JP2011012633A - Scroll compressor - Google Patents

Abstract

In a scroll compressor that cools a fixed scroll and a turning scroll with a cooling fluid, a flow rate of the cooling fluid in both the fixed scroll and the turning scroll is secured.
A main introduction passage (190) through which a cooling fluid flows, first and second branch passages (191, 192) bifurcated from a downstream end of the main introduction passage (190), and a fixed scroll (30) are provided. The fixed side passage (40) through which the cooling fluid that has been formed and flows out of the first branch passage (191) flows, and the cooling fluid that is formed in the orbiting scroll (50) and flows out of the second branch passage (192) flows. A cooling fluid circuit (180) having a turning side passage (60) and a flow rate control mechanism (186) for controlling the flow rate of the cooling fluid flowing through the first branch passage (191) and the second branch passage (192). ).
[Selection] Figure 2

Description

  The present invention relates to a scroll compressor that cools a fixed scroll and a turning scroll with a fluid.

  2. Description of the Related Art Conventionally, there is known a scroll compressor that includes a fixed scroll and a turning scroll, and sucks and compresses gas into a compression chamber formed by the fixed scroll and the turning scroll. Patent Document 1 discloses a scroll compressor that cools the fixed scroll and the orbiting scroll by forming a refrigerant passage inside the fixed scroll and the orbiting scroll and supplying the refrigerant to the passage. In this scroll compressor, the fixed scroll and the orbiting scroll are cooled to suppress the gas temperature rise in the process of being compressed in the compression chamber, and the gas is compressed by the scroll compressor by suppressing the gas temperature rise. The energy required to reduce energy consumption.

  Specifically, in the scroll compressor disclosed in Patent Document 1, the refrigerant sent from the refrigerant tank to the refrigerant cooler and cooled is supplied to the fixed scroll and the orbiting scroll by the refrigerant pump. At that time, a part of the refrigerant discharged from the refrigerant pump is supplied to the passage in the fixed scroll, and the rest is supplied to the passage in the orbiting scroll. That is, in this scroll compressor, the passage in the fixed scroll and the passage in the orbiting scroll are arranged in parallel with each other in the flow path of the refrigerant as the cooling fluid.

JP 2003-254266 A

  In a scroll compressor that cools the fixed scroll and the orbiting scroll, it is necessary to sufficiently cool both the fixed scroll and the orbiting scroll in order to reliably suppress the temperature rise of the gas in the compression chamber. It is necessary to secure a sufficient flow rate of the cooling fluid in both the passage in the scroll and the passage in the orbiting scroll.

  However, in the scroll compressor disclosed in Patent Document 1, the passage in the fixed scroll and the passage in the orbiting scroll are arranged in parallel with each other in the flow path of the cooling fluid. On the other hand, the passage in the fixed scroll and the passage in the orbiting scroll are not necessarily the same in flow passage cross-sectional shape and length, and therefore the flow resistances of these passages are not necessarily equal. For this reason, in the scroll compressor disclosed in the cited document 1, the distribution ratio of the cooling fluid to the passage in the fixed scroll and the passage in the orbiting scroll cannot be appropriately set. There was a risk that both could not be cooled sufficiently.

  The present invention has been made in view of the above point, and an object of the present invention is to provide a cooling compressor for cooling the fixed scroll and the orbiting scroll with the cooling fluid, and the flow rate of the cooling fluid in both the fixed scroll and the orbiting scroll. It is to secure.

  According to a first aspect of the present invention, there is provided a scroll compressor including a compression mechanism (20) provided with a fixed scroll (30) and an orbiting scroll (50) and sucking compressed gas into the compression mechanism (20) for compression. The main introduction passage (190) through which the cooling fluid flows, the first and second branch passages (191, 192) bifurcated from the downstream end of the main introduction passage (190), and the fixed scroll (30) The fixed side passage (40) through which the cooling fluid flowing out of the first branch passage (191) flows and the cooling formed in the orbiting scroll (50) and out of the second branch passage (192). Cooling having a swirl side passage (60) through which a working fluid flows and a flow rate control mechanism (186) for controlling the flow rate of the cooling fluid flowing through the first branch passage (191) and the second branch passage (192). It is provided with the fluid circuit (180) for operation.

  In the first invention, the scroll compressor is provided with a cooling fluid circuit (180). In the cooling fluid circuit (180), the cooling fluid flowing through the main introduction passage (190) is divided into the first branch passage (191) and the second branch passage (192). The cooling fluid that has flowed out of the first branch passage (191) flows into the fixed-side passage (40) formed in the fixed scroll (30), and is used for cooling the fixed scroll (30). The cooling fluid that has flowed out of the second branch passage (192) flows into the turning-side passage (60) formed in the orbiting scroll (50) and is used for cooling the orbiting scroll (50). The flow rate control mechanism (186) of the present invention controls the flow rate of the cooling fluid in the first branch passage (191) and the flow rate of the cooling fluid in the second branch passage (192). Therefore, even if the flow resistance of the fixed side passage (40) is different from the flow resistance of the swivel side passage (60), the flow rate of the cooling fluid in the fixed side passage (40) and the cooling in the swirl side passage (60) are reduced. The flow rate of the working fluid can be made equal.

  In a second aspect based on the first aspect, the flow rate control mechanism (186) includes a first flow rate control valve (184) provided in the first branch passage (191) and the second branch passage (192). And a second flow rate adjustment valve (185).

  In the second aspect of the invention, the flow rate of the cooling fluid in the first branch passage (191) is adjusted by adjusting the opening of the first flow control valve (184), and further the cooling in the fixed side passage (40). The flow rate of the working fluid is adjusted. In addition, the flow rate of the cooling fluid in the second branch passage (192) is adjusted by adjusting the opening of the second flow rate control valve (185), and further, the flow rate of the cooling fluid in the turning side passage (60). Is adjusted. Therefore, even if the flow resistance of the fixed side passage (40) and the flow resistance of the turning side passage (60) are different by individually adjusting the opening degree of these flow control valves (184, 185), the fixed side passage The flow rate of the cooling fluid in (40) can be made equal to the flow rate of the cooling fluid in the turning side passage (60).

  According to a third invention, in the second invention, a casing (11) is provided which is formed in a hollow container shape in which the compression mechanism (20) is accommodated and in which lubricating oil of the compression mechanism (20) is accumulated. Lubricating oil accumulated in the casing (11) is introduced into the introduction passage (190), and an upstream side cooler (181) for cooling the lubricating oil is connected to the introduction passage (190).

  In the third invention, the lubricating oil of the compression mechanism (20) accumulates in the casing (11). The lubricating oil flows through the main introduction passage (190) as a cooling fluid and is cooled in the upstream cooler (181). The lubricating oil cooled in the main introduction passage (190) is divided into the first branch passage (191) and the second branch passage (192). The lubricating oil branched to the first branch passage (191) flows through the fixed side passage (40) and is used for cooling the fixed scroll (30). The lubricating oil branched to the second branch passage (192) flows through the turning side passage (60) and is used for cooling the turning scroll (50).

  According to a fourth aspect of the present invention, there is provided a scroll compressor including a compression mechanism (20) provided with a fixed scroll (30) and an orbiting scroll (50) and sucking compressed gas into the compression mechanism (20) for compression. A first supply passage (193) including a first transfer mechanism (128a) for transferring a cooling fluid, and a second supply passage including a second transfer mechanism (128b) for transferring a cooling fluid. (194), a fixed side passage (40) formed in the fixed scroll (30) through which the cooling fluid flowing out of the first supply passage (193) flows, and formed in the orbiting scroll (50) and the above A cooling fluid circuit (180) having a swirl side passage (60) through which the cooling fluid flowing out of the second supply passage (194) flows is provided.

  In the fourth invention, the scroll compressor is provided with a cooling fluid circuit (180). In the cooling fluid circuit (180), the cooling fluid transported by the first transport mechanism (128a) is sent to the fixed-side passage (40) via the first supply passage (193). In the cooling fluid circuit (180), the cooling fluid transported by the second transport mechanism (128b) is sent to the turning passage (60) via the second supply passage (194). That is, in the present invention, the passage for sending the cooling fluid to the fixed side passage (40) is different from the passage for sending the cooling fluid to the turning side passage (60), and the fixed side passage (40 And a transport mechanism for sending the cooling fluid to the turning passage (60). Therefore, even if the flow resistance of the fixed side passage (40) is different from the flow resistance of the swivel side passage (60), the flow rate of the cooling fluid in the fixed side passage (40) The flow rate of the working fluid can be matched equally.

  According to a fifth invention, in the fourth invention, a casing (11) formed in a hollow container shape in which the compression mechanism (20) is accommodated and in which lubricating oil of the compression mechanism (20) accumulates, and the casing ( 11) a drive shaft (100) that is housed in the drive shaft and drives the orbiting scroll (50), and the first transport mechanism (128a) and the second transport mechanism (128b) are connected to the drive shaft (100). Lubricating oil that is driven to rotate and conveys the lubricating oil accumulated in the casing (11) is respectively constituted, and the first supply passage (193) is lubricated by the first conveying mechanism (128a). A first upstream cooler (181a) for cooling the oil is connected, and a second upstream cooling for cooling the lubricating oil transported by the second transport mechanism (128b) is connected to the second supply passage (194). A device (181b) is connected.

  In the fifth aspect of the invention, the orbiting scroll (50) is driven by the rotation of the drive shaft (100), and at the same time, the first transport mechanism (128a) and the second transport mechanism ( 128b) is also driven rotationally. When the first transport mechanism (128a) is driven to rotate, the lubricating oil accumulated in the casing (11) flows through the first supply passage (193) as a cooling fluid, and the first upstream cooler (181a). Cooled. The lubricating oil cooled in the first supply passage (193) flows through the fixed side passage (40) and is used for cooling the fixed scroll (30). When the second transport mechanism (128b) is driven to rotate, the lubricating oil accumulated in the casing (11) flows through the second supply passage (194) as a cooling fluid, and the second upstream cooler ( It is cooled in 181b). The lubricating oil cooled in the second supply passage (194) flows through the turning side passage (60) and is used for cooling the turning scroll (50).

  In the present invention, since the first transport mechanism (128a) and the second transport mechanism (128b) are positive displacement pumps, each supply passage is independent of the flow resistance of the fixed-side passage (40) and the turning-side passage (60). (193,194) can be sent a constant flow of lubricant. Therefore, the flow rate of the cooling fluid in the fixed side passage (40) can be made equal to the flow rate of the cooling fluid in the turning side passage (60).

  According to a sixth aspect, in the third or fifth aspect, the cooling fluid connected to the cooling fluid circuit (180) and passing through the fixed side passage (40) and the turning side passage (60) is cooled. The cooling fluid circuit (180) includes a downstream side cooler (197), and the cooling fluid circuit (180) sucks the cooling fluid cooled by the downstream side cooler (197) into the compression mechanism (20). It is characterized by supplying to.

  In the sixth aspect of the invention, the cooling fluid that has passed through the fixed side passage (40) and the turning side passage (60) is cooled in the downstream side cooler (197) and then supplied to the compressed gas. The cooling fluid supplied to the compressed gas from the cooling fluid circuit (180) is sucked into the compression mechanism (20) together with the compressed gas. That is, in the scroll compressor of the present invention, the lubricating oil cooled in the downstream cooler (197) is sucked into the compression mechanism (20) together with the low-pressure compressed gas. The lubricating oil that has been cooled in the downstream cooler (197) and sucked into the compression mechanism (20) together with the gas to be compressed comes into direct contact with the gas to be compressed that is being compressed in the compression mechanism (20). Absorbs heat from compressed gas.

  In a seventh aspect based on the sixth aspect, the compression mechanism (20) discharges the compressed gas to be compressed into the internal space of the casing (11), while the casing (11) includes the compression mechanism. A discharge pipe (13) for leading the compressed gas discharged from (20) to the outside is provided. In the internal space of the casing (11), the compressed gas discharged from the compression mechanism (20) is provided. Lubricating oil is stored in a portion where gas is present.

  In the seventh invention, the compressed gas compressed by the compression mechanism (20) is discharged from the compression mechanism (20) to the internal space of the casing (11), and then passes through the discharge pipe (13) to the casing (11 ) Will flow out to the outside. In the internal space of the casing (11), lubricating oil is stored in a portion where the compressed gas discharged from the compression mechanism (20) is present. The pressure of the lubricating oil stored in the casing (11) is substantially equal to the pressure of the compressed gas discharged from the compression mechanism (20). Lubricating oil having substantially the same pressure as the compressed gas discharged from the compression mechanism (20) flows into the cooling fluid circuit (180) as a cooling fluid. The lubricating oil flowing as a cooling fluid in the cooling fluid circuit (180) passes through the fixed-side passage (40) and the turning-side passage (60) and is finally sucked into the compression mechanism (20). To the compressed gas. That is, in the cooling fluid circuit (180) of the present invention, the starting end communicates with the lubricating oil in the casing (11) whose pressure is substantially equal to the high-pressure compressed gas discharged from the compression mechanism (20). The end communicates with the low-pressure compressed gas sucked into the compression mechanism (20). Therefore, in the cooling fluid circuit (180) of the present invention, the cooling fluid can be conveyed by utilizing the pressure difference between the start end and the end.

  In an eighth invention according to any one of the first to seventh inventions, the orbiting scroll (50) includes a revolving side end plate portion (56) formed in a flat plate shape, and the revolving side end plate portion (56). ) And a swirl wall-shaped swirl side wrap (53) standing on the front surface, and the compression mechanism (20) has a housing member (70) in sliding contact with the back surface of the swivel side end plate part (56). An end portion of the turning-side passage (60) is opened on the back surface of the turning-side end plate portion (56), and the back side of the turning-side end plate portion (56) in the housing member (70). The slidable contact portion includes a recess (77) that always communicates with an end of the swing side passage (60) that opens to the back of the swing end panel (56), and a periphery of the recess (77). A sealing member (80, 81) which is provided so as to surround and seals a gap between the turning-side end plate portion (56) and the housing member (70); Vignetting, to the housing member (70) is characterized in that the connection passage downstream end with the cooling fluid is introduced to connect to the recess (77) (83) is formed.

  In the eighth invention, the end of the orbiting side passageway (60) formed in the orbiting scroll (50) opens to the back surface of the orbiting side end plate part (56). On the other hand, in the housing member (70), a recessed portion (77) is formed in a portion that is in sliding contact with the back surface of the turning-side end plate portion (56). The hollow portion (77) is always in communication with the end portion of the turning side passage (60) opened on the back surface of the turning side end plate portion (56). In other words, the orbiting scroll (50) moves during the operation of the scroll compressor, but the hollow portion (77) of the housing member (70) is maintained even while the orbiting scroll (50) is moving. It continues to communicate with the end portion of the turning side passageway (60) opened on the back surface of (56). For this reason, in the cooling fluid circuit (180) of the present invention, the cooling fluid introduced into the connection passage (83) of the housing member (70) regardless of the position of the orbiting scroll (50) 77) to the turning passage (60). The seal member (80, 81) provided on the housing member (70) seals the gap between the turning-side end plate portion (56) and the housing member (70), and is a recessed portion from the turning-side passage (60). The leakage of the cooling fluid flowing into (77) or the cooling fluid flowing into the turning side passageway (60) from the recess (77) is suppressed.

  In the scroll compressor of the first invention, a flow rate control mechanism (186) is provided to control the flow rate of the cooling fluid in the first branch passage (191) and the second branch passage (192). For this reason, the flow rate of the cooling fluid in the fixed side passage (40) connected to the first branch passage (191) is equal to the flow rate of the cooling fluid in the swirl side passage (60) connected to the second branch passage (192). can do. That is, in the scroll compressor of the present invention, the flow rate of the cooling fluid can be prevented from being biased to one of the fixed side passage (40) and the turning side passage (60), and the fixed side passage (40) and the turning side passage (60 ), A sufficient amount of cooling fluid can be reliably supplied. According to the scroll compressor of the present invention, both the fixed scroll (30) and the orbiting scroll (50) can be reliably cooled, and as a result, the compressed gas compressed in the compression mechanism (20). It is possible to reliably suppress the temperature rise.

  In particular, in the second aspect of the invention, the fixed flow passage (40) and the first flow control valve (184) of the first branch passage (191) and the second flow control valve (185) of the second branch passage (192) Each flow rate of the cooling fluid flowing through the turning side passageway (60) can be individually adjusted. For this reason, it can avoid easily and reliably that the flow volume of the cooling fluid is biased to one of the fixed side passage (40) and the turning side passage (60).

  In the third invention, the lubricating oil stored in the internal space of the casing (11) not only lubricates the compression mechanism (20) but also cools the fixed scroll (30) and the orbiting scroll (50). It is also used as a cooling fluid. That is, in this invention, even when the fixed scroll (30) and the orbiting scroll (50) are not cooled, the lubricating oil necessary for the operation of the compression mechanism (20) is also used as the cooling fluid. Therefore, according to the present invention, when the fixed scroll (30) and the orbiting scroll (50) are not cooled, the scroll compressor is compared with the case where unnecessary fluid (for example, cooling water) is used as the cooling fluid. The configuration can be simplified.

  In the scroll compressor according to the fourth aspect of the invention, the cooling fluid transported by the first transport mechanism (128a) is sent to the fixed side passage (40) via the first supply passage (193), and the second transport is performed. The cooling fluid conveyed by the mechanism (128b) is sent to the turning side passage (60) via the second supply passage (194). For this reason, in the scroll compressor of the present invention, the flow rate of the cooling fluid can be prevented from being biased to one of the fixed side passage (40) and the turning side passage (60), and the fixed side passage (40) and the turning side passage ( 60), it is possible to reliably supply a sufficient amount of cooling fluid. According to the scroll compressor of the present invention, both the fixed scroll (30) and the orbiting scroll (50) can be reliably cooled, and as a result, the compressed gas compressed in the compression mechanism (20). It is possible to reliably suppress the temperature rise.

  In particular, in the fifth invention, the first transport mechanism (128a) and the second transport mechanism (128b) are constituted by positive displacement pumps that are rotationally driven by the drive shaft (100). For this reason, it is possible to supply a certain amount of lubricating oil to the fixed side passage (40) and the turning side passage (60) without being affected by the flow resistance of the fixed side passage (40) and the turning side passage (60). It can be avoided more reliably that the flow rate of the cooling fluid is biased to one of the fixed side passage (40) and the turning side passage (60).

  In the fifth invention, the lubricating oil stored in the internal space of the casing (11) not only lubricates the compression mechanism (20) but also cools the fixed scroll (30) and the orbiting scroll (50). It is also used as a cooling fluid for this purpose. Therefore, the configuration of the scroll compressor can be simplified.

  In the sixth invention, the downstream cooler (197) is connected to the cooling fluid circuit (180). Then, the lubricating oil flowing in the cooling fluid circuit (180) as the cooling fluid is cooled in the downstream cooler (197) and then sucked into the compression mechanism (20) together with the gas to be compressed, in the compression mechanism (20). Heat is absorbed from the gas to be compressed during compression. Therefore, according to the present invention, lubricating oil as a cooling fluid is supplied to the fixed side passage (40) and the orbiting side passage (60) to cool the fixed scroll (30) and the orbiting scroll (50). In addition, the temperature of the compressed gas being compressed in the compression mechanism (20) is suppressed by sucking the lubricating oil cooled in the downstream cooler (197) together with the compressed gas into the compression mechanism (20). be able to.

  Particularly in the seventh aspect of the invention, the pressure of the lubricating oil stored in the casing (11) is substantially equal to the pressure of the compressed gas discharged from the compression mechanism (20). For this reason, in the cooling fluid circuit (180) of the present invention, it is possible to flow the lubricating oil as the cooling fluid from the starting end toward the terminating end by utilizing the pressure difference between the starting end and the terminating end. Therefore, according to the present invention, it is possible to reduce energy required for flowing the lubricating oil as the cooling fluid in the cooling fluid circuit (180). For this reason, for example, the power of a pump (conveying mechanism) for conveying the cooling fluid can be reduced, or the conveying mechanism can be omitted.

  In the eighth invention, the housing member (70) is provided with the recess (77), the connection passage (83), and the seal member (80, 81), so that the connection passage (83) of the housing member (70) is provided. And the orbiting side passageway (60) of the orbiting scroll (50) are always in communication. Therefore, according to the present invention, the cooling fluid introduced into the connection passage (83) can be reliably sent to the turning side passage (60) even during operation.

It is a refrigerant circuit figure which shows schematic structure of the air conditioning apparatus of Embodiment 1. FIG. It is a longitudinal cross-sectional view which shows schematic structure of the scroll compressor of Embodiment 1. It is a longitudinal cross-sectional view which shows the principal part of the scroll compressor of Embodiment 1. FIG. 3 is a cross-sectional view illustrating a fixed-side main body member of the fixed scroll according to the first embodiment. It is a cross-sectional view which shows the oil pump of the scroll compressor of Embodiment 1. It is a longitudinal cross-sectional view which shows schematic structure of the scroll compressor of Embodiment 2. FIG. It is a longitudinal cross-sectional view which shows schematic structure of the scroll compressor of the 1st modification of other embodiment. It is a longitudinal cross-sectional view which shows schematic structure of the scroll compressor of the 2nd modification of other embodiment. It is a longitudinal cross-sectional view which shows the principal part of the compression mechanism of the 2nd modification of other embodiment. It is a longitudinal cross-sectional view which shows schematic structure of the scroll compressor of the 3rd modification of other embodiment. It is a longitudinal cross-sectional view which shows the principal part of the compression mechanism of the 3rd modification of other embodiment. It is a longitudinal cross-sectional view which shows schematic structure of the scroll compressor of the 4th modification of other embodiment.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

Embodiment 1 of the Invention
A first embodiment of the present invention will be described. The present embodiment is a so-called separate type air conditioner (150). A scroll compressor (171) is connected to the refrigerant circuit (160) of the air conditioner (150).

<Air conditioning device>
The overall configuration of the air conditioner (150) will be described with reference to FIG. The air conditioner (150) includes one outdoor unit (151) and two indoor units (153a, 153b). The number of indoor units (153a, 153b) is merely an example, and may be one, or may be three or more.

  The outdoor unit (151) is provided with an outdoor circuit (170). Each indoor unit (153a, 153b) is provided with one indoor circuit (175a, 175b). In the air conditioner (150), the refrigerant circuit (160) is connected by connecting the outdoor circuit (170) and each indoor circuit (175a, 175b) with the liquid side connecting pipe (161) and the gas side connecting pipe (162). Is formed. In the refrigerant circuit (160), the indoor circuits (175a, 175b) are arranged in parallel with each other.

  A scroll compressor (171), an outdoor heat exchanger (172), an outdoor expansion valve (173), and a four-way switching valve (174) are connected to the outdoor circuit (170). The scroll compressor (171) includes a compressor body (10) and an upstream cooler (181).

  In the outdoor circuit (170), the compressor body (10) of the scroll compressor (171) has its discharge pipe (13) connected to the first port of the four-way switching valve (174), and its suction pipe (12). Is connected to the second port of the four-way selector valve (174). One end of the outdoor heat exchanger (172) is connected to the third port of the four-way switching valve (174), and the other end is connected to one end of the outdoor expansion valve (173). The other end of the outdoor expansion valve (173) is connected to the liquid side end of the outdoor circuit (170). The fourth port of the four-way switching valve (174) is connected to the gas side end of the outdoor circuit (170).

  The detailed structure of the scroll compressor (171) will be described later. Here, an outline of the scroll compressor (171) will be described. The compressor body (10) of the scroll compressor (171) is a so-called hermetic compressor. An upstream cooler (181) is connected to the compressor body (10). This upstream-side cooler (181) is a fin-and-tube heat exchanger that exchanges heat between the refrigerating machine oil (ie, lubricating oil) stored in the casing (11) and outdoor air. Cooling.

  The outdoor heat exchanger (172) is a fin-and-tube heat exchanger, and exchanges heat between the refrigerant circulating in the refrigerant circuit (160) and outdoor air. The outdoor expansion valve (173) is a so-called electronic expansion valve. The four-way switching valve (174) includes a first state (state indicated by a solid line in FIG. 1) in which the first port communicates with the third port and the second port communicates with the fourth port; The state is switched to a second state (state indicated by a broken line in FIG. 1) in which the port communicates with the fourth port and the second port communicates with the third port.

  One indoor heat exchanger (176a, 176b) and one indoor expansion valve (177a, 177b) are connected to each indoor circuit (175a, 175b). In each indoor circuit (175a, 175b), an indoor heat exchanger (176a, 176b) and an indoor expansion valve (177a, 177b) are arranged in series from the gas side end to the liquid side end. Each indoor circuit (175a, 175b) has its liquid-side end connected to the liquid-side end of the outdoor circuit (170) via the liquid-side connecting pipe (161), and its gas-side end connected to the gas-side connecting pipe (162) Is connected to the gas side end of the outdoor circuit (170).

  The indoor heat exchangers (176a, 176b) are fin-and-tube heat exchangers, and exchange heat between the refrigerant circulating in the refrigerant circuit (160) and room air. The indoor expansion valves (177a, 177b) are so-called electronic expansion valves.

  The outdoor unit (151) is provided with an outdoor fan (152). The outdoor fan (152) is for supplying outdoor air to both the outdoor heat exchanger (172) and the upstream side cooler (181). That is, when the outdoor fan (152) is operated, a part of the outdoor air sucked into the outdoor unit (151) passes through the upstream side cooler (181) and the rest passes through the outdoor heat exchanger (172). Each indoor unit (153a, 153b) is provided with one indoor fan (154a, 154b). The indoor fans (154a, 154b) are for supplying indoor air to the indoor heat exchangers (176a, 176b). That is, when the indoor fan (154a, 154b) is operated, the indoor air sucked into the indoor unit (153a, 153b) passes through the indoor heat exchanger (176a, 176b).

<Scroll compressor>
The overall configuration of the scroll compressor (171) will be described with reference to FIG. As described above, the scroll compressor (171) includes the compressor body (10) and the upstream side cooler (181). The scroll compressor (171) includes a cooling fluid circuit (180). The upstream cooler (181) is connected to the cooling fluid circuit (180). Details of the cooling fluid circuit (180) will be described later.

  As described above, the compressor body (10) is a so-called hermetic compressor, and sucks and compresses a gas refrigerant as a gas to be compressed. The compressor body (10) includes a casing (11) formed in a vertically long cylindrical sealed container shape. A compression mechanism (20), a drive shaft (100), an electric motor (110), and a lower bearing member (115) are accommodated in the internal space of the casing (11). In the internal space of the casing (11), the compression mechanism (20) is disposed above the casing (11), the electric motor (110) is disposed below the compression mechanism (20), and the lower bearing member (115) is disposed below the electric motor (110). Is arranged. In the internal space of the casing (11), refrigeration oil (that is, lubricating oil) is stored at the bottom.

  The casing (11) is provided with a suction pipe (12) and a discharge pipe (13). The suction pipe (12) passes through the casing (11), and one end thereof is connected to the compression mechanism (20). On the other hand, the discharge pipe (13) passes through the casing (11), and one end of the discharge pipe (13) opens in a portion between the compression mechanism (20) and the electric motor (110) in the internal space of the casing (11). The casing (11) is provided with an oil outlet pipe (14), a first oil introduction pipe (17), and a second oil introduction pipe (18).

  The compression mechanism (20) is provided with a fixed scroll (30), a turning scroll (50), and a housing member (70). The detailed structure of the compression mechanism (20) will be described later.

  The electric motor (110) includes a stator (111) and a rotor (112). The stator (111) is fixed to the casing (11). The rotor (112) is inserted inside the stator (111). The drive shaft (100) is inserted through the rotor (112).

  The drive shaft (100) includes a main shaft portion (101), an eccentric portion (102), a lower end shaft portion (103), and a balance weight (104). The eccentric part (102) protrudes from the upper end surface of the main shaft part (101), and its central axis is eccentric with respect to the central axis of the main shaft part (101). The balance weight (104) is disposed at a portion near the upper end of the main shaft (101). The main shaft portion (101) has a portion above the balance weight (104) passing through the housing member (70) of the compression mechanism (20), and this portion is rotatably supported by the housing member (70). Yes. The lower end shaft portion (103) projects from the lower end surface of the main shaft portion (101), and the central axis thereof coincides with the central axis of the main shaft portion (101).

  The drive shaft (100) is formed with an in-shaft passage (105), an upper branch passage (106), and a lower branch passage (107). The in-axis passage (105) extends along the central axis of the main shaft portion (101). In addition, one end of the in-axis passage (105) opens at the lower end surface of the lower end shaft portion (103), and the other end opens at the upper end surface of the eccentric portion (102). The upper branch passage (106) is formed in a portion of the main shaft portion (101) that passes through the housing member (70). The upper branch passage (106) is a passage extending in the radial direction of the main shaft portion (101), one end thereof communicating with the in-shaft passage (105), and the other end opened to the outer peripheral surface of the main shaft portion (101). is doing. The lower branch passage (107) is formed in the lower end shaft portion (103). The lower branch passage (107) is a passage extending in the radial direction of the lower end shaft portion (103), one end thereof communicating with the in-shaft passage (105), and the other end being an outer periphery of the lower end shaft portion (103). Open to the surface.

  The lower bearing member (115) is formed in a substantially flat plate shape and is fixed to the casing (11). The lower bearing member (115) has a through hole formed in the center thereof, and the bearing metal (116) is press-fitted into the through hole. The lower end shaft portion (103) of the drive shaft (100) is inserted into the bearing metal (116). The lower bearing member (115) constitutes a journal bearing that rotatably supports the lower end shaft portion (103) of the drive shaft (100).

  Two oil pumps (127, 128) are provided on the lower end shaft portion (103) of the drive shaft (100). Specifically, the lower end shaft portion (103) is provided with a lubrication pump (127) and a cooling pump (128). As shown in FIG. 5, these oil pumps (127, 128) are trochoid pumps which are a kind of positive displacement pump. In both the oil pumps (127, 128), the outer rotor (124) is rotatably accommodated inside the cylindrical housing (121). A suction port (122) and a discharge port (123) are formed on the end surface of the cylindrical housing (121). The suction port (122) is immersed in refrigeration oil stored at the bottom of the casing (11). An inner rotor (125) is accommodated inside the outer rotor (124). A fluid chamber (126) is formed between the inner rotor (125) and the outer rotor (124). The rotating shaft of the inner rotor (125) is eccentric with respect to the rotating shaft of the outer rotor (124). The inner rotor (125) is directly connected to the drive shaft (100) or connected to the drive shaft (100) through a gear or the like, and is rotationally driven by the drive shaft (100). When the inner rotor (125) rotates, the refrigeration oil is sucked into the fluid chamber (126) through the suction port (122), and the refrigeration oil in the fluid chamber (126) is pushed out to the discharge port (123).

  The discharge port (123) of the lubrication pump (127) is connected to the inlet end of the in-shaft passage (105). When the lubrication pump (127) is driven to rotate, the refrigerating machine oil stored in the internal space of the casing (11) is sent to the in-shaft passage (105), and the bearing and the compression mechanism (20 ) Is used to lubricate sliding parts.

<Compression mechanism>
The detailed structure of the compression mechanism (20) will be described with reference to FIGS.

  As described above, the compression mechanism (20) includes the fixed scroll (30), the orbiting scroll (50), and the housing member (70). In the compression mechanism (20), the fixed scroll (30) is placed on the housing member (70), and the orbiting scroll (50) is placed in the space surrounded by the fixed scroll (30) and the housing member (70). Contained.

  As shown in FIG. 3, the housing member (70) includes a housing main body (71) and a central bulge (74), and is fixed to the casing (11). The housing body (71) includes a disk part (72) and an outer edge part (73). The disc part (72) is formed in a thick disc shape. The outer edge portion (73) is formed in a cylindrical shape with a short wall thickness, and extends upward in FIG. 3 from the outer edge portion of the disk portion (72). The outer peripheral surface of the housing main body portion (71) (that is, the outer peripheral surface of the disc portion (72) and the outer edge portion (73)) is in close contact with the inner peripheral surface of the casing (11). On the other hand, the central bulging portion (74) is formed in a thick disk shape as a whole, and bulges downward from the back surface (lower surface in FIG. 3) of the disk portion (72).

  In the housing member (70), a through hole is formed in the central portion of the central bulge portion (74), and the bearing metal (82) is press-fitted into the through hole. The main shaft portion (101) of the drive shaft (100) is inserted through the bearing metal (82). The housing member (70) constitutes a journal bearing that rotatably supports the main shaft portion (101) of the drive shaft (100).

  Further, in the housing member (70), a central concave portion (75) and an annular convex portion (76) are formed in the disc portion (72) of the housing main body portion (71). The central recess (75) is a bottomed recess that opens to the front surface (upper surface in FIG. 3) of the disk portion (72), and has a circular cross section perpendicular to the axial direction. The through hole of the central bulging portion (74) into which the bearing metal (82) is inserted opens at the bottom surface of the central concave portion (75). The annular convex portion (76) is formed along the outer peripheral edge of the central concave portion (75) and protrudes from the front surface (upper surface in FIG. 3) of the disc portion (72). The protruding end surface (upper surface in FIG. 3) of the annular convex portion (76) is formed in a plane and is in sliding contact with the orbiting scroll (50).

  The annular convex portion (76) is formed with an annular groove (77) that opens to the protruding end surface. The annular groove (77) is an annular groove extending in the circumferential direction of the annular convex portion (76), and constitutes a recess that opens in a sliding contact surface with the orbiting scroll (50). Further, an annular groove concentric with the annular groove (77) is formed on each of the inside and outside of the annular groove (77) on the projecting end surface of the annular protrusion (76). The inner seal ring (80) is fitted into the inner groove of the annular groove (77), and the outer seal ring (81) is fitted into the outer groove of the annular groove (77). The inner seal ring (80) and the outer seal ring (81) constitute a seal member that surrounds the annular groove (77) that is a recess.

  The fixed scroll (30) includes a fixed-side main body member (31) and a fixed-side back member (35). The fixed-side body member (31) includes a fixed-side flat plate portion (32), a fixed-side wrap (33), and an outer peripheral portion (34).

  The fixed-side flat plate portion (32) is generally formed in a disc shape. The fixed side wrap (33) is erected on the front surface (the lower surface in FIG. 3) of the fixed side flat plate portion (32). As shown in FIG. 4, the fixed side wrap (33) is formed in a wall shape extending spirally from the vicinity of the center of the fixed side flat plate portion (32) toward the outer peripheral side. The outer peripheral part (34) is formed in a cylindrical shape with a short wall thickness, and extends downward from the peripheral part of the fixed-side flat plate part (32) in FIG. The outer peripheral portion (34) surrounds the outer peripheral side of the fixed side wrap (33).

  The fixed-side main body member (31) is placed on the housing member (70) in such a posture that the tip (lower end in FIG. 3) of the fixed-side wrap (33) faces the housing member (70) side. The stationary-side main body member (31) is fixed to the housing member (70) with bolts or the like. In this state, the protruding end surface (lower surface in FIG. 3) of the outer peripheral portion (34) of the fixed scroll (30) is in close contact with the protruding end surface (upper surface in FIG. 3) of the outer edge portion (73) of the housing member (70). .

  The fixed-side back member (35) is formed in a generally disc shape and is placed on the fixed-side main body member (31). Specifically, the fixed-side back member (35) is overlaid on the fixed-side flat plate portion (32) of the fixed-side main body member (31), and the back surface (the upper surface in FIG. 3) of the fixed-side flat plate portion (32). ) Is covered throughout. The fixed-side back member (35) is fixed to the fixed-side main body member (31) with a bolt or the like. In the fixed scroll (30), the fixed-side flat plate portion (32) and the fixed-side back member (35) of the fixed-side main body member (31) constitute a fixed-side end plate portion (36).

  The fixed scroll (30) is formed with a suction port (21) and a discharge port (22). The suction port (21) is formed in the outer peripheral part (34) of the stationary main body member (31), and penetrates the outer peripheral part (34) in the radial direction. One end of the suction pipe (12) is inserted into the suction port (21). The discharge port (22) is formed at the center of the fixed side end plate portion (36). The discharge port (22) penetrates the fixed-side back member (35) and the fixed-side flat plate portion (32) of the fixed-side main body member (31) in the respective thickness directions.

  A check valve (25) is attached to the fixed scroll (30). The check valve (25) includes a valve body (26) and a valve presser (27), and is installed on the back surface (upper surface in FIG. 3) of the fixed-side back member (35). The check valve (25) is for closing the discharge port (22) while the scroll compressor (171) is stopped. During the operation of the scroll compressor (171), the discharge port (22) is always kept open.

  The orbiting scroll (50) includes an orbiting side main body member (51) and an orbiting side back member (54). Further, the turning side body member (51) includes a turning side flat plate portion (52) and a turning side wrap (53).

  The turning side flat plate portion (52) is formed in a substantially disc shape. The turning side wrap (53) is erected on the front surface (upper surface in FIG. 3) of the turning side flat plate portion (52). The turning side wrap (53) is formed in a wall shape extending spirally from the vicinity of the center of the turning side flat plate portion (52) toward the outer peripheral side.

  The turning-side back member (54) is generally formed in a disc shape and covers the entire back surface (the lower surface in FIG. 3) of the turning-side flat plate portion (52). That is, in the orbiting scroll (50), the orbiting side main body member (51) is placed on the orbiting side rear member (54). Further, the turning-side back member (54) is fixed to the turning-side main body member (51) with a bolt or the like. In the orbiting scroll (50), the orbiting side flat plate portion (52) and the orbiting side rear member (54) of the orbiting side main body member (51) constitute an orbiting side end plate portion (56).

  A cylindrical convex portion (55) is formed integrally with the turning-side back member (54). The cylindrical convex portion (55) is formed in a cylindrical shape and protrudes from the rear surface (the lower surface in FIG. 3) of the turning-side rear member (54). A bearing metal (57) is press-fitted into the cylindrical convex portion (55). An eccentric part (102) of the drive shaft (100) is inserted into the bearing metal (57) from the protruding end side (lower end side in FIG. 3) of the cylindrical convex part (55). Further, on the inner side of the cylindrical convex portion (55), an upper end space (66) is formed above the upper end surface of the eccentric portion (102) of the drive shaft (100). The upper end space (66) communicates with the in-axis passage (105) opened at the upper end surface of the eccentric part (102).

  The orbiting scroll (50) has its orbiting side wrap (53) meshed with the fixed side wrap (33) of the fixed scroll (30). The fixed scroll (30) and the orbiting scroll (50) are surrounded by a fixed side end plate (36), a fixed side wrap (33), a revolving side end plate (56), and a revolving side wrap (53). A compressed compression chamber (23) is formed.

  The orbiting scroll (50) is placed on the annular convex portion (76) of the housing member (70), and the rear surface (the lower surface in FIG. 3) of the orbiting side rear member (54) is the annular convex portion ( 76) is in sliding contact with the protruding end surface (the upper surface in FIG. 3). However, the annular convex portion (76) of the housing member (70) and the turning-side back member (54) are not in physical contact, and a minute gap is formed between them. And the clearance gap between the cyclic | annular convex part (76) of a housing member (70) and the turning side back member (54) is sealed by the inner side seal ring (80) and the outer side seal ring (81).

  An Oldham coupling (89) is provided between the orbiting scroll (50) and the housing member (70). The Oldham joint (89) constitutes a rotation prevention mechanism (88). That is, the Oldham coupling (89) is slidably engaged with both the orbiting scroll (50) and the housing member (70), and regulates the rotation of the orbiting scroll (50).

<Cooling fluid circuit, fixed passage, swivel passage>
As described above, the scroll compressor (171) is provided with the cooling fluid circuit (180). In the cooling fluid circuit (180), refrigeration oil (that is, lubricating oil) flows as a cooling fluid. The fixed scroll (30) is formed with a fixed side passage (40) for flowing a cooling fluid, and the orbiting scroll (50) is formed with a turning side passage (60) for flowing a cooling fluid. Has been.

  As shown in FIGS. 3 and 4, the fixed scroll (30) includes an in-lap passage (41), an end plate passage (42), a main body side passage (45), an introduction passage (43), A lead-out passage (44) is formed, and these constitute a fixed-side passage (40).

  The in-lap passage (41) and the end plate passage (42) are formed in the stationary-side main body member (31). The wrap passage (41) is a relatively deep and narrow groove-shaped passage that opens to the back surface of the fixed-side flat plate portion (32), and extends from the fixed-side flat plate portion (32) to the fixed-side wrap (33). It is formed over. The in-wrap passage (41) is formed in a spiral shape along the fixed-side wrap (33). The end plate passage (42) is a relatively shallow and wide groove-like passage that opens at the back of the fixed-side flat plate portion (32), and is formed only in the fixed-side flat plate portion (32). The end plate passage (42) is formed in a spiral shape along the lap passage (41). The in-lap passage (41) and the end plate passage (42) are covered with a fixed-side back member (35).

  The main body side communication path (45) is formed in the outer peripheral portion (34) of the fixed side main body member (31). One end of the main body side communication path (45) opens on the back surface (upper surface in FIG. 3) of the fixed main body member (31), and the other end opens on the outer peripheral surface of the outer peripheral portion (34). The first oil introduction pipe (17) is inserted into the other end of the main body side communication path (45).

  The introduction passage (43) and the lead-out passage (44) are formed in the fixed-side back member (35). The introduction passage (43) includes a main body side communication passage (45) that opens to the back surface of the fixed-side main body member (31), and end portions on the outermost peripheral side of the inner wrap passage (41) and the end plate passage (42). Connected. One end of the lead-out passage (44) communicates with the innermost peripheral end of the lap passage (41) and the end plate passage (42), and the other end opens on the outer peripheral surface of the fixed rear member (35). is doing. That is, the outlet passage (44) communicates with the internal space of the casing (11) at the other end.

  As shown in FIG. 3, the orbiting scroll (50) is formed with an in-lap passage (61), an end plate passage (62), an introduction passage (63), and an outlet passage (64). These constitute the turning side passageway (60).

  The in-lap passage (61) and the end plate passage (62) are formed in the turning-side main body member (51). The in-lap passage (61) is a relatively deep and narrow groove-like passage that opens at the back of the turning-side flat plate portion (52), and extends from the turning-side flat plate portion (52) to the turning-side wrap (53). It is formed over. The in-lap passage (61) is formed in a spiral shape along the turning side wrap (53). The end plate passage (62) is a relatively shallow and wide groove-shaped passage that opens at the back of the turning-side flat plate portion (52), and is formed only in the turning-side flat plate portion (52). The end plate passage (62) is formed in a spiral shape along the in-lap passage (61). The in-lap passage (61) and the end plate passage (62) are covered by the turning-side back member (54).

  The introduction passage (63) and the lead-out passage (64) are formed in the turning side rear member (54). One end of the introduction passage (63) communicates with the outermost peripheral end portions of the in-lap passage (61) and the end plate passage (62), and the other end is the back surface of the turning-side back member (54) (in FIG. 3). Open on the bottom surface. The other end of the introduction passage (63) communicates with the annular groove (77) of the housing member (70). One end of the lead-out passage (64) communicates with the innermost peripheral end of the in-lap passage (61) and the end plate passage (62), and the other end is the back surface of the turning-side back member (54) (FIG. 3). Open on the lower surface). The other end of the lead-out passage (64) communicates with the cylindrical space (78) in the central recess (75) of the housing member (70).

  The introduction passage (63) formed in the orbiting scroll (50) always communicates with the annular groove (77) regardless of the position of the orbiting scroll (50). Specifically, the opening end of the introduction passage (63) on the back surface of the turning-side back member (54) has a circular shape. On the other hand, the radial width W of the annular groove (77) is the sum (r1 + r2) of the radius r1 of the opening end of the introduction passage (63) and the revolution radius r2 of the orbiting scroll (50) on the back surface of the orbiting back member (54). ) Twice or more (W ≧ 2 (r1 + r2)). Therefore, even during the revolution of the orbiting scroll (50), the introduction passage (63) always communicates with the annular groove (77).

  The housing member (70) is formed with a connection passage (83) and a discharge passage (85). One end of the connection passage (83) opens on the bottom surface of the annular groove (77), and the other end opens on the outer peripheral surface of the outer edge (73). The second oil introduction pipe (18) is inserted into the other end of the connection passage (83). One end of the discharge passage (85) opens near the lower end of the wall surface of the central recess (75) of the housing member (70), and the other end opens on the outer surface of the housing member (70). That is, the discharge passage (85) allows the cylindrical space (78) in the central recess (75) to communicate with the outside of the compression mechanism (20) in the internal space of the casing (11).

  As described above, the oil outlet pipe (14) is provided in the casing (11) of the scroll compressor (171) (see FIG. 2). The oil outlet pipe (14) passes through the lower part of the casing (11). The oil outlet pipe (14) has one end connected to the discharge port (123) of the cooling pump (128) and the other end connected to the inlet end of the upstream cooler (181). A fixed side branch (182) and a swirl side branch (183) are provided on the outflow side of the upstream cooler (181). The fixed side branch (182) is connected to the first oil introduction pipe (17), and the turning side branch (183) is connected to the second oil introduction pipe (18). A first flow rate control valve (184) is provided in the fixed side branch channel (182), and a second flow rate control valve (185) is provided in the turning side branch channel (183). These flow rate control valves (184, 185) are constituted by electrically operated valves whose opening degree can be adjusted.

  In the cooling fluid circuit (180), the passage from the oil outlet pipe (14) to the branching portion of the stationary side branch (182) and the swirl side branch (183) has one main flow through which the cooling fluid flows. An introduction passage (190) is formed. Further, in the cooling fluid circuit (180), a first branch passage (191) is formed from the fixed side branch passage (182) to the passage inside the first oil introduction pipe (17), and the swirl side branch passage (183) To the passage inside the second oil introduction pipe (18) constitutes a second branch passage (192). Furthermore, the first flow rate control valve (184) and the second flow rate control valve (185) are flow rate controls for controlling the flow rate of the cooling fluid flowing through the first branch passage (191) and the second branch passage (192). The mechanism (186) is configured.

  In the scroll compressor (171), the cooling pump (128), the main introduction passage (190), the first branch passage (191), the second branch passage (192), the fixed side passage (40), A cooling fluid circuit (180) is formed by a passage including the connection passage (83), the annular groove (77), the turning side passage (60), the cylindrical space (78), and the discharge passage (85). Is composed. In the cooling fluid circuit (180), the refrigeration oil stored in the internal space of the casing (11) flows as a cooling fluid. The refrigerating machine oil flowing as a cooling fluid in the cooling fluid circuit (180) is cooled in the upstream cooler (181), and then sequentially passes through the turning side passage (60) and the fixed side passage (40). Heat is absorbed from the scroll (50) and the fixed scroll (30). A part of the refrigerating machine oil flowing through the cooling fluid circuit (180) is also used for lubricating the bearing of the drive shaft (100) and the sliding portion of the compression mechanism (20).

-Driving action-
The operation of the air conditioner (150) and the operation of the scroll compressor (171) provided therein will be described.

<Operation of air conditioner>
The air conditioner (150) performs switching between cooling operation and heating operation.

  First, the cooling operation of the air conditioner (150) will be described. During the cooling operation, the four-way switching valve (174) is set to the first state (the state indicated by the solid line in FIG. 1), the outdoor heat exchanger (172) operates as a condenser, and the indoor heat exchangers (176a, 176b) Operates as an evaporator. Specifically, the refrigerant discharged from the scroll compressor (171) dissipates heat to the outdoor air in the outdoor heat exchanger (172), condenses, and is then distributed to the indoor circuits (175a, 175b). The refrigerant flowing into each indoor circuit (175a, 175b) is depressurized when passing through the indoor expansion valve (177a, 177b), then flows into the indoor heat exchanger (176a, 176b), and absorbs heat from the indoor air. Evaporate. The indoor units (153a, 153b) supply indoor air cooled when passing through the indoor heat exchangers (176a, 176b) to the room. The refrigerant evaporated in each indoor heat exchanger (176a, 176b) returns to the outdoor circuit (170) and is sucked into the scroll compressor (171).

  Next, the heating operation of the air conditioner (150) will be described. During the heating operation, the four-way switching valve (174) is set to the second state (the state indicated by the broken line in FIG. 1), the indoor heat exchangers (176a, 176b) operate as condensers, and the outdoor heat exchanger (172) Operates as an evaporator. Specifically, the refrigerant discharged from the scroll compressor (171) is distributed to each indoor circuit (175a, 175b), and is radiated to the indoor air by the indoor heat exchanger (176a, 176b) and condensed. The indoor units (153a, 153b) supply indoor air heated when passing through the indoor heat exchangers (176a, 176b) to the room. The refrigerant condensed in each indoor circuit (175a, 175b) is depressurized when returning to the outdoor circuit (170) and passing through the outdoor expansion valve (173), and then absorbs heat from the outdoor air in the outdoor heat exchanger (172). Then evaporate. The refrigerant evaporated in the outdoor heat exchanger (172) is sucked into the scroll compressor (171).

<Operation of scroll compressor>
The operation of the scroll compressor (171) will be described.

  When the electric motor (110) is energized, the orbiting scroll (50) engaged with the drive shaft (100) is driven. The orbiting scroll (50) does not rotate but only revolves. When the orbiting scroll (50) revolves, the volume of the compression chamber (23) formed with the fixed scroll (30) changes, and the low-pressure gas flowing into the compression mechanism (20) through the suction pipe (12) The refrigerant is sucked into the compression chamber (23). The gas refrigerant sucked into the compression chamber (23) is compressed to become high-pressure gas refrigerant, and is discharged to the internal space of the casing (11) through the discharge port (22). The high-pressure gas refrigerant in the casing (11) passes through the discharge pipe (13) and is discharged to the outside of the casing (11).

  When the drive shaft (100) rotates, the lubrication pump (127) and the cooling pump (128) are driven by the drive shaft (100). The lubrication pump (127) sucks the refrigeration oil stored in the internal space of the casing (11), and pushes out the sucked refrigeration oil to the in-shaft passage (105). A part of the refrigerating machine oil pushed out to the in-shaft passage (105) flows into the lower branch passage (107) and the upper branch passage (106), and the rest flows into the upper end space (66).

  The refrigerating machine oil that has flowed into the lower branch passage (107) is supplied to the gap between the bearing metal (116) and the drive shaft (100) provided in the lower bearing member (115) and used for lubrication. The refrigerating machine oil that has flowed into the upper branch passage (106) is supplied to the gap between the bearing metal (82) and the drive shaft (100) provided in the housing member (70) and used for lubrication. A part of the refrigerating machine oil flowing into the upper end space (66) is supplied to the gap between the bearing metal (57) and the eccentric part (102) provided in the orbiting scroll (50) and used for lubrication.

  The cooling pump (128) sucks the refrigerating machine oil stored in the internal space of the casing (11), and pushes the sucked refrigerating machine oil into the oil outlet pipe (14). The refrigerating machine oil discharged to the oil outlet pipe (14) flows into the upstream cooler (181) and dissipates heat to the outdoor air. That is, in the upstream cooler (181), the refrigeration oil is cooled by the outdoor air. The refrigerating machine oil cooled in the upstream side cooler (181) is divided into the fixed side branch (182) and the swirl side branch (183).

  The refrigerating machine oil that has flowed into the fixed side branch passage (182) sequentially passes through the first oil introduction pipe (17), the main body side communication passage (45), and the introduction passage (43), and then the passage in the wrap (41). It distributes to the end plate passage (42). The refrigerating machine oil that has flowed into the wrap inner passage (41) and the end plate inner passage (42) flows from the outer peripheral end portion toward the inner peripheral end portion, and absorbs heat from the fixed scroll (30). Thereafter, the refrigeration oil flows into the lead-out passage (44), flows out from the terminal end of the lead-out passage (44) to the internal space of the casing (11), and flows down to the bottom of the casing (11).

  The refrigerating machine oil that has flowed into the swirl side branch passage (183) passes through the second oil introduction pipe (18) and the connection passage (83) in this order, and then flows into the annular groove (77). The refrigerating machine oil flowing into the annular groove (77) is distributed to the in-lap passage (61) and the end plate passage (62) after passing through the introduction passage (63). The refrigerating machine oil that has flowed into the lap inner passage (61) and the end plate inner passage (62) flows from the outer peripheral end to the inner peripheral end, and absorbs heat from the orbiting scroll (50). Thereafter, the refrigerating machine oil flows into the cylindrical space (78) in the central recess (75) through the outlet passage (64). The refrigeration oil that has flowed into the cylindrical space (78) flows into the discharge passage (85), flows out from the end of the discharge passage (85) to the internal space of the casing (11), and flows down to the bottom of the casing (11). Go.

  Thus, in the cooling fluid circuit (180) of the scroll compressor (171), the orbiting side passage (60) of the orbiting scroll (50) and the fixed side passage (40) of the fixed scroll (30) are arranged in parallel. Has been placed. Here, in the present embodiment, the first flow control valve (184) is provided in the first branch passage (191), and the second flow control valve (185) is provided in the second branch passage (192). For this reason, the flow rate of the refrigerating machine oil flowing through the fixed side passage (40) and the flow rate of the refrigerating machine oil flowing through the turning side passage (60) can be adjusted equally by adjusting the opening degree of these flow rate control valves (184, 185) . That is, each flow control valve (184, 185) functions as a drift prevention mechanism for preventing the refrigeration oil from drifting to one of the fixed side passage (40) and the turning side passage (60).

  The annular groove (77) of the housing member (70) is formed over the entire circumference of the annular convex portion (76). The refrigerating machine oil that has passed through the orbiting scroll (50) of the orbiting scroll (50) flows into the annular groove (77). The pressure of the refrigerating machine oil flowing into the annular groove (77) is higher than the pressure in the internal space of the casing (11) (that is, the pressure of the high-pressure gas refrigerant discharged from the compression mechanism (20)). An annular groove (77) is formed in a portion between the inner seal ring (80) and the outer seal ring (81) on the rear surface (lower surface in FIG. 3) of the orbiting side rear member (54) of the orbiting scroll (50). The pressure of the refrigeration oil that flows into As a result, a force pressing the orbiting scroll (50) toward the fixed scroll (30) acts on the orbiting scroll (50), and the airtightness of the compression chamber (23) is ensured. That is, in the scroll compressor (171), the refrigerating machine oil flowing through the cooling fluid circuit (180) to cool the fixed scroll (30) and the orbiting scroll (50) is fixed to the orbiting scroll (50). 30) It is also used to apply a pressing force to the side.

-Effect of Embodiment 1-
In the scroll compressor (171) of the present embodiment, the fixed side passage (40) formed in the fixed scroll (30) and the orbiting side passage (60) formed in the orbiting scroll (50) include a cooling fluid. The circuits (180) are arranged in parallel to each other. For this reason, it is possible to cool both the fixed scroll (30) and the orbiting scroll (50) while relatively reducing the flow resistance of the passage through which the cooling fluid flows. On the other hand, when the turning-side passage (60) and the fixed-side passage (40) are arranged in parallel as described above, the cooling that flows through the passage having the larger flow resistance of the fixed-side passage (40) and the turning-side passage (60). There is a risk of insufficient fluid flow. However, in the present embodiment, the first branch passage (191) for supplying the cooling fluid to the stationary side passage (40) and the second branch passage for supplying the cooling fluid to the turning side passage (60). (192) and a flow control valve (184, 185), respectively. For this reason, by adjusting the opening degree of these flow rate control valves (184, 185), the flow rate of the refrigerating machine oil flowing through the fixed side passage (40) as the cooling fluid and the swirl side passage (60) flows as the cooling fluid. The flow rate of the refrigerating machine oil can be made equal. Therefore, the flow rate of the refrigerating machine oil as the cooling fluid is not biased to one of the fixed side passage (40) and the swivel side passage (60), and both the fixed side passage (40) and the swivel side passage (60) And a sufficient amount of refrigerating machine oil can be reliably supplied. Therefore, according to the scroll compressor (171) of the present embodiment, it is possible to reliably cool both the fixed scroll (30) and the orbiting scroll (50), and as a result, the compression is performed in the compression mechanism (20). It is possible to reliably suppress the temperature rise of the gas refrigerant.

  Further, in the scroll compressor (171) of the present embodiment, the refrigerating machine oil stored in the internal space of the casing (11) not only lubricates the compression mechanism (20) but also the fixed scroll (30) and the orbiting scroll. It is also used as a cooling fluid for cooling (50). That is, in the present embodiment, the refrigerating machine oil necessary for the operation of the compression mechanism (20) is used as the cooling fluid even when the fixed scroll (30) and the orbiting scroll (50) are not cooled. Therefore, according to this embodiment, the complexity of the configuration of the scroll compressor (171) due to cooling of the fixed scroll (30) and the orbiting scroll (50) can be suppressed.

  In addition, the air conditioner (150) of the above embodiment includes a scroll compressor (171), an outdoor heat exchanger (172) that exchanges heat between the refrigerant and outdoor air, and an indoor heat exchange that exchanges heat between the refrigerant and indoor air. The refrigerant circuit (160) connected to the compressors (176a, 176b), the scroll compressor (171) sucks and compresses the gas refrigerant as the compressed gas, and the refrigerant circuit (160) performs the refrigeration cycle. An indoor air exchanger (176a, 176b) and an indoor fan (154a, 154b) for supplying indoor air to the indoor heat exchanger (176a, 176b) An outdoor unit in which a unit (153a, 153b), a scroll compressor (171), an outdoor heat exchanger (172), and an outdoor fan (152) for supplying outdoor air to the outdoor heat exchanger (172) are installed An upstream cooler provided with a scroll compressor (171) 181) cools the cooling fluid by exchanging heat with outdoor air, and in the outdoor unit (151), the outdoor fan (152) is connected to the outdoor heat exchanger (172) and the upstream side cooler (181). Supply outdoor air to both. Therefore, according to this embodiment, compared with the case where the fan for supplying outdoor air to the upstream cooler (181) of the scroll compressor (171) is provided separately from the outdoor fan (152), the outdoor unit (151 ) Can be simplified.

-Modification of Embodiment 1-
In Embodiment 1 described above, the flow rate control mechanism (186) for controlling the flow rate of the cooling fluid flowing through the first branch passage (191) and the second branch passage (192) serves as a flow rate in each branch passage (191, 192). A control valve (184, 185) is provided. However, as this flow rate control mechanism, a capillary tube that imparts a predetermined flow resistance to one of the branch passages (191, 192) may be used. Specifically, for example, when the flow resistance of the fixed side passage (40) is larger than the flow resistance of the turning side passage (60), a capillary tube is provided in the second branch passage (192) connected to the turning side passage (60). Like that. Thereby, it can prevent that the flow volume of the cooling fluid supplied to a fixed side channel | path (40) runs short, and the flow volume of the cooling fluid which flows through a fixed side channel | path (40), and a swirl side channel | path (60) flow The flow rate of the cooling fluid can be made equal.

<< Embodiment 2 of the Invention >>
A second embodiment of the present invention will be described. This embodiment is obtained by changing the configuration of the cooling fluid circuit (180) in the first embodiment. Here, the difference between the scroll compressor (171) of the present embodiment and the scroll compressor (171) of the first embodiment will be described.

  As shown in FIG. 6, the scroll compressor (171) of the present embodiment is provided with three oil pumps (127, 128a, 128b) at the lower end of the drive shaft (100). Specifically, a lubrication pump (127), a first cooling pump (128a), and a second cooling pump (128b) are connected to the lower end portion of the drive shaft (100) in order from the top to the bottom. is doing. The lubrication pump (127), the first cooling pump (128a), and the second cooling pump (128b) are configured by a trochoid pump, which is a type of positive displacement pump, like the oil pump of the first embodiment. . In the first cooling pump (128a) and the second cooling pump (128b), the volume of fluid flowing out from the discharge port (123) per revolution (so-called displacement volume) is equal.

  The casing (11) of the present embodiment is provided with a first oil outlet pipe (15) and a second oil outlet pipe (16). One end of the first oil outlet pipe (15) is connected to the discharge port (123) of the first cooling pump (128a). The other end of the first oil outlet pipe (15) is connected to the first oil introduction pipe (17). One end of the second oil outlet pipe (16) is connected to the discharge port (123) of the second cooling pump (128b). The other end of the second oil outlet pipe (16) is connected to the second oil introduction pipe (18).

  In the scroll compressor (171) of the second embodiment, the cooling fluid is transported across the first cooling pump (128a), the first oil outlet pipe (15), and the first oil introduction pipe (17). The first supply passage (193) is formed. In the scroll compressor (171), the second cooling pump (128b), the second oil lead-out pipe (16), and the second oil introduction pipe (18) are transported through the first cooling fluid for conveying the cooling fluid. Two supply passages (194) are formed. That is, the first cooling pump (128a) constitutes a first transfer mechanism that is included in the first supply passage (193) and transfers the cooling fluid. The second cooling pump (128b) constitutes a second transport mechanism that is included in the second supply passage (194) and transports the cooling fluid.

  In the second embodiment, one upstream-side cooler (181a, 181b) is provided in each of the first supply passage (193) and the second supply passage (194). Specifically, the first supply passage (193) is provided with a first upstream cooler (181a), and the second supply passage (194) is provided with a second upstream cooler (181b). ing. These upstream side coolers (181a, 181b) have the same configuration as the upstream side cooler (181) of the first embodiment. In the outdoor unit (151) of the second embodiment, the outdoor fan (152) with respect to the outdoor heat exchanger (172), the first upstream cooler (181a), and the second upstream cooler (181b). To supply outdoor air.

  In the second embodiment, when the drive shaft (100) rotates, the lubrication pump (127), the first cooling pump (128a), and the second cooling pump (128b) are driven by the drive shaft (100). The lubrication pump (127) sucks the refrigeration oil stored in the internal space of the casing (11), and pushes out the sucked refrigeration oil to the in-shaft passage (105). A part of the refrigerating machine oil pushed out to the in-shaft passage (105) flows into the lower branch passage (107) and the upper branch passage (106), and the rest flows into the upper end space (66). As a result, the bearing of the drive shaft (100) is lubricated as in the first embodiment.

  The first cooling pump (128a) sucks the refrigeration oil stored in the internal space of the casing (11), and pushes out the sucked refrigeration oil to the first oil outlet pipe (15). The refrigerating machine oil discharged to the first oil outlet pipe (15) flows into the first upstream cooler (181a) and radiates heat to the outdoor air. That is, in the first upstream cooler (181a), the refrigeration oil is cooled by the outdoor air. The refrigerating machine oil cooled in the first upstream cooler (181a) flows into the fixed passage (40) from the first oil introduction pipe (17).

  The refrigerating machine oil that has flowed into the fixed side passage (40) passes through the main body side communication passage (45) and the introduction passage (43) in this order, and is then distributed to the lap passage (41) and the end plate passage (42). The The refrigerating machine oil that has flowed into the wrap inner passage (41) and the end plate inner passage (42) flows from the outer peripheral end portion toward the inner peripheral end portion, and absorbs heat from the fixed scroll (30). Thereafter, the refrigeration oil flows into the lead-out passage (44), flows out from the terminal end of the lead-out passage (44) to the internal space of the casing (11), and flows down to the bottom of the casing (11).

  The second cooling pump (128b) sucks the refrigerating machine oil stored in the internal space of the casing (11), and pushes out the sucked refrigerating machine oil to the second oil outlet pipe (16). The refrigerating machine oil discharged to the second oil outlet pipe (16) flows into the second upstream cooler (181b) and dissipates heat to the outdoor air. That is, in the second upstream side cooler (181b), the refrigeration oil is cooled by the outdoor air. The refrigerating machine oil cooled in the second upstream cooler (181b) flows into the turning side passage (60) from the second oil introduction pipe (18).

  The refrigeration oil that has flowed into the turning side passage (60) passes through the connection passage (83) and flows into the annular groove (77). The refrigerating machine oil flowing into the annular groove (77) is distributed to the in-lap passage (61) and the end plate passage (62) after passing through the introduction passage (63). The refrigerating machine oil that has flowed into the lap inner passage (61) and the end plate inner passage (62) flows from the outer peripheral end to the inner peripheral end, and absorbs heat from the orbiting scroll (50). Thereafter, the refrigerating machine oil flows into the cylindrical space (78) in the central recess (75) through the outlet passage (64). The refrigeration oil that has flowed into the cylindrical space (78) flows into the discharge passage (85), flows out from the end of the discharge passage (85) to the internal space of the casing (11), and flows down to the bottom of the casing (11). Go.

  As described above, in the second embodiment, the first supply passage (193) for sending the refrigeration oil to the fixed side passage (40) and the second supply passage (for feeding the refrigeration oil to the turning side passage (60) ( 194) are different from each other, and the first supply passage (193) and the second supply passage (194) are individually provided with cooling pumps (128a, 128b), respectively. Yes. Here, since the first cooling pump (128a) and the second cooling pump (128b) are positive displacement pumps, regardless of the flow resistance of the fixed side passage (40) and the turning side passage (60), The cooling fluid can be conveyed at a constant flow rate. Moreover, the first cooling pump (128a) and the second cooling pump (128b) have the same displacement volume and are driven at the same rotational speed by the single drive shaft (100). For this reason, even if the flow resistance between the fixed side passage (40) and the turning side passage (60) is different, the flow rate of the refrigerating machine oil flowing through the fixed side passage (40) and the refrigeration flowing through the turning side passage (60). The flow rate of machine oil can be made equal.

-Effect of Embodiment 2-
In the scroll compressor (171) of the present embodiment, the fixed side passage (40) formed in the fixed scroll (30) and the orbiting side passage (60) formed in the orbiting scroll (50) include a cooling fluid. The circuits (180) are arranged in parallel to each other. For this reason, it is possible to cool both the fixed scroll (30) and the orbiting scroll (50) while relatively reducing the flow resistance of the passage through which the cooling fluid flows. On the other hand, when the turning-side passage (60) and the fixed-side passage (40) are arranged in parallel as described above, the cooling that flows through the passage having the larger flow resistance of the fixed-side passage (40) and the turning-side passage (60). There is a risk of insufficient fluid flow. However, in this embodiment, the first supply passage (193) including the first cooling pump (128a) is connected to the fixed-side passage (40), and the second supply passage (including the second cooling pump (128b) ( 194) is connected to the turning passage (60). For this reason, since the flow rate of the cooling fluid sent to the fixed side passage (40) and the flow rate of the cooling fluid sent to the swivel side passage (60) can be individually controlled, the cooling fluid flowing through the fixed side passage (40) And the flow rate of the cooling fluid flowing through the turning side passageway (60) can be made equal.

  In particular, in the present embodiment, the first cooling pump (128a) and the second cooling pump (128b) are constituted by positive displacement pumps having the same displacement volume, and one of these cooling pumps (128a, 128b) is provided. Connected to the drive shaft (100). Therefore, when the drive shaft (100) is driven to rotate, the flow rate of the refrigerating machine oil discharged from the first cooling pump (128a) and the flow rate of the refrigerating machine oil discharged from the second cooling pump (128b) Can be equal. As a result, the flow rate of the cooling fluid flowing through the fixed side passage (40) and the flow rate of the refrigerating machine oil flowing through the swivel side passage (60) can be made substantially equal. Further, since the drive shaft (100) for driving the two cooling pumps (128a, 128b) is shared, the structure of the apparatus can be simplified.

-Modification of Embodiment 2-
In the second embodiment, the two cooling pumps (128a, 128b) are rotationally driven by one drive mechanism (that is, the drive shaft (100) and the electric motor (110)). However, in the second embodiment, a driving mechanism for driving the two cooling pumps (128a, 128b) is individually provided, and the flow rate of the cooling fluid conveyed by each cooling pump (128a, 128b) is individually set. It is good also as a structure to control. As a result, the flow rate of the cooling fluid flowing through the fixed side passage (40) and the flow rate of the cooling fluid flowing through the turning side passage (60) can be adjusted equally. The conveying means constituting the cooling pump (128a, 128b) is not limited to the trochoid pump of the second embodiment, and may be another pump such as a gear pump.

<< Other Embodiments >>
In each of the above-described embodiments, the following modified configuration may be employed.

-First modification-
As shown in FIG. 7, in the first modification, in the cooling fluid circuit (180) of the scroll compressor (171) of each of the above embodiments, the first outflow pipe (195), the second outflow pipe (196), A downstream cooler (197), a power recovery machine (198), and an injection pipe (12a) are added.

  The first outflow pipe (195) is inserted into the outlet end of the outlet passage (44) of the stationary side passage (40). The second outflow pipe (196) is inserted into the outlet end of the discharge passage (85) formed in the housing member (70). The outflow side of the first outflow pipe (195) and the outflow side of the second outflow pipe (196) are combined into one passage and connected to the inlet end of the downstream cooler (197). The outlet end of the downstream cooler (197) is connected to the inlet end of the power recovery machine (198). That is, the power recovery machine (198) is disposed downstream of the downstream cooler (197). The injection pipe (12a) branches off from the suction pipe (12) of the compression mechanism (20). The inlet end of the injection pipe (12a) is connected to the outlet end of the power recovery machine (198).

  The downstream cooler (197) is a fin-and-tube heat exchanger, and cools the refrigerating machine oil flowing as a cooling fluid in the cooling fluid circuit (180) by exchanging heat with outdoor air. Further, in the outdoor unit (151) of the present embodiment, not only the outdoor heat exchanger (172) and the upstream side cooler (181) but also the downstream side cooler (197) is outdoors by an outdoor fan (152). Air is supplied.

  The power recovery machine (198) is constituted by a fluid machine such as a rotary fluid machine, and is driven by refrigerating machine oil flowing in the cooling fluid circuit (180). The power recovery machine (198) constitutes an oil energy recovery mechanism that converts the energy of the refrigerating machine oil flowing through the cooling fluid circuit (180) into rotational power. Although not shown, a power generator is connected to the power recovery machine (198). The rotational power recovered when the high pressure oil is depressurized by the power recovery machine (198) is used to drive the generator. That is, the energy of the refrigerating machine oil flowing through the cooling fluid circuit (180) is converted into electric power. Electric power generated in the generator connected to the power recovery machine (198) is supplied to the electric motor (110) of the scroll compressor (171) to drive the compression mechanism (20) together with electric power supplied from the commercial power source. Used for

  In the cooling fluid circuit (180) of the present embodiment, the refrigerating machine oil flowing as the cooling fluid is separated into the swirl side passage (60) and the fixed side passage (40) after being cooled in the upstream side cooler (181). The heat is absorbed from the orbiting scroll (50) and the fixed scroll (30).

  The refrigerating machine oil that has flowed out of the fixed side passage (40) and passed through the first outflow pipe (195) and the refrigerating machine oil that has flowed out of the discharge passage (85) and passed through the second outflow pipe (196) merged. Later, it flows through the downstream cooler (197). In the downstream cooler (197), the refrigeration oil radiates heat to the outdoor air. The refrigeration oil that has flowed out of the downstream cooler (197) drives the power recovery machine (198). The refrigerating machine oil whose pressure has dropped when passing through the power recovery machine (198) is supplied to the low-pressure gas refrigerant flowing through the suction pipe (12) through the injection pipe (12a), and the compression mechanism ( 20) is sucked into the compression chamber (23).

  As described above, in the cooling fluid circuit (180) of the present embodiment, the refrigerating machine oil cooled in the downstream cooler (197) is combined with the low-pressure gas refrigerant flowing through the suction pipe (12) of the compression mechanism (20). Inhaled into the compression chamber (23). The refrigerating machine oil sucked into the compression mechanism (20) together with the gas refrigerant directly contacts the gas refrigerant being compressed in the compression mechanism (20) and absorbs heat from the gas refrigerant. Therefore, according to this embodiment, the refrigerating machine oil cooled in the upstream side cooler (181) is supplied to the fixed side passage (40) and the orbiting side passage (60), and the fixed scroll (30) and the orbiting scroll (50) are supplied. In the compression chamber (23) of the compression mechanism (20) not only by cooling) but also by sucking the refrigeration oil cooled in the downstream side cooler (197) together with the gas refrigerant into the compression mechanism (20). The temperature rise of the gas refrigerant being compressed can be suppressed.

  Here, in the cooling fluid circuit (180) of the present embodiment, the suction port (122) of the cooling pump (128) serving as the starting end thereof is a refrigerating machine oil (that is, a compression mechanism) stored in the casing (11). (20) is immersed in the high-pressure gas refrigerant discharged from the high-pressure gas refrigerant, and the downstream-side oil introduction pipe (19) at the end of the oil is introduced into the suction pipe (12) (ie, compressed) This is connected to the portion through which the low-pressure gas refrigerant sucked into the mechanism (20) flows. That is, in this cooling fluid circuit (180), the pressure at the start end is substantially equal to the pressure of the high-pressure gas refrigerant discharged from the compression mechanism (20), and the pressure at the end is sucked into the compression mechanism (20). The pressure of the low-pressure gas refrigerant is substantially equal. Therefore, in the cooling fluid circuit (180) of the present embodiment, the pressure difference between the start and end can be used as the driving force for flowing the refrigerating machine oil as the cooling fluid, and the cooling pump (128) The power required to drive the vehicle can be reduced.

-Second modification-
In the scroll compressor (171) of each embodiment described above, a mechanism other than the Oldham coupling (89) may be used as the rotation prevention mechanism (88). Here, the rotation prevention mechanism (88) of this modification will be described by taking as an example the case where it is applied to the scroll compressor (171) of the first embodiment.

  The rotation prevention mechanism (88) of the present modification is configured by at least three joint units (90). As shown in FIG. 8, each joint unit (90) includes one fixed-side pin (91), one turning-side pin (92), and one cylindrical member (93), and the turning-side end plate of the turning scroll (50). The portions (56) are arranged at equiangular intervals in the circumferential direction.

  The orbiting side pin (92) is formed in a columnar shape or a circular tube shape, and is attached to the orbiting scroll (50). Specifically, the turning-side pin (92) is embedded in the vicinity of the periphery of the turning-side back member (54) in a posture protruding from the back surface (the lower surface in FIG. 8) of the turning-side back member (54). The axial direction of the turning side pin (92) is substantially orthogonal to the back surface of the turning side rear member (54).

  The fixed side pin (91) is formed in a cylindrical shape or a circular tube shape, and is attached to the housing member (70). Specifically, the fixed side pin (91) is embedded in a position outside the annular convex portion (76) in a posture protruding from the front surface (upper surface in FIG. 8) of the disc portion (72) of the housing member (70). Has been. The axial direction of the fixed side pin (91) is substantially orthogonal to the front surface of the disc part (72).

  The cylindrical member (93) is formed in a relatively short cylindrical shape, and is sandwiched between the housing member (70) and the orbiting scroll (50). One end surface (lower end surface in FIG. 8) of this cylindrical member (93) is in sliding contact with the front surface of the disk portion (72) of the housing member (70), and the other end surface (upper end surface in FIG. 8) is orbiting scroll ( 50) is in sliding contact with the rear surface of the turning-side rear member (54). Further, the cylindrical member (93) is inserted with a portion of the orbiting side pin (92) protruding from the orbiting scroll (50) and a portion of the fixed side pin (91) protruding from the housing member (70). ing.

  In each joint unit (90), the outer peripheral surface of the fixed side pin (91) and the outer peripheral surface of the turning side pin (92) are in contact with the inner peripheral surface of the cylindrical member (93). The contact part with the fixed side pin (91) on the inner peripheral surface of the cylindrical member (93) and the contact part with the turning side pin (92) on the inner peripheral surface of the cylindrical member (93) are the cylindrical member (93). It is located on the opposite side across the central axis. Even if the orbiting scroll (50) moves during the operation of the scroll compressor (171), the inner peripheral surface of the cylindrical member (93) is the outer periphery of both the fixed side pin (91) and the orbiting side pin (92). As a result, the rotation of the orbiting scroll (50) is restricted.

  In addition, in the compression mechanism (20) shown in FIG. 8, the width | variety of the cyclic | annular convex part (76) formed in the housing member (70) is the cyclic | annular form formed in the compression mechanism (20) of Embodiment 1 shown in FIG. It is narrower than the convex part (76). And in the compression mechanism (20) shown in FIG. 8, the seal ring (84) is provided in the protrusion end surface of the cyclic | annular convex part (76). The seal ring (84) seals the gap between the back surface of the orbiting-side back member (54) of the orbiting scroll (50) and the projecting end surface of the annular convex portion (76).

  One of the joint units (90) provided in the compression mechanism (20) constitutes a part of the cooling fluid circuit (180). In the compression mechanism (20) shown in FIG. 8, the joint unit (90a) provided on the right side of FIG. 8 constitutes a part of the cooling fluid circuit (180).

  As shown in FIG. 9, in the joint unit (90a) constituting the cooling fluid circuit (180), each of the fixed side pin (91a) and the swivel side pin (92a) is formed in a circular tube whose both ends are open. The The internal space of the stationary pin (91a) communicates with a connection passage (83) formed in the housing member (70). The internal space of the orbiting side pin (92a) communicates with an introduction passage (63) formed in the orbiting scroll (50).

  In the joint unit (90a), the cylindrical member (93a) is provided with two seal rings (94, 95). Specifically, circumferential step portions along the inner peripheral edge are formed on both end faces of the cylindrical member (93a), and seal rings (94, 95) are fitted into the step portions. . And the seal ring (94) arrange | positioned at the upper end side of the cylindrical member (93a) in FIG. 9 is slidably contacted with the back surface of the turning side back member (54) of the turning scroll (50), and the turning side back member (54). And the gap between the cylindrical member (93a) is sealed. On the other hand, the seal ring (95) arranged on the lower end side of the cylindrical member (93a) in the same figure is in sliding contact with the front surface of the disk portion (72) of the housing member (70), and the housing member (70) and the cylindrical member Seal the gap (93a).

  In this joint unit (90a), the space inside the cylindrical member (93a) communicates with the connection passage (83) of the housing member (70) via the fixed side pin (91), and the swivel side pin (92) To communicate with the introduction passage (63) of the orbiting scroll (50). The space inside the cylindrical member (93a) is sealed from the outside by a seal ring (94, 95) provided in the cylindrical member (93a). Then, the refrigerating machine oil flowing through the connection passage (83) of the cooling fluid circuit (180) flows into the space inside the cylindrical member (93a) through the fixed side pin (91a), and then the swivel side pin ( 92a) to the turning side passageway (60).

-Third modification-
In the scroll compressor (171) of each embodiment described above, a mechanism other than the Oldham coupling (89) may be used as the rotation prevention mechanism (88). Here, the rotation prevention mechanism (88) of this modification will be described as an example where it is applied to the scroll compressor (171) of the first embodiment.

  The rotation prevention mechanism (88) of the present modification is configured by at least three joint units (90). As shown in FIG. 10, each joint unit (90) includes one pin member (96) and one protrusion (97), and in the circumferential direction of the orbiting end plate (56) of the orbiting scroll (50). They are arranged at approximately equal angular intervals.

  The pin member (96) is formed in a columnar shape or a circular tube shape, and is attached to the orbiting scroll (50). Specifically, the pin member (96) is embedded in the vicinity of the periphery of the turning-side back member (54) in a posture protruding from the back surface (the lower surface in FIG. 10) of the turning-side back member (54). The axial direction of the pin member (96) is substantially orthogonal to the back surface of the turning-side back member (54).

  The protrusion (97) is formed integrally with the housing member (70). Specifically, the protruding portion (97) protrudes from the front surface (upper surface in FIG. 10) of the disc portion (72) of the housing member (70), and is formed in a short columnar shape having a flat upper end. On the front surface of the disc part (72), the protrusions (97) are located one by one corresponding to each pin member (96) at a position facing the pin member (96) provided on the orbiting scroll (50). Has been placed. Further, the protruding end surface (upper surface in FIG. 10) of the projecting portion (97) is in sliding contact with the back surface of the turning-side back member (54).

  One guide hole (98) is formed in each protrusion (97). The guide hole (98) is a hole having a circular cross section and a bottom, and is open to the projecting end surface of the projecting portion (97). A portion of the corresponding pin member (96) protruding from the orbiting scroll (50) is inserted into the guide hole (98).

  In the rotation prevention mechanism (88) of this modification, the wall surface of the guide hole (98) is in contact with the outer peripheral surface of the pin member (96). The inner diameter Dg of the guide hole (98) is equal to the sum (dp + 2 × r2) of the outer diameter dp of the pin member (96) and the value obtained by doubling the revolution radius r2 of the orbiting scroll (50) ( Dg = dp + 2 * r <2>). Even if the orbiting scroll (50) moves during the operation of the scroll compressor (171), the wall surface of the guide hole (98) continues to be in sliding contact with the outer peripheral surface of the pin member (96). 50) Rotation is regulated.

  One of the joint units (90) provided in the compression mechanism (20) constitutes a part of the cooling fluid circuit (180). In the compression mechanism (20) shown in FIG. 10, the joint unit (90a) provided on the right side of FIG. 10 constitutes a part of the cooling fluid circuit (180).

  As shown in FIG. 11, in the joint unit (90a) constituting the cooling fluid circuit (180), the pin member (96a) is formed in a circular tube having both ends opened. The internal space of the pin member (96a) communicates with an introduction passage (63) formed in the orbiting scroll (50). Further, in the joint unit (90a), a connection passage (83) is opened on the bottom surface of the guide hole (98a) formed in the protrusion (97a).

  In the joint unit (90a), the protrusion (97a) is provided with a seal ring (99). Specifically, a circumferential groove along the inner peripheral edge is formed on the projecting end surface of the projecting portion (97a), and a seal ring (99) is fitted into the groove. This seal ring (99) is in sliding contact with the back surface of the orbiting side back member (54) of the orbiting scroll (50) and seals the gap between the orbiting side back member (54) and the protruding portion (97a).

  In this joint unit (90a), the guide hole (98a) communicates with the introduction passage (63) of the orbiting scroll (50) via the pin member (96a), and opens to the bottom surface of the connection passage (83). Communicating with Further, the guide hole (98a) is sealed from the outside by a seal ring (99) provided in the protrusion (97a). The refrigerating machine oil flowing through the connection passage (83) of the cooling fluid circuit (180) passes through the guide hole (98a) and the pin member (96a) toward the turning side passage (60) of the turning scroll (50). Will flow.

-Fourth modification-
The scroll compressor (171) of each embodiment described above is configured in a high-pressure dome shape in which the internal space of the casing (11) is filled with the gas refrigerant discharged from the compression mechanism (20). The scroll compressor (171) may be configured as a low-pressure dome type in which the internal space of the casing (11) is filled with the gas refrigerant sucked into the compression mechanism (20). Here, what is different from the first embodiment will be described with respect to the modification applied to the scroll compressor (171) of the first embodiment.

  As shown in FIG. 12, the compression mechanism (20) of the present modification is provided with a cover member (28). The cover member (28) is provided on the back surface (upper surface in FIG. 12) of the fixed-side back member (35) of the fixed scroll (30) so as to cover the check valve (25). In the compression mechanism (20), a closed space communicating with the discharge port (22) is formed by the cover member (28) and the fixed-side back member (35). One end of the discharge pipe (13) of this modified example is attached to the cover member (28), and is connected to a space formed inside the cover member (28) and communicating with the discharge port (22). . The discharge pipe (13) extends through the casing (11) to the outside of the casing (11).

  Further, in the compression mechanism (20) of this modification, the suction port (21) is formed in the housing member (70). The suction port (21) passes through the housing body (71) from the back surface (lower surface in FIG. 12) toward the front surface (upper surface in the same drawing). And the suction port (21) is a space between the compression mechanism (20) and the electric motor (110) in the internal space of the casing (11) in a space surrounded by the housing member (70) and the fixed scroll (30). Communicate. The suction pipe (12) of this modification penetrates the casing (11), and one end of the suction pipe (12) opens into a portion between the compression mechanism (20) and the electric motor (110) in the internal space of the casing (11). Yes.

  In the scroll compressor (171) of this modification, the low-pressure gas refrigerant that has flowed into the internal space of the casing (11) through the suction pipe (12) passes through the suction port (21) to the compression chamber (23). Inhaled and compressed. The gas refrigerant compressed in the compression chamber (23) flows into the space inside the cover member (28) through the discharge port (22), and then passes through the discharge pipe (13) in the casing (11). It flows out to the outside.

-Fifth modification-
In the scroll compressor (171) of each embodiment described above, the trochoid pump is used as the oil pump (127, 128, 128a, 128b), but the pump that can be used as the oil pump (127, 128, 128a, 128b) is limited to this. Instead, for example, a gear pump may be used as the oil pump (127, 128, 128a, 128b).

-Sixth Modification-
In each embodiment mentioned above, although the scroll compressor (171) is provided in the refrigerant circuit (160) of the air conditioning apparatus (150), the use of the scroll compressor (171) is not limited to this. The scroll compressor (171) described above may be provided, for example, in a refrigerant circuit (160) of a refrigeration apparatus that cools the inside of a refrigerator, or provided in a refrigerant circuit (160) of a hot water heater that heats water with the refrigerant. It may be. The scroll compressor (171) described above may be used not only to compress the refrigerant but also to compress air, for example.

-Seventh modification-
In the scroll compressor (171) of each embodiment described above, the refrigerating machine oil is used as the cooling fluid, but a fluid other than the refrigerating machine oil may be used as the cooling fluid. For example, a refrigerant or cooling water in the refrigerant circuit (160) may be used as the cooling fluid.

  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or its use.

  As described above, the present invention is useful for the scroll compressor that cools the fixed scroll and the orbiting scroll with the fluid, and the air conditioner including the scroll compressor.

11 Casing
13 Discharge pipe
20 Compression mechanism
30 Fixed scroll
40 Fixed passage
50 orbiting scroll
53 Swivel lap
56 Rotating end panel
60 Turn side passage
70 Housing material
77 Annular groove (dent)
80 Inner seal ring (seal member)
81 Outer seal ring (seal member)
83 Connection passage
128a First cooling pump (first transfer mechanism)
128b Second cooling pump (second transport mechanism)
171 scroll compressor
180 Fluid circuit for cooling
181 Upstream cooler
181a First upstream cooler
181b Second upstream cooler
184 First flow control valve
185 Second flow control valve
186 Flow control mechanism
190 Main introduction passage
191 First branch passage
192 Second branch passage
193 First supply passage
194 Second supply passage
197 Downstream cooler

Claims (8)

A scroll compressor including a compression mechanism (20) provided with a fixed scroll (30) and a turning scroll (50), and sucking compressed gas into the compression mechanism (20) for compression.
The main introduction passage (190) through which the cooling fluid flows, the first and second branch passages (191, 192) bifurcated from the downstream end of the main introduction passage (190), and the fixed scroll (30) are formed. The fixed side passage (40) through which the cooling fluid flowing out of the first branch passage (191) flows and the cooling fluid formed in the orbiting scroll (50) and out of the second branch passage (192) A cooling fluid circuit having a flowing swirl side passage (60) and a flow rate control mechanism (186) for controlling the flow rate of the cooling fluid flowing through the first branch passage (191) and the second branch passage (192). (180) The scroll compressor characterized by the above-mentioned. In claim 1,
The flow rate control mechanism (186) includes a first flow rate adjustment valve (184) provided in the first branch passage (191), and a second flow rate adjustment valve (185) provided in the second branch passage (192). A scroll compressor characterized by comprising: In claim 2,
A casing (11) formed in a hollow container shape in which the compression mechanism (20) is accommodated and in which the lubricating oil of the compression mechanism (20) accumulates,
The main inlet passage (190) is connected to an upstream cooler (181) for introducing lubricating oil accumulated in the casing (11) and cooling the lubricating oil. Machine. A scroll compressor including a compression mechanism (20) provided with a fixed scroll (30) and a turning scroll (50), and sucking compressed gas into the compression mechanism (20) for compression.
A first supply passage (193) including a first transfer mechanism (128a) for transferring a cooling fluid and a second supply passage (194) including a second transfer mechanism (128b) for transferring a cooling fluid A fixed side passage (40) formed in the fixed scroll (30) through which the cooling fluid flowing out of the first supply passage (193) flows, and a second supply formed in the orbiting scroll (50). A scroll compressor comprising a cooling fluid circuit (180) having a swirl side passage (60) through which a cooling fluid flowing out of the passage (194) flows. In claim 4,
A casing (11) which is formed in a hollow container shape in which the compression mechanism (20) is accommodated and in which the lubricating oil of the compression mechanism (20) accumulates;
A drive shaft (100) housed in the casing (11) and driving the orbiting scroll (50),
The first transport mechanism (128a) and the second transport mechanism (128b) are respectively constituted by positive displacement pumps that are driven to rotate by the drive shaft (100) and transport the lubricating oil accumulated in the casing (11). ,
Connected to the first supply passage (193) is a first upstream cooler (181a) for cooling the lubricating oil transported by the first transport mechanism (128a),
A scroll compressor, wherein a second upstream side cooler (181b) for cooling the lubricating oil conveyed by the second conveying mechanism (128b) is connected to the second supply passage (194). . In claim 3 or 5,
A downstream cooler (197) that is connected to the cooling fluid circuit (180) and cools the cooling fluid that has passed through the stationary passage (40) and the turning passage (60);
The cooling fluid circuit (180) supplies the cooling fluid cooled by the downstream cooler (197) to the compressed gas sucked into the compression mechanism (20). . In claim 6,
While the compression mechanism (20) discharges the compressed gas to be compressed into the internal space of the casing (11),
The casing (11) is provided with a discharge pipe (13) for leading the compressed gas discharged from the compression mechanism (20) to the outside.
A scroll compressor characterized in that lubricating oil is stored in a portion where compressed gas discharged from the compression mechanism (20) exists in the internal space of the casing (11). In any one of Claims 1 thru | or 7,
The orbiting scroll (50) has a revolving side end plate portion (56) formed in a flat plate shape and a spiral wall-like revolving side wrap (53) standing on the front surface of the revolving side end plate portion (56). Provided,
The compression mechanism (20) is provided with a housing member (70) that is in sliding contact with the back surface of the turning side end plate portion (56).
An end of the turning side passageway (60) is opened on the back of the turning side end plate portion (56),
The portion of the housing member (70) that is in sliding contact with the back surface of the swivel side end plate portion (56) is always in contact with the end of the revolving side passageway (60) that opens to the back side of the revolving side end plate portion (56). A communicating recess (77), and a seal member (80, 81) which is provided so as to surround the recess (77) and seals the gap between the swivel end plate (56) and the housing member (70). ) And
The housing compressor (70) is formed with a connecting passage (83) for introducing a cooling fluid and having a downstream end connected to the recess (77).

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