Patent Application
20120321497
The present invention relates to a positive displacement expander capable of recovering, as power, fluid energy during an expansion process and a refrigeration cycle apparatus including the positive displacement expander.
There is known a traditional refrigeration cycle apparatus that includes a compressor having an orbiting scroll which is driven by a motor and is configured to compress a refrigerant, a radiator which dissipates heat of the refrigerant compressed by the compressor, an expander having a rolling piston which is configured to decompress the refrigerant that has passed through the radiator, and an evaporator which allows the refrigerant decompressed by the expander to evaporate. Such a refrigeration cycle apparatus has been known which has a communicating path connecting an intermediate position of the expansion process in an expansion chamber (a section partitioned by the rolling piston in the expansion chamber) to an outlet position (outlet port side) such that when a pressure in the expansion chamber excessively drops, fluid on the outlet side is returned to the expansion chamber in order to prevent overexpansion and thus prevents a drop in power recovery efficiency (refer to, for example, Patent Literature 1).
In addition, a refrigerating and air-conditioning apparatus is known that includes a scroll expander, which expands and decompresses a refrigerant cooled by a radiator to recover power, and a scroll auxiliary compressor, which is driven by power recovered by the expander and compresses the refrigerant in an auxiliary manner. With the auxiliary compression of the refrigerant by the auxiliary compressor, load on a main compressor is reduced, the electric power necessary for a drive motor of the main compressor is reduced, and, thus, efficiency of the refrigeration cycle apparatus is increased (refer to, for example, Patent Literature 2).
Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2004-190559 (FIGS. 4 and 15)
Patent Literature 2: Japanese Unexamined Patent Application Publication No. 2009-109158 (FIG. 1)
As disclosed in Patent Literature 2, when a drive shaft of the expander is not connected to the motor or a generator and the expander is activated only using the fluid energy of the refrigerant, depending on a stop position of the orbiting scroll constituting the expander, there has been a possibility of startup failure of the expander due to lack of driving force when reactivating the refrigeration cycle apparatus.
Stopping of the orbiting scroll (or the rolling piston) of the expander at a predetermined position can be controlled by determining the position in which the refrigerant in the expansion chamber is released to a low-pressure side. For this, a communicating path bypassing the refrigerant from an intermediate portion of the expansion chamber to the low-pressure side is needed.
As regards the communicating path bypassing the refrigerant from an intermediate portion of the expansion chamber to the low-pressure side, the communicating path of Patent Literature 1 connecting the intermediate position of the expansion process in the expansion chamber (a section partitioned by the rolling piston in the expansion chamber) to an outlet position (outlet port side) can be used so that, for example, the refrigerant in the expansion chamber can be discharged to the outlet side. However, in a power recovery expander driven by fluid energy generated during decompression of the refrigerant, as described above, when the refrigerant in the expansion chamber is discharged by way of connecting the communicating path communicating with the low-pressure side to one of the sections partitioned by the orbiting scroll (or the rolling piston) in the expansion chamber, there has existed a risk of the rolling piston or the orbiting scroll stopping in the intermediate position of the expansion process in the expansion chamber and sufficient driving force cannot be obtained in the expander when reactivating the refrigeration cycle apparatus again.
A technical challenge of the present invention is to achieve control of the stop position of the orbiting scroll or the rolling piston of the expander and to obtain sufficient driving force in the expander when resuming.
The present invention provides a positive displacement expander equipped with an expansion mechanism in which power is generated using fluid energy generated while a high-pressure fluid, supplied to a plurality of expansion chambers partitioned by an orbiting scroll or an rolling piston, is being expanded and decompressed, the positive displacement expander including a communicating path that allows each of the expansion chambers to communicate with an expander discharge side; and an opening and closing device disposed in the communicating path, in which when supply of the high-pressure fluid is stopped, the opening and closing device is opened by the time when high and low pressures between each expansion chamber and the expander discharge side are equalized, thus stopping the orbiting scroll or the rolling piston at a predetermined position.
In the positive displacement expander according to the present invention, when the supply of the high-pressure fluid is stopped, a stop position of the orbiting scroll or the rolling piston can be controlled so that the expander can be easily resumed. Advantageously, this prevents such startup failure that the orbiting scroll or the rolling piston does not orbit when resuming.
Referring to
This air-conditioning apparatus uses carbon dioxide as the refrigerant. Carbon dioxide has an ozone depletion potential of zero and a lower global warming potential as compared with traditional fluorocarbon refrigerants.
In Embodiment 1, the main compressor 1, the auxiliary compressor 2, a first four-way valve 3 and a second four-way valve 6 which are refrigerant flow switching devices, the outdoor heat exchanger 4, a bypass valve 5, a pre-expansion valve 7, the expander 8, and an accumulator 9 are housed in an outdoor unit 101. An expansion valve 31 and the indoor heat exchanger 32 are housed in an indoor unit 102. A controller 103 configured to control the whole of the air-conditioning apparatus is housed in the outdoor unit 101. Note that although the number of indoor units 102 (indoor heat exchangers 32) is one in Embodiment 1, any number of indoor units 102 (indoor heat exchangers 32) may be used. The outdoor unit 101 is connected to the indoor unit 102 through a liquid pipe 27 and a gas pipe 28.
More specifically, the auxiliary compressor 2 and the expander 8 are housed in a container 51. The auxiliary compressor 2 is connected to the expander 8 through the drive shaft 52, such that power generated in the expander 8 is recovered by the drive shaft 52 and is transferred to the auxiliary compressor 2. Accordingly, the auxiliary compressor 2 sucks the refrigerant discharged from the main compressor 1 and further compresses the refrigerant.
A refrigerant passage between the auxiliary compressor 2 and the outdoor heat exchanger 4 and a refrigerant passage between the indoor heat exchanger 32 and the accumulator 9 are connected to the first four-way valve 3, serving as the refrigerant flow switching device. In addition, a refrigerant passage between the outdoor heat exchanger 4 and the expander 8 and a refrigerant passage between the expander 8 and the expansion valve 31 are connected to the second four-way valve 6. The four-way valves 3 and 6 each switch between passages associated with an operation mode related to cooling or heating in accordance with an instruction from the controller 103 to switch between refrigerant paths.
In the cooling operation, the refrigerant flows from the auxiliary compressor 2 to the outdoor heat exchanger 4 and flows from the indoor heat exchanger 32 to the accumulator 9. Furthermore, the refrigerant flows from the outdoor heat exchanger 4 through the expander 8 to the indoor heat exchanger 32.
In the heating operation, the refrigerant flows from the auxiliary compressor 2 to the indoor heat exchanger 32 and flows from the outdoor heat exchanger 4 to the accumulator 9. In addition, the refrigerant flows from the indoor heat exchanger 32 through the expander 8 to the outdoor heat exchanger 4.
The first and second four-way valves 3 and 6 permit the refrigerant passing through the expander 3 and that passing through the auxiliary compressor 2 to flow in the same direction regardless of the cooling operation or the heating operation.
The outdoor heat exchanger 4 includes fins (not illustrated) for increasing the area of heat transfer between, for example, a heat transfer tube through which the refrigerant is allowed to pass and the refrigerant flowing therethrough and outside air to exchange heat between the refrigerant and the air (outside air). For example, the outdoor heat exchanger 4 functions as an evaporator in the heating operation to evaporate the refrigerant into a gas (vapor). Whereas, the outdoor heat exchanger 4 functions as a condenser or gas cooler (hereinafter, referred to as a condenser) in the cooling operation. In some cases, the outdoor heat exchanger 4 does not completely convert the refrigerant into a gas or liquid and produces a two-phase mixture of gas and liquid (two-phase gas-liquid refrigerant).
The accumulator 9 has a function of retaining an excess refrigerant in the refrigeration cycle and a function of preventing the main compressor 1 from being damaged by returning a large amount of refrigerant to the main compressor 1.
The pre-expansion valve 7 configured to control the flow rate of the refrigerant passing through the expander 8 is disposed in a refrigerant passage 23 between the second four-way valve 6 and an inlet of the expander 8.
The second four-way valve 6, the pre-expansion valve 7, a bypass 25 that bypasses the expander 8, and the bypass valve 5 configured to control the flow rate of the refrigerant passing through the bypass 25 are arranged in a refrigerant passage between the outdoor heat exchanger 4 and the indoor heat exchanger 32.
Controlling the bypass valve 5 and the pre-expansion valve 7 controls the flow rate of the refrigerant passing through the expander 8 and controls a pressure on a high-pressure side. Thus, the refrigeration cycle can be kept in a high efficiency state.
Note that control is not limited to control of the bypass valve 5 and the pre-expansion valve 7 and the pressure on the high-pressure side may be controlled by other methods.
A pressure sensor 11 configured to detect the pressure of the refrigerant flowing into the expander 8 is disposed at the inlet of the expander 8. In addition, a pressure sensor 12 configured to detect the pressure of the refrigerant flowing out of the expander 8 is disposed at an outlet of the expander 8. Installation positions of the pressure sensors 11 and 12 are not limited to the above-described positions. As long as the sensors can detect the pressure of the refrigerant flowing into the expander 8 and that of the refrigerant flowing out of the expander 8, the sensors may be arranged in any positions.
If those pressures can be estimated, temperature sensors configured to detect the temperature of the refrigerant may be used instead of the pressure sensors 11 and 12.
The indoor heat exchanger 32 includes fins (not illustrated) for increasing the area of heat transfer between, for example, a heat transfer tube through which the refrigerant is allowed to pass and the refrigerant flowing therethrough and the air to exchange heat between the refrigerant and the indoor air. For example, the indoor heat exchanger 32 functions as an evaporator in the cooling operation to evaporate the refrigerant into a gas (vapor). Whereas, the indoor heat exchanger 32 functions as a condenser or gas cooler (hereinafter, referred to as a condenser) in the heating operation.
The indoor heat exchanger 32 is connected to the expansion valve 31. The expansion valve 31 controls the flow rate of the refrigerant flowing into the indoor heat exchanger 32. In the case where the refrigerant is not sufficiently decompressed by the expander 8, a pressure level is controlled by the expansion valve 31.
An operation in the cooling operation of the refrigeration cycle apparatus according to Embodiment 1, that is, the air-conditioning apparatus will now be described with reference to
In the cooling operation, a low-pressure refrigerant, first sucked in by the main compressor 1, is compressed into a high-temperature medium-pressure refrigerant and is then discharged from the main compressor 1. The refrigerant discharged from the main compressor 1 is sucked into the auxiliary compressor 2, is further compressed into a high-temperature high-pressure refrigerant, and is then discharged from the auxiliary compressor 2. The refrigerant discharged from the auxiliary compressor 2 passes through the first four-way valve 3, flows into the outdoor heat exchanger 4, dissipates heat to transfer heat to the outdoor air, and turns into a low-temperature high-pressure refrigerant.
The refrigerant, which has flowed out of the outdoor heat exchanger 4, branches into a channel toward the second four-way valve 6 and a channel toward the bypass valve 5. The refrigerant, which has passed through the second four-way valve 6, passes through the pre-expansion valve 7, enters the expander 8, and is decompressed into a low-pressure refrigerant, so that the refrigerant enters a low state of dryness. At this time, power is generated in the expander 8 with a decrease in pressure of the refrigerant. This power is recovered by the drive shaft 52, is transferred to the auxiliary compressor 2, and is used to compress the refrigerant in the auxiliary compressor 2.
The refrigerant discharged from the expander 8 passes through the second four-way valve 6 and then merges with the refrigerant, which has passed through the bypass valve 5 and flowed through the bypass 25. The resultant refrigerant flows out of the outdoor unit 101, passes through the liquid pipe 27, enters the indoor unit 102, flows toward the expansion valve 31, and is further decompressed by the expansion valve 31.
The refrigerant, which has flowed out of the expansion valve 31, removes heat from the indoor air to evaporate in the indoor heat exchanger 32, so that the refrigerant obtains a high state of dryness while being kept at a low pressure. Consequently, the indoor air is cooled.
The refrigerant, which has flowed out of the indoor heat exchanger 32, flows out of the indoor unit 102, passes through the gas pipe 28, enters the outdoor unit 101, passes through the first four-way valve 3, enters the accumulator 9, and is again sucked into the main compressor 1.
Repeating the above-described operation transfers heat of the indoor air to the outdoor air, so that an indoor space is cooled.
An operation in the heating operation of the refrigeration cycle apparatus according to Embodiment 1, that is, the air-conditioning apparatus will now be described.
In the heating operation, a low-pressure refrigerant, first sucked by the main compressor 1, is compressed into a high-temperature medium-pressure refrigerant and is then discharged from the main compressor 1. The refrigerant discharged from the main compressor 1 is sucked into the auxiliary compressor 2, is further compressed into a high-temperature high-pressure refrigerant, and is then discharged from the auxiliary compressor 2. The refrigerant discharged from the auxiliary compressor 2 passes through the first four-way valve 3 and flows out of the outdoor unit 101.
The refrigerant, which has flowed out of the outdoor unit 101, passes through the gas pipe 28, enters the indoor unit 102, flows towards the indoor heat exchanger 32, dissipates heat to transfer heat to the indoor air in the indoor heat exchanger 32, and turns into a low-temperature high-pressure refrigerant.
The refrigerant, which has flowed out of the indoor heat exchanger 32, is decompressed by the expansion valve 31, and flows out of the expansion valve 31. The refrigerant, which has flowed out of the expansion valve 31, flows out of the indoor unit 102, passes through the liquid pipe 27, enters the outdoor unit 101, and branches into a channel toward the second four-way valve 6 and a channel toward the bypass valve 5. The refrigerant, which has passed through the second four-way valve 6, passes through the pre-expansion valve 7, enters the expander 8, and is decompressed into a low-pressure refrigerant, so that the refrigerant enters a low state of dryness. At this time, power is generated in the expander 8 with a decrease in pressure of the refrigerant. This power is recovered by the drive shaft 52, is transferred to the auxiliary compressor 2, and is used to compress the refrigerant in the auxiliary compressor 2.
The refrigerant discharged from the expander 8 passes through the second four-way valve 6 and then merges with the refrigerant, which has passed through the bypass valve 5 and flowed through the bypass 25. The resultant refrigerant enters the outdoor heat exchanger 4.
The refrigerant removes heat from the outdoor air to evaporate in the outdoor heat exchanger 4, so that the refrigerant obtains a high state of dryness while being kept at a low pressure.
The refrigerant, which has flowed out of the outdoor heat exchanger 4, passes through the first four-way valve 3, enters the accumulator 9, and is again sucked into the main compressor 1.
Repeating the above-described operation transfers heat of the outdoor air to the indoor air, so that the indoor space is heated.
The structure and operation of a scroll expander 8 and that of a scroll auxiliary compressor 2 will now be described as examples of the expander 8 and the auxiliary compressor 2. Note that the auxiliary compressor 2 and the expander 8 are not limited to a scroll type. An auxiliary compressor and an expander of other positive displacement types, for example, a rolling piston type may be used.
A high-temperature medium-pressure refrigerant discharged from the main compressor 1 is sucked in through a suction pipe 53 of the auxiliary compressor 2 and is introduced into an outer side of the auxiliary compressor 2 defined by the spiral wrap 66 of the compressor fixed scroll 58 and the spiral wrap 64 of the orbiting scroll 57. Orbiting of the orbiting scroll 57 allows the refrigerant to gradually move to an inner side of the auxiliary compressor 2, so that the refrigerant is compressed into a high-temperature high-pressure refrigerant. The compressed refrigerant is discharged out through a discharge pipe 54 of the auxiliary compressor 2.
Whereas, a high-pressure refrigerant cooled by the outdoor heat exchanger 4 or the indoor heat exchanger 32 is sucked in through a suction pipe 55 of the expander 8 and is introduced into an inner side of the expander 8 defined by the spiral wrap 67 of the expander fixed scroll 59 and the spiral wrap 65 of the orbiting scroll 57. Orbiting of the orbiting scroll 57 allows the refrigerant to gradually move to an outer side of the expander 8, so that the refrigerant is expanded into a low-pressure refrigerant. The expanded refrigerant is discharged out through a discharge pipe 56 of the expander 8. Power generated by expansion of the refrigerant in the expander 8 is recovered through the drive shaft 52 and is transferred as power for compression to the auxiliary compressor 2.
The above-described mechanism constituting the auxiliary compressor 2 and the expander 8 is housed in the container 51.
As features of the present invention, the expander 8 includes a communicating pipe 71, which allows expansion chambers during expansion to communicate with the discharge pipe 56 of the expander 8, and a solenoid valve 72, serving as an opening and closing device, provided to the connecting pipe 71. The communicating pipe 71 is in communication with an expansion chamber 82a at a position 90 degrees away from a terminal 73 of the spiral wrap 67 in a direction toward the center thereof and an expansion chamber 81a at a position 270 degrees away from the terminal 73 in the direction toward the center.
An operation of the expander 8 will now be described with reference to
The crank angle of the drive shaft 52 is assumed to be 0 degree in a state in which an end portion of the center of the spiral wrap 67 is in contact with the inner surface of the spiral wrap 65. When the crank angle is 0 degree, the refrigerant is partitioned into the expansion chamber 81a and the expansion chamber 82b. The inflow of the high-pressure refrigerant into the expansion chamber 81a and the expansion chamber 82a continues until immediately before the crank angle reaches 360 degrees. Expansion of the refrigerant in a trapped state in the expansion chamber 81a and the expansion chamber 82a drives the orbiting scroll 57.
While the crank angle shifts from 270 degrees to 360 degrees (0 degree), expansion in the expansion chambers 81a and 82a terminates, so that the refrigerant is discharged to an expander discharge space 85. In a position at 360 degrees in FIG. 4, the expansion chambers 81a and 82a opening into the expander discharge space 85 are represented as expansion chambers 81b and 82b, respectively. The discharged refrigerant is expelled to the low-pressure side through the discharge pipe 56.
An operation of the expander 8 upon stopping the refrigeration cycle apparatus according to Embodiment 1, that is, the air-conditioning apparatus will now be described with reference to
The orbiting scroll 57 continues orbiting while gradually reducing its rotation speed until high and low pressures are equalized after stop of the main compressor 1. When driving force of the expander 8 becomes smaller than the force of friction between the orbiting scroll 57 and the compressor fixed scroll 58 or the expander fixed scroll 59, the orbiting scroll 57 completely stops.
In Embodiment 1, the solenoid valve 72 is opened after stop of the main compressor 1 by the time when high and low pressures are equalized. During the orbiting of the orbiting scroll 57 until high and low pressures are equalized, the expansion chamber 81a becomes in communication with the discharge pipe 56 immediately after a contact point 91b between the outer surface of the spiral wrap 67 and the inner surface of the spiral wrap 65 passes the communicating pipe 71. In other words, the expansion chamber 81a is under low pressure. Similarly, the expansion chamber 82a becomes in communication with the discharge pipe 56 immediately after a contact point 92b between the outer surface of the spiral wrap 65 and the inner surface of the spiral wrap 67 passes the communicating pipe 71. In other words, the expansion chamber 82a is under low pressure.
When the expansion chambers 81a and 82a are under low pressure as described above, no difference in pressure between the expansion chambers 81a and 82a and the expander discharge space 85 will exist. Thus, the orbiting scroll 57 loses its driving force, such that the orbiting scroll can easily stop. In other words, the orbiting scroll 57 stops immediately after the contact points 91b and 92b pass the communicating pipe 71. Specifically, the communicating pipe 71 is connected to the expansion chambers 81a and 82a on the track of the contact points 91b and 92b during orbiting (revolving) of the orbiting scroll 57.
After the main compressor 1 and the expander 8 completely stop, the solenoid valve 71 is closed. Complete stop of the expander 8 means that the orbiting scroll 57 stops orbiting (revolving). Stop of the expander 8 can be determined after one or two minutes from the time when pressures detected by the pressure sensor 11 and that by the pressure sensor 12 are approximately equal.
Effects of improved startup performance by control of the stop position of the orbiting scroll 57 as in Embodiment 1 will be described.
Since high and low pressures in the air-conditioning apparatus are equalized after complete stop of the main compressor 1 and the expander 8, pressures in the circuit are substantially equalized. In the expander 8, pressures in the expansion chambers 81a and 82a and the expander discharge space 85 are equalized. In such a stopped mode, when the main compressor 1 is resumed, the refrigerant is gradually expelled through the discharge pipe 56, thus reducing the pressure in the expander discharge space 85.
Since the expansion chamber 81 a is partitioned by the spiral wraps 65 and 67 and has not been opened to the expander discharge space 85, the pressure during the equalization is kept. Thus, a pressure difference exists between the expansion chamber 81a and the expander discharge space 85. Pressure receiving portion 95a or pressure receiving portion 95b that receives the pressure difference is a portion between the contact point 92b and the contact point 91b in the spiral wrap 65.
When driving force caused by the pressure difference received by the pressure receiving portion 95a or pressure receiving portion 95b is greater than static friction force applied to various sliding portions, such as the orbiting scroll 57 and an orbiting bearing 63, the orbiting scroll 57, which has stopped, starts orbiting.
Comparison between the pressure receiving portion 95b in the case where the orbiting scroll 57 is stopped while the stop position thereof is being controlled as in Embodiment 1 (
As described above, since the pressure receiving portion 95b that receives the difference between the pressure during the equalization and a low pressure upon startup of the air-conditioning apparatus can be further increased in Embodiment 1, force acting in the orbiting direction in which the orbiting scroll 57 is driven from the stopped mode can be further increased.
Furthermore, in Embodiment 1, since the connecting portions with the communicating pipe 71 is provided 90 crank angle degrees before the crank angle in which the expansion chamber 81a and the expansion chamber 82a each open into the expander discharge space 85, the pressure receiving portion 95b when the air-conditioning apparatus is resumed can be increased. The angular positions in which the portions connected to the communicating pipe 71 are not limited to the above-described positions. As long as the pressure receiving portion 95b can be increased, the portions may be arranged in any position. However, it is effective to provide each portion between the position where the expansion chambers 81a and 82a each opens into the expander discharge space 85 and a position 90 degrees before each corresponding opening position.
Furthermore, while two portions connected to the communicating pipe 71 are arranged in Embodiment 1, a single portion may be disposed in order to increase workability.
Furthermore, in Embodiment 1, since driving force applied to the orbiting scroll 57 is smaller than static friction force applied to various sliding portions, such as the orbiting scroll 57 and the orbiting bearing 63, startup failure that the orbiting scroll 57 does not orbit can be reduced. Thus, the reliability of the air-conditioning apparatus can be further increased.
Furthermore, while Embodiment 1 has been described with respect to the case where the present invention is applied to a scroll expander, the application is not limited to a scroll type, but the present invention is applicable to, for example, a rotary expander including a rolling piston.
Specifically, even in the rotary expander, the area of pressure reception varies depending on a stop position of the rolling piston. Disadvantageously, insufficient revolution of the rolling piston may occur upon startup of the air-conditioning apparatus. Therefore, the communicating pipe 71 allows chambers partitioned by the rolling piston to communicate with a discharge pipe (low-pressure side), so that the stop position of the rolling piston can be controlled. Consequently, the area of pressure reception can be increased so that startup failure does not easily occur.
Furthermore, in Embodiment 1, when starting up the expander 8, means for forcing the orbiting scroll 57 to orbit, for example, using a power recovery generator as a motor is not required. The orbiting scroll 57 can be allowed to orbit only using fluid energy generated during decompression of the refrigerant by the expander. Thus, the structure of the expander 8 can be simplified.
Furthermore, in Embodiment, the solenoid valve 72 is used as an opening and closing device for the communicating pipe 71. Needless to say, other opening and closing devices may be used.
In the above-described Embodiment 1, the communicating pipe 71 and the solenoid valve 72 are arranged outside the container 51. Embodiment 2 in which the communicating pipe 71 and the valve are housed in the container 51 will now be described.
In
Referring to
In Embodiment 2, the coil 111, the valve 112, and the spring 113 provide the same function as that of the above-described solenoid valve 72. Since these components are housed in the container 51, the air-conditioning apparatus can be reduced in size.
In the above description, for convenience of explanation, each of the coil 111, the valve 112, the spring 113, and the communicating path 114 is illustrated as a single component. However, another coil 111, another valve 112, another spring 113, and another communicating path 114 are arranged for communication between an expansion chamber 81 and the expander discharge space 85. Alternatively, each of these components may be a single component.
1 main compressor; 2 auxiliary compressor; 3 first four-way valve; 4 outdoor heat exchanger; 5 bypass valve; 6 second four-way valve; 7 pre-expansion valve; 8. expander; 9 accumulator; 11, 12 pressure sensor; 21 discharge pipe of main compressor 1; 22 inlet or outlet pipe of outdoor heat exchanger; 23 suction pipe of expander 8; 24 discharge pipe of expander 8; 25 bypass; 26 pipe; 27 liquid pipe; 28 gas pipe; 29 inlet pipe of accumulator 9; 31 expansion valve; 32 indoor heat exchanger; 51 container; 52 drive shaft; 53 suction pipe of auxiliary compressor 2; 54 discharge pipe of auxiliary compressor 2; 55 suction pipe of expander 8; 56 discharge pipe of expander 8; orbiting scroll; 58 compressor fixed scroll; 59 expander fixed scroll; 60 Oldham's ring; 61 slider; 62 shaft fitting hole; 63 orbiting bearing; 64 spiral wrap on upper surface of orbiting scroll 57; 65 spiral wrap on lower surface of orbiting scroll 57; 66 spiral wrap of compressor fixed scroll 58; 67 spiral wrap of expander fixed scroll 59; 68 oil pump; 69 lubricating oil; 70 balancer; 71 communicating pipe; 72 solenoid valve; 73 terminal of spiral wrap 67; 81a, 81b expansion chamber; 82a, 82b expansion chamber; 85 expander discharge space; 91a, 91b contact point between outer surface of spiral wrap 67 and inner surface of spiral wrap 65; 92a, 92b contact point between outer surface of spiral wrap 65 and inner surface of spiral wrap 67; 95a, 95b pressure receiving portion; 111 coil; 112 valve; 113 spring; 114 communicating path.
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2010/000257 | 1/19/2010 | WO | 00 | 8/24/2012 |
