerant pressure-temperature-heat-transfer coefficient relational expression, a refrigerant pressure-temperature-density relational expression, a refrigerant pressure-temperature-viscosity relational expression, and a refrigerant pressure-temperature-constant pressure specific heat relational expression. The term Dref represents characteristic length, the symbols C, α, and β represent relational expression coefficients of the Nusselt number Nu, the Reynolds number Re, and the Prandtl number Pr, and these values are determined experimentally. The term Aref represents the surface area of the oil level of the oil sump  36   c.    
     Thus, in step ST 3 , the predicted condensation amount Mref of refrigerant is calculated using the above formulas 3-1 to 3-9. In the process of the first step ST 3  following the stopping of the air-conditioning apparatus  1 , the predicted condensation amount Mref of refrigerant is calculated using the initial value of the first oil temperature target value Ts 1 oil (the outdoor air temperature Ta herein). 
     A predicted condensation amount Mref of the refrigerant caused by in-dome condensation at the start of operation of the air-conditioning apparatus  1  (at startup of the compressor  21 ) is herein obtained by a transient calculation of a heat radiation model of the refrigerant at the oil level of the oil sump  36   c , but the predicted condensation amount is not limited to being obtained in this manner. For example, the predicted condensation amount Mref of the refrigerant may be obtained from actual operation data at the previous start of operation of the air-conditioning apparatus  1 , or the predicted condensation amount Mref of the refrigerant may be obtained assuming typical startup operation control of the air-conditioning apparatus  1 . The first oil temperature target value Ts 1 oil may also be prepared by calculation in advance in order to reduce the amount of calculation as much as possible. For example, a relational expression and/or table of refrigerant predicted condensation amounts Mref—first oil temperature target values Ts 1 oil may be prepared, and the first oil temperature target value Ts 1 oil may be determined from the obtained refrigerant predicted condensation amount Mref. 
     &lt;Steps ST 4  to ST 6 : Determination of First Oil Temperature Target Value Ts 1 oil&gt; 
     Next, in step ST 4 , the controller  9  assesses whether or not the allowable condensation amount Mcref decided in step ST 2  and the predicted condensation amount Mref decided in step ST 3  coincide. In the process of the first step ST 4  after the stopping of the air-conditioning apparatus  1 , it is assessed whether or not the predicted condensation amount Mref coincides with the allowable condensation amount Mcref calculated using the initial value of the first oil temperature target value Ts 1 oil (the outdoor air temperature Ta herein). 
     When the allowable condensation amount Mcref and the predicted condensation amount Mref do not coincide, the sequence transitions to the process of step ST 5 , and the first oil temperature target value Ts 1 oil is updated. When the predicted condensation amount Mref herein is greater than the allowable condensation amount Mcref, the first oil temperature target value Ts 1 oil is updated so as to be higher, and when the predicted condensation amount Mref is less than the allowable condensation amount Mcref, the first oil temperature target value Ts 1 oil is updated so as to be lower. 
     Returning to steps ST 2  and ST 3 , the allowable condensation amount Mcref and the predicted condensation amount Mref are calculated again using the updated first oil temperature target value Ts 1 oil, and it is again assessed in step ST 4  whether or not the predicted condensation amount Mref coincides with the allowable condensation amount Mcref. 
     After these processes of steps ST 2  to ST 5  are repeated until the predicted condensation amount Mref coincides with the allowable condensation amount Mcref, the sequence transitions to step ST 6 . A first oil temperature target value Ts 1 oil is thereby decided at which the refrigerant condensation amount Mref, caused by in-dome condensation at the start of operation of the air-conditioning apparatus  1 , can be kept equal to or less than the allowable condensation amount Mcref at which the concentration or viscosity of refrigerator oil needed to lubricate the compressor  21  (i.e., the allowable oil concentration yaoil or allowable oil viscosity μaoil) can be maintained. 
     &lt;Steps ST 7  to ST 10 : Heater Control while Air-Conditioning Apparatus  1  is Stopped&gt; 
     Next, in step ST 7 , the controller  9  sets the first oil temperature target value Ts 1 oil obtained in step ST 6  as the oil temperature target value Tsoil for heater control while the air-conditioning apparatus  1  (the compressor  21 ) is stopped. 
     In step ST 8 , the controller  9  compares the temperature Toil of refrigerator oil in the oil sump  36   c  and the oil temperature target value Tsoil, and when the refrigerator oil temperature Toil has not reached the oil temperature target value Tsoil, the sequence transitions to the process of step ST 9  and the crank case heater  28  is turned on to heat the refrigerator oil. When the refrigerator oil temperature Toil in the oil sump  36   c  and the oil temperature target value Tsoil are compared and the refrigerator oil temperature Toil has reached the oil temperature target value Tsoil, the sequence transitions to the process of step ST 10  and the crank case heater  28  is turned off to suspend the heating of the refrigerator oil. Performing these processes of steps ST 8  to ST 10  ensures that the refrigerator oil temperature Toil in the oil sump  36   c  will reach the oil temperature target value Tsoil (the first oil temperature target value Ts 1 oil herein) while the air-conditioning apparatus  1  is stopped. 
     By controlling the heating of refrigerator oil inside the compressor  21  while accounting for in-dome condensation as described above, it is possible herein to heat the refrigerator oil while the air-conditioning apparatus  1  (the compressor  21 ) is stopped until the temperature Toil of refrigerator oil collected in the oil sump  36   c  reaches the oil temperature target value Tsoil (the first oil temperature target value Ts 1 oil herein) accounting for the decrease in concentration (viscosity) of the refrigerator oil caused by in-dome condensation at the start of operation of the air-conditioning apparatus  1  (refer to the state of the air-conditioning apparatus  1  while stopped in  FIG. 7 ). It is thereby possible to maintain the concentration (viscosity) of refrigerator oil needed to lubricate the compressor at the start of operation of the air-conditioning apparatus  1  even if in-dome condensation occurs (refer to the state of the air-conditioning apparatus  1  at the start of operation in  FIG. 7 ). Limiting the extent of heating the refrigerator oil collected in the oil sump  36   c  to the oil temperature target value Tsoil (the first oil temperature target value Ts 1 oil herein) makes it possible to reduce the power consumption of the crank case heater  28 , and consequently the standby power of the air-conditioning apparatus  1 , more so than when the refrigerator oil is constantly heated while the air-conditioning apparatus  1  is stopped (refer to the state of the air-conditioning apparatus  1  while stopped in  FIG. 7 ). 
     It is thereby possible hereinto minimize the standby power of the air-conditioning apparatus  1  as well as improve the reliability of the compressor  21  while taking into account the decrease in refrigerator oil concentration (viscosity) caused by in-dome condensation. 
     Moreover, the allowable condensation amount Mcref is decided on the basis of the amount Moil of refrigerator oil collected in the oil sump  36   c  while the air-conditioning apparatus  1  is stopped, after which the first oil temperature target value Ts 1 oil is decided so that the refrigerant condensation amount Mref caused by in-dome condensation will be equal to or less than the allowable condensation amount Mcref, and an appropriate first oil temperature target value Ts 1 oil can therefore be obtained. 
     (4) Modification 1 
     In the heating control of the refrigerator oil inside the compressor  21  in the above embodiment, the first oil temperature target value Ts 1 oil, which accounts for the decrease in refrigerator oil concentration (viscosity) caused by in-dome condensation at the start of operation of the air-conditioning apparatus  1  (at startup of the compressor  21 ), is designated as the oil temperature target value Tsoil. Heating control of the refrigerator oil inside the compressor  21  herein is performed with consideration given to the decrease in refrigerator oil concentration (viscosity) while the air-conditioning apparatus  1  (the compressor  21 ) is stopped, in addition to in-dome condensation. 
     Specifically, in steps ST 11  and ST 12 , the controller  9  herein decides a second oil temperature target value Ts 2 oil that accounts for the refrigerator oil concentration (viscosity) while the air-conditioning apparatus  1  is stopped, in parallel with the process of deciding the first oil temperature target value Ts 1 oil in steps ST 1  to ST 6 , as shown in  FIG. 8 . 
     The second oil temperature target value Ts 2 oil is an oil temperature target value at which the concentration or viscosity of refrigerator oil collected in the oil sump  36   c  in a state of solution equilibrium can be maintained at the concentration or viscosity of refrigerator oil needed to lubricate the compressor  21  while the refrigeration apparatus  1  is stopped. The term “state of solution equilibrium” means a state in which at the refrigerant pressure Pbd in the high-pressure space  36   a  which is the internal space of the casing  21   a , the refrigerant in the refrigerator oil collected in the oil sump  36   c  has reached a saturation solubility. Therefore, the second oil temperature target value Ts 2 oil can be calculated from, e.g., a polynomial of the refrigerant saturation temperature Tbd of the high-pressure space  36   a  obtained by converting the refrigerant pressure Pbd to a saturation temperature.
 
 Ts 2oil= C 1× Tbd^ 2+ C 2× Tbd+C 3+ Tbd  
 
     In step ST 7 , the controller  9  compares the second oil temperature target value Ts 2 oil decided in steps ST 11  and ST 12  and the first oil temperature target value Ts 1 oil decided in steps ST 1  to ST 6 , sets the higher of the two as the oil temperature target value Tsoil, and performs the heater control of steps ST 8  to ST 10 , as shown in  FIG. 9 . 
     Thus, while the air-conditioning apparatus  1  is stopped, the refrigerator oil is heated until the temperature Toil of refrigerator oil collected in the oil sump  36   c  reaches the oil temperature target value Tsoil (i.e. the higher value of the first oil temperature target value Ts 1 oil and the second oil temperature target value Ts 2 oil), which accounts for the decrease in refrigerator oil concentration (viscosity) while the air-conditioning apparatus  1  is stopped as well as the decrease in refrigerator oil concentration (viscosity) caused by in-dome condensation at the start of operation of the air-conditioning apparatus  1 . The refrigerator oil concentration or viscosity needed to lubricate the compressor  21  can thereby be maintained throughout the stopping of the air-conditioning apparatus  1  and the start of operation of the air-conditioning apparatus  1 . 
     It is thereby possible to minimize the standby power of the air-conditioning apparatus  1  as well as improve the reliability of the compressor  21 , while taking into account the decrease in refrigerator oil concentration (viscosity) caused by in-dome condensation and the decrease in refrigerator oil concentration (viscosity) while the air-conditioning apparatus  1  is stopped. 
     (5) Other Modifications 
     &lt;A&gt; 
     In the above embodiment and Modification 1, the crank case heater  28  is used as the heater for heating the refrigerator oil, but the heater is not limited to this option. For example, the refrigerator oil may be heated by open-phase current conduction to the compressor motor  21   c , instead of being heated by the crank case heater  28 . The heater may also be disposed inside the casing  21   a , rather than being disposed as wrapped around the external periphery of the casing  21   a.    
     &lt;B&gt; 
     In the above embodiment and Modification 1, the compressor  21  having a high-pressure dome structure with a single-stage compression element  21   b  is employed as a compressor having a structure in which refrigerant compressed by the compression element is sent out of the casing after being discharged into the internal space of the casing in which the oil sump for collecting refrigerator oil is formed, but the compressor is not limited to this option. For example, when a compressor having a multiple-stage compression element is employed, the compressor may have an intermediate-pressure dome structure or a high-pressure dome structure in which the refrigerant compressed by an intermediate-stage or final-stage compression element is sent out of the casing after being discharged into the internal space of the casing. 
     The compression element constituting the compressor is not limited to a scroll-type element, and may be a rotary or other type of compression element. 
     &lt;C&gt; 
     In the above embodiment and Modification 1, the present invention was applied to an air-conditioning apparatus  1  having a refrigerant circuit  10  capable of switching between an air-cooling operation and an air-warming operation, but the invention is not limited to such an apparatus. For example, the present invention may be applied to a refrigeration apparatus having another refrigerant circuit dedicated for a single purpose such as air-cooling. 
     INDUSTRIAL APPLICABILITY 
     The present invention is widely applicable to refrigeration apparatuses that comprise a compressor having a structure in which refrigerant compressed by a compression element is sent out of a casing after being discharged into an internal space of the casing in which an oil sump for collecting refrigerator oil is formed, a heater for heating the refrigerator oil collected in the oil sump, and a controller for controlling the heater.