JP2004169617A - Horizontal compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a horizontal compressor capable of improving oil sealing performance and surely preventing oil shortage in minute clearances of sliding portions. <P>SOLUTION: The horizontal compressor (multistage compression type rotary compressor) 10 comprises a drive element 14 and a compressing mechanism section 18 driven by the drive element 14 in a horizontal hermetic container 12, in which refrigerant is compressed and discharged by the compressing mechanism section 18. The compressor is equipped with an oil separation means (tank) 130 provided on a refrigerant discharge side of the compressing mechanism section 18. Oil separated in the oil separation means (tank) 130 is supplied to the sliding portions of members in the hermetic container 12. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a horizontal compressor in which a driving element and a compression mechanism driven by the driving element are provided in a horizontal closed container, and the compression mechanism compresses and discharges the refrigerant. Things.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, a rotary compressor as an electric compressor of this type, particularly a multi-stage compression type rotary compressor having a rotary compression mechanism including a first rotary compression element and a second rotary compression element, usually has an upper portion inside a vertical closed container. , And a rotary compression mechanism driven by a rotation shaft of the drive element is arranged at a lower portion. Refrigerant gas is sucked into the low pressure chamber side of the cylinder from the suction port of the first rotary compression element, is compressed by the operation of the rollers and vanes, and is discharged from the high pressure chamber side of the cylinder through the discharge port and the discharge muffling chamber. It is discharged into. At this time, the inside of the sealed container has an intermediate pressure (see Patent Document 1).
[0003]
The intermediate-pressure refrigerant gas in the closed container is sucked into the low-pressure chamber side of the cylinder from the suction port of the second rotary compression element, and the second-stage compression is performed by the operation of the roller and the vane, so that the high-temperature and high-pressure refrigerant gas is discharged. Thus, the configuration is such that the gas flows from the high-pressure chamber through a discharge port and a discharge muffling chamber to a radiator outside the compressor.
[0004]
Further, in such a vertical rotary compressor, the bottom of the closed container located below the rotary compression mechanism is an oil reservoir, and oil is supplied from the oil reservoir by an oil pump as an oil supply means formed at the lower end of the rotary shaft. It is sucked and supplied to the rotary compression mechanism to prevent wear of the rotary compression mechanism and the sliding portion of the rotary shaft.
[0005]
[Patent Document 1]
JP-A-2-294587 (F04C 23/00) (pages 4 and 5).
[0006]
[Problems to be solved by the invention]
In such an electric compressor, the oil supplied to the first and second rotary compression elements is mixed in the discharged refrigerant gas, but the oil mixed in the refrigerant gas flows into a radiator outside the compressor. And a problem will occur. For this reason, after separating the oil in the discharged refrigerant gas, the oil is generally returned to the upper part in the closed container using a thin tube such as a capillary tube to lubricate the sliding portion in the closed container. There is a problem that the oil downstream from the upper portion is hard to enter the gap between the sliding portions, and the oil sealing performance of the sliding portion is reduced.
[0007]
Further, the oil downstream from the upper part of the container is hard to enter particularly the sliding portion of the minute gap. For this reason, there is also a problem that inconvenience such as running out of oil occurs in the sliding portion of the minute gap.
[0008]
The present invention has been made in order to solve the problems of the related art, and a horizontal mounting type capable of improving oil sealing performance and reliably preventing oil shortage in a minute gap of a sliding portion. An object is to provide a compressor.
[0009]
[Means for Solving the Problems]
That is, the horizontal compressor of the present invention includes a driving element in a closed container, and a compression mechanism driven by the driving element, and compresses and discharges the refrigerant by the compression mechanism. There is provided an oil separating means provided on the refrigerant discharge side of the compression mechanism, and the oil separated by the oil separating means is supplied at a high pressure to a member sliding portion in the closed container. The oil can be supplied even to the minute gap of the member sliding portion.
[0010]
In particular, since the oil returning from the oil separating means provided on the refrigerant discharge side of the compression mechanism has a high pressure, it is possible to improve the oil sealing performance of the minute gap of the member sliding portion. Therefore, it is possible to reliably prevent inconvenience such as running out of oil in the minute gap of the member sliding portion.
[0011]
In the horizontal compressor according to the second aspect of the present invention, the oil separated by the oil separating means is supplied to the sliding portion between the rotating shaft of the driving element and the bearing of the rotating shaft at a high pressure. Therefore, it is possible to reliably perform lubrication between the rotating shaft and the bearing. Thereby, the oil seal performance between the rotating shaft and the bearing can be greatly improved.
[0012]
According to a third aspect of the present invention, there is provided a horizontal compressor according to the first aspect, wherein the compression mechanism portion is fitted to an eccentric portion formed on a rotary shaft of a drive element and a cylinder, and the eccentric portion is formed in the cylinder. A rotary compression element including a rotating roller, a vane abutting on the roller to partition the inside of the cylinder into a low pressure chamber side and a high pressure chamber side, and a guide groove formed in the cylinder and accommodating the vane. Since the oil separated by the oil separating means is supplied to the sliding portion between the vane and the guide groove at a high pressure, particularly in the case of a rotary compressor, the lubrication between the vane and the guide groove is preferably performed. Becomes possible. As a result, the oil seal performance and lubrication performance between the vane and the guide groove can be greatly improved.
[0013]
Also, in the horizontal compressor according to the invention of claim 4, in addition to claim 1, claim 2 or claim 3, the compression mechanism section comprises first and second rotary compression elements. The refrigerant compressed by the rotary compression element is discharged into the closed container, and the discharged intermediate-pressure refrigerant is compressed by the second rotary compression element and discharged to the oil separating means. In the multi-stage compression type rotary compressor described above, high-pressure oil can be supplied to the minute gap of the sliding portion in the sealed container.
[0014]
In particular, since the oil returning from the oil separating means provided on the refrigerant discharge side of the second rotary compression element has an extremely high pressure, the oil sealing performance and the lubrication performance of the minute gap of the sliding portion in the closed container are greatly reduced. It can be improved. Therefore, it is possible to reliably prevent inconvenience such as running out of oil in a minute gap of the sliding portion in the closed container.
[0015]
Furthermore, in the horizontal compressor according to the fifth aspect of the present invention, since carbon dioxide is used as the refrigerant in the first, second, third, or fourth aspect, a carbon dioxide refrigerant having a large difference between high and low pressures is used. In this case, the oil returning from the oil separating means has an extremely high pressure. As a result, it is possible to particularly effectively perform oil sealing of the minute gap of the sliding portion in the closed container. Therefore, it is possible to reliably prevent inconvenience such as running out of oil even in a minute gap of a sliding portion in a sealed container of a horizontal compressor by using a carbon dioxide refrigerant having a large difference between high and low pressures. It becomes.
[0016]
BEST MODE FOR CARRYING OUT THE INVENTION
Next, an embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 shows, as an embodiment of a horizontal compressor of the present invention, a longitudinal section of a horizontal multistage (two-stage) compression type rotary compressor 10 of an internal intermediate pressure type having first and second rotary compression elements 32 and 34. FIG. 2 is a side sectional view of the multi-stage compression type rotary compressor 10 shown in FIG.
[0017]
In each of the drawings, reference numeral 10 denotes an internal intermediate-pressure type horizontally mounted multistage compression type electric compressor (multistage compression type rotary compressor) using carbon dioxide (CO2) as a refrigerant, and the multistage compression type rotary compressor 10 is sealed at both ends. A horizontally long cylindrical closed container 12 is provided, and the bottom of the closed container 12 is used as an oil reservoir. The closed container 12 includes a container body 12A and a substantially bowl-shaped end cap (lid) 12B for closing an opening of the container body 12A.
[0018]
A rotary compression mechanism unit including a drive element 14 and a first rotary compression element 32 and a second rotary compression element 34 driven by the rotation shaft 16 of the drive element 14 extending in the horizontal direction. 18 are housed side by side. A circular mounting hole 12D is formed at the end of the closed container 12 on the driving element 14 side, and a terminal 20 (wiring is omitted) for supplying power to the driving element 14 is formed in the mounting hole 12D. Installed.
[0019]
The driving element 14 includes a stator 22 annularly mounted along the inner peripheral surface of the closed casing 12, and a rotor 24 inserted inside the stator 22 with a slight space therebetween. The rotor 24 is fixed to the rotating shaft 16 that extends through the center in the axial direction of the closed casing 12.
[0020]
An oil pump 80 as an oil supply means is formed at an end of the rotary shaft 16 on the side of the rotary compression mechanism 18. The oil pump 80 is provided for sucking oil as a lubricating oil from an oil reservoir formed at the bottom of the sealed container 12 and supplying the oil to the sliding portion of the rotary compression mechanism 18 to prevent wear. An oil suction pipe 80A descends from the oil pump 80 toward the bottom of the sealed container 12, and is opened in the oil reservoir.
[0021]
The stator 22 has a laminated body 26 in which donut-shaped electromagnetic steel sheets are laminated, and a stator coil 28 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method. The rotor 24 is also formed of a laminated body 30 of electromagnetic steel sheets, like the stator 22, and is formed by inserting a permanent magnet MG into the laminated body 30.
[0022]
The first rotary compression element 32 and the second rotary compression element 34 are constituted by first and second cylinders 40 and 38, and an intermediate partition plate 36 is sandwiched between the cylinders 40 and 38. That is, the rotary compression mechanism 18 includes a first rotary compression element 32 and a second rotary compression element 34, and an intermediate partition plate 36.
[0023]
Further, the first and second rotary compression elements 32 and 34 are respectively provided with first and second cylinders 40 and 38 disposed on both sides (left and right in FIG. 1) of the intermediate partition plate 36, respectively, with a 180 ° phase difference. The first and second rollers 48 which are fitted to the first and second eccentric portions 44 and 42 provided on the rotating shaft 16 and eccentrically rotate in the first and second cylinders 40 and 38. , 46, and the first and second vanes 52, which respectively contact the rollers 48, 46 to reciprocate and partition the cylinders 40, 38 into a low-pressure chamber LR and a high-pressure chamber HR (FIG. 3), respectively. The support members 54, 56, which also serve as bearings for the rotating shaft 16, by closing the opening surface of the cylinder 50 on the drive element 14 side and the opening surface of the cylinder 40 on the side opposite to the drive element 14. .
[0024]
A guide groove 70 (the second vane 52 side is not shown) for slidably storing the first and second vanes 52, 50 is provided in both cylinders 40, 38. Are provided with springs 76, 74 that abut against the outer ends of the first and second vanes 52, 50 and constantly bias the first and second vanes 52, 50 toward the rollers 48, 46. (Fig. 3). Further, metal plugs 76A and 74A are provided on the closed container 12 side of the springs 76 and 74, and serve to prevent the springs 76 and 74 from coming off. A back pressure chamber (not shown) is formed in the second vane 50, and the pressure of the high pressure chamber HR in the cylinder 38 is applied to the back pressure chamber as a back pressure.
[0025]
The support members 54 and 56 have suction ports 58 and 60 that communicate with the low-pressure chamber LR inside the cylinders 38 and 40 at the suction ports 161 and 162, respectively, and a part thereof is recessed. , 68 are provided, respectively. In addition, 163 is a discharge port.
[0026]
The discharge muffling chamber 64 and the inside of the sealed container 12 penetrate the cylinders 38 and 40, the intermediate partition plate 36, and the cover 66, and further penetrate a baffle plate 100, which will be described later, provided separately from the cover 66. It communicates with a communication passage (not shown) that opens to the 14 side, and an intermediate discharge pipe 121 is provided upright at an end of the communication passage. The intermediate-pressure refrigerant gas compressed by the first rotary compression element 32 is discharged from the intermediate discharge pipe 121 toward the drive element 14 in the closed casing 12. At this time, the oil supplied to the first rotary compression element 32 is mixed in the refrigerant gas, and this oil is also discharged to the drive element 14 side in the closed container 12. Here, the oil mixed in the refrigerant gas is separated from the refrigerant gas and stored in an oil reservoir at the bottom of the closed container 12.
[0027]
The above-described baffle plate 100 is provided to divide the inside of the closed container 12 into the drive element 14 side and the rotary compression mechanism 18 side, and to configure a differential pressure in the closed container 12. The baffle plate 100 is made of a donut-shaped steel plate disposed at a small distance from the inner surface of the closed container 12. In this case, the intermediate-pressure refrigerant gas compressed by the first rotary compression element 32 and discharged to the drive element 14 side in the sealed container 12 passes through a gap formed between the sealed container 12 and the baffle plate 100. However, due to the presence of the baffle plate 100, the pressure on the drive element 14 side of the baffle plate 100 is high in the closed container 12 and the difference is low on the rotary compression mechanism portion 18 side. Pressure is configured.
[0028]
Then, due to this differential pressure, the oil stored in the oil reservoir at the bottom of the closed container 12 moves to the rotary compression mechanism 18 side, and the oil level on the rotary compression mechanism 18 side from the baffle plate 100 rises. As a result, the opening of the oil suction pipe 80A is immersed in the oil without any trouble, so that the oil pump 80 smoothly supplies the oil to the sliding portion of the rotary compression mechanism 18. .
[0029]
In addition, the baffle plate 100 is provided with an intake passage 102 that communicates with the above-described suction passage 58 in order to introduce the intermediate-pressure refrigerant gas in the closed casing 12 into the second rotary compression element 34. The suction port 104 of the intake passage 102 is opened at the upper part of the baffle plate 100 on the side of the rotary compression mechanism 18, and the refrigerant gas at an intermediate pressure is sucked from the suction port 104. The intake passage 102 penetrates through the baffle plate 100, extends along the drive element 14 side of the baffle plate 100, and then penetrates through the baffle plate 100 and the cover 66 to communicate with the suction passage 58. Have been.
[0030]
The baffle plate 100 is disposed at a predetermined distance from the cover 66 of the second rotary compression element 34 of the rotary compression mechanism 18. This makes it difficult for the baffle plate 100 to be heated by the heat of the rotary compression mechanism 18, so that the refrigerant gas introduced into the second rotary compression element 34 through the intake passage 102 provided in the baffle plate 100 Is also difficult to be heated. Thereby, the compression efficiency of the second rotary compression element 34 is improved.
[0031]
Further, the suction port 104 of the intake passage 102 is opened at the upper part of the rotary compression mechanism 18 opposite to the drive element 14 side where the intermediate discharge pipe 121 opens, with the baffle plate 100 interposed therebetween. Thereby, oil separation of the refrigerant gas sucked into the intake passage 102 is performed smoothly. In addition, the intake passage 102 and the rotary compression mechanism 18 do not interfere with each other, and the components in the closed casing 12 can be easily arranged.
[0032]
As the refrigerant in this case, the CO2 (carbon dioxide), which is a natural refrigerant in consideration of flammability and toxicity, which is friendly to the global environment, is used, and is used as an oil as a lubricating oil sealed in the closed container 12. For example, mineral oil (mineral oil), alkyl benzene oil, ether oil, ester oil, PAG (polyalkyl glycol) and the like are used.
[0033]
Sleeves 142 and 143 are fixed to the side surfaces of the sealed container 12 by welding at positions corresponding to the side portions of the support members 56 and 54, respectively. One end of a refrigerant introduction pipe 94 for introducing refrigerant into the cylinder 40 is inserted and connected into the sleeve 142, and communicates with the suction passage 60. A refrigerant discharge pipe 96 is inserted into the sleeve 143, and one end of the refrigerant discharge pipe 96 is connected to the discharge muffling chamber 62. Further, a mounting pedestal 110 is provided at the bottom of the sealed container 12 (not shown in FIG. 2).
[0034]
On the other hand, a refrigerant pipe 98 is fixedly connected to an end of the refrigerant discharge pipe 96 by welding via a vertically long cylindrical tank 130 (corresponding to the oil separating means of the present invention). It is open at the top inside the tank 130. An oil return pipe 134 is connected to a lower part of the tank 130, and the oil return pipe 134 is opened at a lower part in the tank 130, and a tip end is opened around the rotation shaft 16 through the container body 12A and the support member 54. . That is, the tip of the oil return pipe 134 connected to the lower part of the tank 130 is a sliding portion between the rotating shaft 16 and a bearing (support member 54) of the rotating shaft 16 (corresponding to a minute gap of the member sliding portion of the present invention). ).
[0035]
Although not shown, an oil separator is provided in the tank 130 so as to partition the space in the tank 130 up and down. While the refrigerant gas flowing into the tank 130 from the refrigerant discharge pipe 96 passes through the oil separator, the oil separator separates the oil discharged together with the refrigerant gas. The separated oil is stored in the lower portion of the tank 130 and supplied to the sliding portion between the rotating shaft 16 of the driving element 14 and the bearing (support member 54) of the rotating shaft 16 through the oil return pipe 134. You.
[0036]
Next, the operation of the above configuration will be described. When the stator coil 28 of the driving element 14 is energized via the terminal 20 and the wiring (not shown), the driving element 14 starts and the rotor 24 rotates. By this rotation, the rollers 46 and 48 fitted to the eccentric portions 42 and 44 provided integrally with the rotating shaft 16 eccentrically rotate inside the cylinders 38 and 40.
[0037]
As a result, the low-pressure refrigerant sucked from the suction port 162 to the low-pressure chamber side of the cylinder 40 via the refrigerant introduction pipe 94 and the suction passage 60 formed in the support member 56 is supplied to the roller 48 and the second vane 52. It is compressed by the operation to become an intermediate pressure, and is discharged from the intermediate discharge pipe 121 into the closed container 12 through a communication passage (not shown) from the high pressure chamber side of the cylinder 40. Thereby, the inside of the sealed container 12 has an intermediate pressure.
[0038]
The intermediate-pressure refrigerant gas in the sealed container 12 is drawn into the low-pressure chamber LR of the cylinder 38 from the suction port 161 via a refrigerant introduction pipe and a suction passage (not shown). The sucked intermediate-pressure refrigerant gas is compressed in the second stage by the operation of the roller 46 and the first vane 50, and becomes a high-temperature and high-pressure refrigerant gas. The high-temperature and high-pressure refrigerant gas is discharged from the high-pressure chamber HR through the discharge port 163, through the discharge muffling chamber 62 formed in the support member 54, through the refrigerant discharge pipe 96, into the tank 130, and into the tank 130. Inside is high pressure.
[0039]
The high-temperature and high-pressure refrigerant gas discharged into the tank 130 passes through an oil separator provided in the tank 130, whereby oil dissolved therein is separated. The refrigerant gas from which oil has been separated by the oil separator flows out of the tank 130 from the refrigerant pipe 98 on the downstream side, and flows into an external gas cooler (not shown). After the refrigerant radiates heat in the gas cooler, the pressure is reduced by a pressure reducing device (not shown) or the like, and also flows into an evaporator (not shown).
[0040]
Then, a cycle in which the refrigerant evaporates and thereafter is sucked into the first rotary compression element 32 from the refrigerant introduction pipe 94 through the accumulator is repeated.
[0041]
The oil separated from the refrigerant gas by the oil separator is stored in a high-pressure tank 130. The oil stored in the tank 130 is extruded at a high pressure into an oil return pipe 134, passes through the oil return pipe 134, and slides between the rotation shaft 16 of the driving element 14 and a bearing (support member 54) of the rotation shaft 16. It is supplied to the section at high pressure and lubricated.
[0042]
As described above, the high-pressure oil separated in the tank 130 is supplied to the sliding portion between the rotating shaft 16 of the driving element 14 and the supporting member 54 of the rotating shaft 16 without using a conventional capillary tube. Therefore, it is possible to reliably perform lubrication even in a minute gap between the rotating shaft 16 and the support member 54. As a result, the performance of the oil seal between the rotating shaft 16 and the support member 54 can be greatly improved.
[0043]
In the above-described embodiment, the high-pressure oil separated in the tank 130 is supplied to the sliding portion between the rotating shaft 16 and the support member 54 of the rotating shaft 16 by the oil return pipe 134, but is not limited thereto. Instead, as shown in FIG. 3, an oil return pipe 134 may extend through the cylinder 38 of the second rotary compression element 34 to the guide groove 70 of the second vane 50 and be opened there (FIG. 3). ).
[0044]
That is, in this case, the oil return pipe 134 is opened between the second vane 50 and the guide groove 70 (corresponding to a minute gap of the sliding portion of the present invention). Then, the oil separated in the tank 130 is supplied at high pressure to the sliding portion between the second vane 50 and the guide groove 70 through the branched oil return pipe 134.
[0045]
As described above, when the high-pressure oil separated in the tank 130 is supplied to the sliding portion between the second vane 50 and the guide groove 70, in the internal intermediate pressure type multi-stage compression type rotary compressor 10, Lubrication can be suitably performed even in the minute gap between the second vane 50 of the cylinder 38 of the second-stage rotary compression element 34 and the guide groove 70. As a result, it is possible to greatly improve the oil sealing performance between the second vane 50 and the guide groove 70. Therefore, it is possible to reliably prevent inconvenience such as running out of oil in a minute gap of the sliding portion in the sealed container 12.
[0046]
In the embodiment, the horizontal compressor of the present invention is applied to the internal intermediate pressure type horizontal multistage compression type rotary compressor 10, but the present invention is not limited to this, and the present invention is also effective for a single cylinder rotary compressor.
[0047]
【The invention's effect】
As described above in detail, according to the present invention, a drive element and a compression mechanism driven by the drive element are provided in a horizontal closed container, and the compression mechanism compresses and discharges the refrigerant. It is provided with oil separating means provided on the refrigerant discharge side of the compression mechanism, and the oil separated by the oil separating means is supplied at high pressure to a member sliding portion in a closed container, Oil can be supplied even to a minute gap in the member sliding portion in the closed container.
[0048]
In particular, since the oil returning from the oil separating means provided on the refrigerant discharge side of the compression mechanism has a high pressure, it is possible to improve the oil sealing performance of the minute gap of the member sliding portion. Therefore, it is possible to reliably prevent inconvenience such as running out of oil in the minute gap of the member sliding portion.
[0049]
According to the second aspect of the present invention, in addition to the above, the oil separated by the oil separating means is supplied at a high pressure to the sliding portion between the rotating shaft of the driving element and the bearing of the rotating shaft. Lubrication between the rotating shaft and the bearing can be reliably performed. Thereby, the oil seal performance between the rotating shaft and the bearing can be greatly improved.
[0050]
According to the third aspect of the present invention, in addition to the first aspect, the compression mechanism includes a cylinder and a roller that is fitted to an eccentric portion formed on a rotation shaft of the drive element and that rotates eccentrically in the cylinder. A rotary compression element having a vane abutting against the roller and partitioning the inside of the cylinder into a low pressure chamber side and a high pressure chamber side, and a guide groove formed in the cylinder and accommodating the vane. Since the oil separated by the means is supplied to the sliding portion between the vane and the guide groove at high pressure, lubrication between the vane and the guide groove can be suitably performed particularly in the case of a rotary compressor. As a result, the oil seal performance and lubrication performance between the vane and the guide groove can be greatly improved.
[0051]
According to the fourth aspect of the present invention, in addition to the first, second, or third aspect, the compression mechanism section includes the first and second rotary compression elements, and the first rotary compression element. Is discharged into the closed container, and the discharged intermediate-pressure refrigerant is compressed by the second rotary compression element and discharged to the oil separating means. For example, the internal intermediate-pressure multistage compression type In this rotary compressor, high-pressure oil can be supplied to a minute gap in a sliding portion in a closed container.
[0052]
In particular, since the oil returning from the oil separating means provided on the refrigerant discharge side of the second rotary compression element has an extremely high pressure, the oil sealing performance and the lubrication performance of the minute gap of the sliding portion in the closed container are greatly reduced. It can be improved. Therefore, it is possible to reliably prevent inconvenience such as running out of oil in a minute gap of the sliding portion in the closed container.
[0053]
According to the fifth aspect of the present invention, carbon dioxide is used as the refrigerant in the first, second, third, or fourth aspect of the present invention. The oil returning from the separation means has a very high pressure. Thereby, it is possible to particularly effectively perform the oil sealing of the minute gap of the sliding portion in the closed container. Therefore, it is possible to reliably prevent inconvenience such as running out of oil even in a minute gap of a sliding portion in a sealed container of a horizontal compressor by using a carbon dioxide refrigerant having a large difference between high and low pressures. It becomes.
[Brief description of the drawings]
FIG. 1 is a vertical cross-sectional side view of an internal intermediate pressure type horizontal multi-stage compression type rotary compressor having first and second rotary compression elements as an embodiment of the compressor of the present invention.
FIG. 2 is a plan sectional view of the multi-stage compression type rotary compressor of FIG. 1;
FIG. 3 is a vertical sectional side view of a second cylinder of a multi-stage compression type rotary compressor illustrating another embodiment of the present invention.
[Explanation of symbols]
Reference Signs List 10 multi-stage compression type rotary compressor 12 closed container 12A container body 18 rotary compression mechanism 32 first rotary compression element 34 second rotary compression element 38, 40 cylinder 42, 44 eccentric part 46, 48 roller 50 second vane 52 First vane 54 Support member 70 Guide groove 96 Refrigerant discharge pipe 98 Refrigerant pipe 130 Tank 134 Oil return pipe

Claims (5)

In a horizontal compressor that includes a driving element in a horizontal type closed container and a compression mechanism driven by the driving element, and compresses and discharges the refrigerant in the compression mechanism.
An oil separating unit provided on a refrigerant discharge side of the compression mechanism unit, wherein the oil separated by the oil separating unit is supplied to a member sliding portion in the closed container. Compressor. The horizontal compressor according to claim 1, wherein the oil separated by the oil separating means is supplied to a sliding portion between a rotation shaft of the driving element and a bearing of the rotation shaft. The compression mechanism section, a cylinder, a roller that is fitted to an eccentric portion formed on the rotation shaft of the drive element and that rotates eccentrically in the cylinder, A rotary compression element having a vane partitioned into a high-pressure chamber and a guide groove formed in the cylinder and accommodating the vane, wherein the oil separated by the oil separating means is supplied to the vane. The horizontal compressor according to claim 1, wherein the compressor is supplied to a sliding portion between the first and second guide grooves. The compression mechanism section includes first and second rotary compression elements, discharges the refrigerant compressed by the first rotary compression element into the closed container, and further discharges the discharged intermediate-pressure refrigerant to the closed container. 4. The horizontal compressor according to claim 1, wherein said compressor is compressed by a second rotary compression element and discharged to said oil separating means. 5. The horizontal compressor according to claim 1, wherein carbon dioxide is used as the refrigerant.

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