JP2009299632A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor preventing poor lubrication and damage or the like to each sliding part. <P>SOLUTION: This compressor is provided with an oil separating means 5 separating oil from refrigerant compressed by a compression mechanism part 4, a drive part 3 driving the compression mechanism part 4 via a shaft 8, and a plurality of bearings 6, 7 bearing the shaft 8. A lubricating oil passage 30 and lubrication holes 30a, 30b for lubrication the bearings 6, 7 are included in the shaft 8. In the lubricating oil passage 30 in the shaft 8, at least an inner diameter of the lubricating oil passage 30 at an axial direction position where the lubrication hole 30b for the downstream side bearing 6 is set equal to or larger than an inner diameter of the lubricating oil passage 30 at an upstream side axial direction position. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a compressor that performs lubrication without lubrication failure using lubricating oil in a working fluid such as a refrigerant.

2. Description of the Related Art Conventionally, a compressor is known in which a part of a refrigerant in a compression process is supplied to a low pressure side by a pressure difference so that a low pressure side sliding portion is lubricated with a lubricating oil contained in the refrigerant.
For example, Patent Document 1 discloses a so-called horizontal electric scroll compressor.
In such an electric scroll compressor, the flow of the lubricating oil in the refrigerant follows from the scroll to the separator, the high pressure oil storage chamber, the throttle, the in-shaft lubricating oil passage, the bearing, the electric motor chamber oil storage chamber, and the scroll.
In addition, the shaft has a coaxial through hole, and this is used as a lubricating oil passage.

JP 2008-8285 A

The through hole for oil supply in the shaft is formed by drilling from both sides, but there is a possibility that misalignment between the holes occurs at the joint. For this reason,
(1) Insufficient lubrication of the downstream bearing (improper lubrication)
(2) The sliding parts such as the bearing and the scroll are damaged by the burr.
The present invention has been proposed to improve the above-described problems, and an object of the present invention is to provide a compressor that does not have poor lubrication or damage to each sliding portion.

  In order to achieve the above-described object, according to the first aspect of the present invention, in the compressor (1) in which the compression mechanism portion (4) for compressing the refrigerant is built in the housing (2), the compression mechanism portion (4) Oil separating means (5) for separating oil from the compressed refrigerant, a drive unit (3) for driving the compression mechanism (4) via the shaft (8), and a plurality of bearings for supporting the shaft (8) (6, 7), and the shaft (8) has a lubricating oil passage (30) and oil supply holes (30a, 30b) for supplying oil to the bearings (6, 7) in the shaft (8). For the lubricating oil passage (30) in (8), the inner diameter of the lubricating oil passage (30) at least in the axial position where the oil supply hole (30b) to the downstream bearing (6) is located is defined as the upstream axial direction. It is characterized by being equal to or greater than the inner diameter of the lubricating oil passage (30) at the position.

  As a result, the lubricating oil can be flowed from the upstream side to the downstream side in the lubricating oil passage (30) without hindering the flow, and there is no risk of insufficient lubrication with respect to the downstream bearing (67). Refueling can be performed reliably.

  More specifically, with respect to the lubricating oil passage (30) in the shaft (8), the bearing on the downstream side with respect to the inner diameter d1 from the lubricating oil passage (30) inlet to the oil supply hole (30a) to the bearing (7). The inner diameter d2 up to the oil supply hole (30b) to (6) can be set to satisfy d1 <d2.

  Further, in the lubricating oil passage (30) in the shaft (8), with respect to the inner diameter d1 at the intermediate position, the vicinity of the inlet of the lubricating oil passage (30) and the oil supply hole (30b) to the bearing (6) on the downstream side. The inner diameter d2 can be set so that d1 <d2.

  According to the second aspect of the present invention, the oil separation means (5) for separating the lubricating oil from the refrigerant compressed by the compression mechanism (4), the interior of the housing (2) being lower than the discharge pressure, and the oil separation means (5 ) Is provided with a lubricating oil supply path that guides the lubricating oil separated by (2) to the shaft (8) of the drive unit (3), and a pressure reducing means provided in the lubricating oil supply path.

  Thus, when the lubricating oil separated by the oil separation means (5) from the high-pressure refrigerant compressed by the compression mechanism section (4) is traced along the lubricating oil supply path, the pressure is reduced by the pressure reducing means, and the drive section (3) To the shaft (8).

  According to the third aspect of the present invention, the compression mechanism (4) includes a working chamber (14) that sucks and compresses the refrigerant, and a suction port (21) for taking the refrigerant into the working chamber (14) from an external circuit. And a suction chamber (20) provided downstream of the suction port (21), communicating with the working chamber (14), and having a lower pressure region than the suction port (21) region.

  Thereby, since the refrigerant | coolant is not diverted into the drive part room | chamber (3a) more than necessary, the performance fall by suction | inhalation heating can be suppressed. In addition, since the main flow path of the refrigerant is not restricted more than necessary, it is possible to suppress a decrease in performance due to suction pressure loss.

  In the invention according to claim 4, the compression mechanism portion (4) meshes with the fixed scroll (24) having the fixed spiral portion (18) fixed to the housing body (2a) and the fixed spiral portion (18). It has a movable scroll (17) provided with a movable spiral part (16) which forms a working chamber (14), and an inlet (21) is provided in the side of a working chamber (14).

  Thereby, the lubricating oil that has flowed into the drive chamber (3a) can be reliably guided to the suction chamber (20).

  According to a fifth aspect of the present invention, the drive portion (3) is a lubricating oil separated from the refrigerant in the lower portion, which is higher than the pressure in the suction chamber (20) by the differential pressure forming means in the housing (2). It arrange | positions in the drive part chamber (3a) which accumulates.

  Thereby, even if the lubricating oil is stored in the drive section chamber (3a) and the oil level rises, the through hole of the communication passage (12) can be made difficult to be immersed in the oil level of the lubricating oil. Thereby, it can prevent that lubricating oil bubbles or stirs with the refrigerant | coolant which branched to the drive part chamber (3a).

Furthermore the invention according to claim 6, the refrigerant taken into the compression mechanism unit (4) is characterized in that the main component CO _2.

As a result, a system using a refrigerant mainly composed of CO ₂ has a high operating pressure, and the lubricating state becomes severe when the lubricating oil stagnates in the drive section chamber (3a), so that a greater effect can be expected.

  In addition, the code | symbol in the bracket | parenthesis of each said means is an example which shows a corresponding relationship with the specific means of embodiment mentioned later.

FIG. 1 shows an example of a hot water supply system using the compressor 1. This hot water supply system is, for example, a heat pump hot water supply system, and heats hot water by giving heat to the hot water with an amount of heat absorbed from the outside air and a compression work amount of the compressor 1.
Such a hot water supply system substantially includes a compressor 1 that sucks and compresses a refrigerant, a water refrigerant heat exchanger A that performs heat exchange between hot water in a hot water storage tank and refrigerant discharged by the compressor 1, and A decompressor B that depressurizes the refrigerant that flows out of the water-refrigerant heat exchanger A, an evaporator C that absorbs heat from the outside air and evaporates the refrigerant, and a refrigerant that flows out of the evaporator C is separated into a liquid-phase refrigerant and a gas-phase refrigerant. Thus, an excess refrigerant is stored and a gas-liquid separator D that supplies the gas-phase refrigerant to the compressor 1 is used.

In the compressor 1 here, CO ₂ is used as a refrigerant, and the compressor 1 is a horizontal type compressor that operates a compression mechanism by a horizontally mounted electric motor unit incorporated in the housing, as will be described later.
When CO ₂ is used as a refrigerant, higher pressure is required in terms of efficiency as compared with conventional chlorofluorocarbon refrigerants, and the pressing force applied to the place where the orbiting scroll and the fixed scroll described later slide is excessive. However, as described later, since it is configured to constantly supply and recover the lubricating oil during operation, CO ₂ can be used as the refrigerant.

That is, this compressor 1 is, for example, an electric scroll type. As shown in FIG. 2, as shown in FIG. 2, an electric motor unit 3 that is a drive unit and a compression mechanism unit 4 that is operated by the electric motor unit 3 as a housing 2. And an oil separating means 5 for separating oil from the refrigerant compressed by the compression mechanism section 4 and the inside of the housing 2 is set to a pressure lower than the discharge pressure.
The housing 2 is substantially composed of a housing main body 2a that houses the electric motor section 3, the compression mechanism section 4 and the oil separating means 5, and end housings 2b and 2c welded to both ends of the housing main body 2a. It is a sealed container.

  The electric motor unit 3 has a shaft 8 held substantially horizontally by a plurality of bearings 6 and 7 in the housing main body 2a, and the shaft 8 and the compression mechanism unit 4 are connected to each other dynamically. The electric motor unit 3 includes a rotor 9 that is fixed integrally with the shaft 8 and rotates together with the shaft 8, and a stator 10 that is fixed to the inner wall of the housing body 2 a and surrounds the periphery of the rotor 9.

  Next, the compression mechanism unit 4 is disposed so as to face the movable scroll 13, the middle housing 11 fixed in the housing body 2 a, the movable scroll 13 revolving by the crank mechanism 12 supported by the bearing 7 provided in the middle housing 11, and the movable scroll 13. Both are provided with a fixed scroll 15 forming a working chamber 14.

  The movable scroll 13 has a substantially disk shape. The movable scroll 13 has an involute curve standing from the end surface toward the fixed scroll 15 side, and an end surface opposite to the movable side spiral 16. And a boss portion 17 standing in a cylindrical shape toward the middle housing 11 side.

  The fixed scroll 15 includes a fixed side spiral 18 formed by a spiral groove provided on the end face on the movable scroll 13 side.

  The middle housing 11 has a three-stage cylindrical shape that gradually increases in diameter from the motor unit 3 side toward the fixed scroll 15 side. The smallest diameter cylinder 19a close to the motor unit 3 constitutes the bearing 7 and is the middle. The cylinder 19b accommodates the crank mechanism 12, the cylinder 19c having the largest diameter close to the fixed scroll 15 accommodates the movable scroll 13 therein, and is fixed to the inner peripheral surface of the housing body 2a by fixing means such as shrink fitting. Yes.

  A suction chamber 20 is formed on the outer peripheral side between the movable scroll 13 and the fixed scroll 15, and communicates with a working chamber 14 formed by the fixed scroll 15 and the movable scroll 13 toward the center side. The suction chamber 20 is a space surrounded by the movable scroll 13 and the fixed scroll 15 and the large diameter cylinder 19 c of the middle housing 11. Further, the suction chamber 21 is connected to the suction chamber 20 through the housing body 2a so as to be able to suck the refrigerant.

  The crank mechanism 12 includes an eccentric portion 22 that is integrally provided at the end portion of the shaft 8 on the compression mechanism portion 4 side, and a boss portion 17 of the movable scroll 13. The eccentric portion 22 is provided so as to be eccentric by a predetermined amount from the shaft centers of the bearing 7 and the bearing 6. This amount of eccentricity becomes the revolution radius of the movable scroll 13.

An anti-rotation means (not shown) is arranged on the end surface of the large-diameter cylinder 19c constituting the middle housing 11 on the movable scroll 13 side to prevent the movable scroll 13 from rotating. Thereby, only the revolution of the movable scroll 13 is permitted.
Further, a slide bearing (not shown) is interposed between the large-diameter cylinder 19c of the middle housing 11 and the end surface of the movable scroll 13 on the side where the boss portion 17 is provided.

  With the configuration as described above, the compression mechanism unit 4 reduces the volume of the plurality of working chambers 14 formed by the engagement of the movable-side spiral 16 and the fixed-side spiral 18 as the movable scroll 13 pivots with respect to the fixed scroll 15. Thus, the refrigerant supplied to the suction chamber 20 communicating with the outermost peripheral side of the fixed-side spiral 18 is compressed.

Further, a discharge port 23 that penetrates the fixed scroll 15 in the axial direction is provided at the center of the fixed-side spiral 18 in the compression mechanism unit 4.
The refrigerant compressed by the movable scroll 13 and the fixed scroll 15 is discharged from the discharge port 23 to the oil separation means 5 (described later) through a discharge valve 24 for preventing backflow.

Next, the oil separation means 5 will be described. The oil separating means 5 has a lubricating oil separator 25 that separates the lubricating oil from the refrigerant compressed by the compression mechanism section 4 by a centrifugal method.
The lubricant separator 25 includes an introduction path 25a, a separation pipe 25b, and a discharge path 25c.
The separation pipe 25 b has a substantially cylindrical shape, and its downstream end communicates with the discharge port 26. The separation pipe 25b is disposed in a separation chamber 25d that forms a cylindrical space coaxial with the separation pipe 25b. The separation chamber 25d communicates with an introduction path 25a for introducing the refrigerant compressed by the compression mechanism unit 4. In this case, the inflow direction of the refrigerant passing through the introduction path 25a is preferably substantially parallel to the tangential direction of the circumferential surface constituting the separation chamber 25d.

A mechanism configuration for circulating lubricating oil in the compressor 1 as described above will be described.
Lubricating oil is supplied to the compression mechanism part 4 in the housing main body 2a formed at a relatively low pressure by the differential pressure forming means described later as the movable part of the compression mechanism part 4 operates.
For this purpose, a lubricating oil return passage 28 is formed so as to penetrate from the oil storage chamber 27 that temporarily stores oil through the discharge passage 25c in the oil separation means 5 to the fixed scroll 15 below the discharge port 23 as a passage for lubricating oil. ing.

The lubricating oil return passage 28 penetrating the fixed scroll 15 is connected to a return passage 29 formed in the cylinder 19 c of the middle housing 11. Further, the passage 29 reaches a bearing (not shown) on the contact surface with the movable scroll 13.
Next, from the bearing, the gap between the cylinder 19 b of the middle housing 11 and the boss portion 17, the space between the eccentric portion 22 at the tip of the shaft 8 and the boss portion 17, and the space between the end portion of the shaft 8 and the bottom surface of the boss portion 17 are reached. It is configured.
In that case, the return passage 29 formed in the cylinder 19 c of the middle housing 11 and the gap between the cylinder 19 b of the middle housing 11 and the boss portion 17 are intermittently communicated by the revolving motion of the movable scroll 13. The return passage 29, the cylinder 19b of the middle housing 11 and the gap between the boss portion 17 function as decompression means for decompressing to a desired pressure by intermittent communication.

The space between the end portion of the shaft 8 and the bottom surface of the boss portion 17 communicates with the lubricating oil passage 30 that penetrates the shaft 8 in the axial direction.
The lubricating oil passage 30 has different inner diameters on the upstream side and the downstream side. In this case, in the lubricating oil passage 30 in the shaft 8, the inner diameter d1 on the upstream side and the inner diameter d2 on the downstream side are set to satisfy d1 <d2.
The lubricating oil passage 30 is provided with oil supply holes 30 a and 30 b at portions corresponding to the bearings 7 and 6 so as to branch from the lubricating oil passage 30.

  In addition, the lower part of the whole area | region in the housing main body 2a comprises the low pressure oil storage chamber 31, and it is made to store the lubricating oil which passed the lubricating oil channel | path 30.

  A lubricating oil return hole 32 is provided in the large-diameter cylinder 19c of the middle housing 19 so that the lubricating oil stored in the low-pressure oil storage chamber 31 can be returned to the movable scroll 13 side.

  Further, a support plate 33 is provided on the end housing 2b side of the housing main body 2a, to which a bearing 6 that rotatably supports the shaft 8 is fixed. Lubricating oil contained in the refrigerant flows into and accumulates in the space surrounded by the support plate 33 and the end housing 2b through the upper passage 34, the lower passage 35, and the central passage 36 provided in the support plate 33. Become. The central passage 35 communicates with the lubricating oil passage 30 extending in the entire axial direction of the shaft 8.

Here, the differential pressure forming means disposed in the housing body 2a will be described.
The differential pressure forming means is formed inside a pipe fixed to the housing body 2a. A through-hole penetrating the side wall of the pipe is provided at a position downstream of the suction port 21 and upstream of the suction chamber 20 on the inner wall surface of the pipe. This through hole is connected to a communication passage 37 provided so as to penetrate the cylinder 19c in the middle housing 11 and communicate with the electric motor chamber 3a. The communication passage 37 is a pressure introduction path that guides the pressure in the suction port 21 region to the motor chamber 3a.

In the suction port 21, a small-diameter passage 38 is formed in a cylindrical passage corresponding to the upstream side of the suction chamber 20. The cross-sectional area perpendicular to the flow direction of the small-diameter passage 38 is much smaller than the cross-sectional area perpendicular to the flow direction of the passage located upstream of the passage to constitute the throttle portion 39.
By this throttle 39, the suction chamber 20 is set to be in a lower pressure region than the suction port 21 region.
Further, by using the throttle portion 39, a pipe forming a cylindrical passage is processed so that the refrigerant pressure difference can be easily set between the suction port 21 and the suction chamber 20.
Even if the pressure on the high pressure side is not sufficiently high, the throttle portion 39 is configured to generate a differential pressure between the suction chamber 20 and the motor chamber 3a in which the motor portion 3 is disposed.

Further, the cross-sectional area perpendicular to the flow direction of the communication passage 37 is smaller than the cross-sectional area perpendicular to the flow direction of the cylindrical passage, and further smaller than the cross-sectional area perpendicular to the flow direction of the small diameter passage 38. preferable.
When the refrigerant flows through the compressor 1 by the communication passage 37 and the throttle portion 39, the suction chamber 20 is set to a lower pressure region than the suction port 21 region, and the refrigerant has a pressure higher than the pressure of the suction chamber 20. Is allowed to act as a differential pressure forming means for making the pressure in the motor chamber 3 a higher than the pressure in the suction chamber 20.

The operation and action of the compressor 1 configured as described above will be described.
When the motor unit 3 of the compressor 1 is started and the compression mechanism unit 4 is operated, a part of the refrigerant recirculated from the refrigerant circuit introduces pressure in the region of the suction port 21 from the suction port 21 to the motor chamber 3a. The refrigerant flows into the motor chamber 3 a through the communication passage 37 as a route, and the remaining refrigerant flows into the suction chamber 20 communicating with the outermost peripheral side of the fixed spiral 26 through the small diameter passage 38 of the suction port 21 and the throttle portion 39.
When a refrigerant having a pressure higher than the refrigerant pressure in the suction chamber 20 is sent to the electric motor chamber 3a, the electric pressure in the electric motor chamber 3a is increased and separated from the refrigerant in the electric motor chamber 3a and collected in the low-pressure oil storage chamber 31 below the housing body 2a. The oil level of the lubricating oil exhibits a stable behavior when the pressure in the motor chamber 3a is increased.

On the other hand, when the shaft 18 of the electric motor unit 3 rotates, the movable scroll 13 turns with respect to the fixed scroll 23, and the volumes of the plurality of working chambers 14 formed by the engagement of the movable side spiral 24 and the fixed side spiral 26 are reduced. Thus, the refrigerant flowing into the suction chamber 20 can be compressed to increase the pressure.
When the refrigerant reaches a predetermined discharge pressure, the refrigerant pushes the discharge valve 24 for preventing backflow from the discharge port 23 and discharges it to the oil separating means 5.
Further, the refrigerant flows from the discharge chamber through the introduction path 25a of the lubricating oil separator 25 into the separation chamber 25d. At this time, the refrigerant flows downward while swirling between the separation pipe 25b and the inner wall surface of the separation chamber 25d, and the refrigerant gas having a small specific gravity flows into the pipe passage extending upward from the lower end through hole of the separation pipe 25b. Then, it can be discharged from the discharge port 26 toward the external circuit.

On the other hand, the lubricating oil having a large specific gravity contained in the refrigerant is separated to the inner wall side of the separation chamber 25d by centrifugal force and descends by gravity. The lowered lubricating oil is temporarily stored in the oil storage chamber 27. The lubricating oil passes through the lubricating oil return passage 28 provided in the fixed scroll 15 and the return passage 29 formed in the cylinder 19c of the middle housing 11 from the oil storage chamber 27 due to the pressure difference between the separation chamber 25d and the electric motor chamber 3a. The bearing reaches the contact surface with the movable scroll 13.
Here, in the return passage 29 formed in the cylinder 19 c of the middle housing 11, the clearance between the cylinder 19 b of the middle housing 11 and the boss portion 17 is intermittently communicated by the revolving motion of the movable scroll 13. The lubricating oil can be depressurized. A part of the refrigerant dissolved in the lubricating oil is separated by the decompression, and the end of the shaft 8 is removed from the gap between the cylinder 19b of the middle housing 11 and the boss portion 17 in a gas-liquid two-phase state. To the space between the bottom and the bottom surface of the boss part 17.

  When the lubricating oil reaches the lubricating oil passage 30 penetrating in the axial direction inside the shaft 8 from the space between the end portion of the shaft 8 and the bottom surface of the boss portion 17 in the gas-liquid two-phase state, the shaft 8 moves at high speed. Since the oil is rotating, the oil and the refrigerant flow as a drift that is biased toward the inner wall surface of the lubricating oil passage 30 by the centrifugal separation of the oil and the refrigerant (see FIG. 3).

By the way, the lubricating oil passage 30 is formed so that the inner diameter, that is, the inner diameter d1 on the upstream side and the inner diameter d2 on the downstream side satisfy d1 <d2, so that the flow resistance increases due to the viscosity of the lubricating oil. However, the lubricating oil can be sent downstream without being obstructed. As a result, the bearing 6 can be lubricated from the upstream oil supply hole 30a through the downstream oil supply hole 30b as well as the bearing 7.
As described above, the lubricating oil flows out from the lubricating oil passage 30 through the central passage 35 and accumulates in the low-pressure oil storage chamber 31 below the housing body 2a.
The lubricating oil stored in the low-pressure oil storage chamber 31 can be returned to the movable scroll 13 side through the lubricating oil return hole 32 into the large-diameter cylinder 19 c of the middle housing 19.

  Thus, in the above-described compressor 1, the lubricating oil returned from the oil separating means 5 is supplied from the oil storage chamber 27 to the lubricating oil return passage provided in the fixed scroll 15 by the pressure difference between the separation chamber 25d and the electric motor chamber 3a. 28, through the return passage 29 formed in the cylinder 19c of the middle housing 11, reaches the bearing on the contact surface with the movable scroll 13 and is decompressed by the operation of the movable scroll 13, and the cylinder 19b and the boss portion of the middle housing 11 The lubricating oil passage 30 penetrating in the axial direction inside the shaft 8 from the gap between the spaces 17, the space between the eccentric portion 22 at the tip of the shaft 8 and the boss portion 17, and the end portion of the shaft 8 and the bottom surface of the boss portion 17 At this time, the bearing 7 and the bearing 6 supporting the shaft 8 can be lubricated through the oil supply holes 30a and 30b.

  Since the lubricating oil passage 30 is formed so that the inner diameter d1 on the upstream side and the inner diameter d2 on the downstream side satisfy d1 <d2, the lubricating oil is separated into the lubricating oil passage 30 by the centrifugal separation action. Even when the flow resistance is biased toward the wall surface and the flow resistance due to viscosity increases, the flow of oil is not hindered and the lubricating oil can be sent downstream, and the bearing 7 and bearing 6 that support the shaft 8 are lubricated. be able to.

  As described above, the lubricating oil passage 30 in the shaft 8 is formed so that the inner diameter d1 on the upstream side and the inner diameter d2 on the downstream side satisfy d1 <d2. (1) Inferior lubrication of the downstream bearing, and (2) Burrs will not cause damage to the sliding parts such as the bearing and scroll.

FIG. 4 shows a compressor 1 according to the second embodiment. The lubricating oil passage 30 in the shaft 8 forms the inner diameter of the lubricating oil passage 30 as follows.
That is, the inner diameter d2 of the eccentric lubricating oil passage 30 is the same as that of the eccentric portion 22 side of the shaft 8 that is upstream of the lubricating oil passage 30 and the downstream lubricating oil passage 30, and d1 <d2 Can be formed.
Since other configurations are substantially the same as those in the first embodiment, the description thereof is omitted individually.

  Even with such a configuration, even if the lubricating oil is drifted due to centrifugal separation and the oil content is biased toward the inner wall surface side of the lubricating oil passage 30, the inner diameter is increased on the upstream side and the downstream side. Due to the viscosity of the oil, it is possible to prevent the downstream bearing from becoming poorly lubricated due to the flow hindrance caused by the increase in flow resistance.

  Although the electric scroll type compressor has been described as an example of the compressor in the above embodiment, the compressor in the present invention has a configuration in which the motor chamber and the compression chamber are not formed in one chamber. Anything can be used, and a rolling piston type compressor can also be used.

It is a mimetic diagram showing the heat pump type hot water supply machine containing the compressor in a 1st embodiment of the present invention. It is sectional drawing which shows the internal structure of the compressor in 1st Embodiment. It is typical explanatory drawing which showed the cross-section of the shaft of the compressor in 1st Embodiment, and the lubrication effect | action. It is sectional drawing which shows the internal structure of the compressor in 2nd Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 2 Housing 2a Housing main body 2b, 2c End part housing 3 Electric motor part 3a Electric motor room 4 Compression mechanism part 5 Oil separation means 6, 7 Bearing 8 Shaft 9 Rotor 10 Stator 11 Middle housing 12 Crank mechanism 13 Movable scroll 14 Operating chamber DESCRIPTION OF SYMBOLS 15 Fixed scroll 16 Movable side spiral 17 Boss part 18 Fixed side spiral 19a, 19b, 19c Cylinder 20 Suction chamber 21 Suction port 22 Eccentric part 23 Discharge port 24 Discharge valve 25 Lubricating oil separator 25a Inlet path 25b Separation pipe 25c Discharge path 26 Discharge port 27 Oil storage chamber 28 Lubricating oil return passage 29 Return passage 30 Lubricating oil passage 31 Low pressure oil storage chamber 32 Lubricating oil return hole 33 Support plate 34 Upper passage 35 Lower passage 36 Central passage 37 Connection passage 38 Small diameter passage 39 Restriction portion

Claims (6)

In the compressor (1) in which the compression mechanism (4) for compressing the refrigerant is built in the housing (2),
Oil separation means (5) for separating oil from the refrigerant compressed by the compression mechanism section (4);
A drive unit (3) for driving the compression mechanism unit (4) via a shaft (8);
A plurality of bearings (6, 7) supporting the shaft (8);
With
The shaft (8) has a lubricating oil passage (30) for supplying oil to the bearings (6, 7) and oil supply holes (30a, 30b) in the shaft (8),
For the lubricating oil passage (30) in the shaft (8), at least the inner diameter of the lubricating oil passage (30) at the axial position where the oil supply hole (30b) to the downstream bearing (6) is located The compressor characterized by being equal to or greater than the inner diameter of the lubricating oil passage (30) at the axial position. An oil separation means (5) for separating the lubricating oil from the refrigerant compressed by the compression mechanism section (4), the interior of the housing (2) being lower than the discharge pressure;
A lubricating oil supply path for guiding the lubricating oil separated by the oil separating means (5) to the shaft (8) of the drive unit (3);
Pressure reducing means provided in the lubricating oil supply path;
The compressor according to claim 1, further comprising: The compression mechanism (4) includes a working chamber (14) for sucking and compressing refrigerant,
An inlet (21) for taking refrigerant from an external circuit into the working chamber (14);
A suction chamber (20) provided on the downstream side of the suction port (21) and communicating with the working chamber (14) and having a lower pressure region than the suction port (21) region;
The compressor according to claim 1, further comprising: The compression mechanism (4) is fixed to the housing body (2a), and has a fixed scroll (24) having a fixed spiral part (18);
A movable scroll (17) comprising a movable swirl (16) meshing with the fixed swirl (18) to form a working chamber (14);
Have
The compressor according to any one of claims 1 to 3, wherein the suction port (21) is provided on a side of the working chamber (14).   The drive unit (3) has a drive unit chamber (3a) in which the lubricating oil separated from the refrigerant is accumulated in the lower part of the housing (2), which is higher than the pressure of the suction chamber (20) by the differential pressure forming means. The compressor according to claim 1 or 2, characterized in that the compressor is disposed in the inside. The refrigerant taken into the compression mechanism unit (4), of the claims 1 to 5 further characterized in that the main component CO _2, compressor as claimed in any one.

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