WO2019017144A1

WO2019017144A1 - Compressor

Info

Publication number: WO2019017144A1
Application number: PCT/JP2018/023644
Authority: WO
Inventors: 孝幸桑原; 藤田　勝博; 竹内　真実
Original assignee: 三菱重工サーマルシステムズ株式会社
Priority date: 2017-07-20
Filing date: 2018-06-21
Publication date: 2019-01-24
Also published as: JP6953213B2; JP2019019790A; US20210102538A1

Abstract

Provided is a compressor which enables reliable separation of oil from a refrigerant gas while suppressing increases in the size of equipment and manufacturing costs. This compressor (1) is provided with: a housing (2); a compression mechanism (13) which compresses a refrigerant gas flowing into an intake space (Ss); an oil separation space (So) which separates oil from the refrigerant gas compressed by the compression mechanism (13) and guides the oil to a discharge pipe (40); and a separation cylinder (30) which is disposed along an axial line (X2) of the oil separation space (So) over the oil separation space (So) in the gravitational direction. The separation cylinder (30) has a small-diameter section, and a large-diameter section formed under the small-diameter section in the gravitational direction; the oil separation space (So) has a separation section in which the small-diameter section and the large-diameter section are disposed, and which has a first inner diameter larger than a second outer diameter of the large-diameter section, and an oil storage section disposed under the separation section; and the refrigerant gas compressed by the compression mechanism (13) flows into the separation section.

Description

Compressor

The present invention relates to a compressor.

Conventionally, in a compressor provided in a vehicle air conditioner or the like, it is known to provide an oil separation mechanism so as not to discharge lubricating oil contained in a refrigerant to other than the compressor (for example, Patent Document 1) , 2)).
Patent Document 1 discloses that the refrigerant guided to the separation chamber 11 is swirled in a cylindrical space in which the separation pipe 12a is disposed to separate the lubricating oil and discharge the separated lubricating oil to the oil storage chamber 15 ing.
In Patent Document 2, the oil separation chamber 20 and the oil reservoir 25 are formed as one space, and the refrigerant gas in which the oil is separated from the small holes 32 formed in the small diameter portion 29 of the oil separation cylinder 26 is an internal space 33. It is disclosed to lead to.

JP 2001-295767 A JP, 2014-20306, A

However, the mechanism disclosed in Patent Document 1 is a mechanism provided with an oil storage chamber 15 for storing the lubricating oil separated separately from the separation chamber 11 for separating the lubricating oil from the refrigerant. Therefore, a sufficient space for providing two spaces is required, and the enlargement of the compressor can not be suppressed. Moreover, since it is the complicated shape which provided two space, a manufacturing cost will increase.

On the other hand, in the mechanism disclosed in Patent Document 2, since the oil separation chamber 20 and the oil reservoir 25 are formed as one space, downsizing of the compressor can be realized. However, in the mechanism disclosed in Patent Document 1, the small diameter portion 29 is formed on the side of the oil reservoir 25 below the oil separation cylinder 26, and the small holes 32 for guiding the refrigerant to the internal space 33 are formed in the small diameter portion 29. It is done. Therefore, the oil is wound up from the oil reservoir 25 below the oil separation cylinder 26 by the swirling flow of the refrigerant gas, and the oil is taken into the internal space 33 from the small holes 32 and the oil is not sufficiently separated from the refrigerant gas. There is a possibility of

The present invention has been made in view of such circumstances, and provides a compressor capable of reliably performing oil separation from refrigerant gas while suppressing increase in size of the device and increase in manufacturing cost. The purpose is to

In order to solve the above-mentioned subject, a compressor of the present invention adopts the following means.
A compressor according to one aspect of the present invention includes: a housing forming a suction space for a refrigerant gas therein; a compression mechanism disposed in the housing; and compressing the refrigerant gas flowing into the suction space; And an oil separation space for separating oil from the refrigerant gas compressed by the compression mechanism and guiding the oil to a discharge pipe, and the oil separation space above the oil separation space in the gravity direction. A cylindrical member disposed along an axis of the cylindrical member, the cylindrical member being formed at a small diameter portion having a first outer diameter, and below the gravity direction of the small diameter portion, the first outer diameter A large diameter portion having a second outer diameter larger than the first small diameter portion; and an introduction port for guiding the refrigerant gas from the lower end of the small diameter portion to the internal space of the cylindrical member; And the large diameter portion A first space portion having a first inner diameter larger than the second outer diameter, and a second space portion disposed below the first space portion in the direction of gravity, and compressed by the compression mechanism The refrigerant gas flows into the first space portion.

According to the compressor of this aspect, the refrigerant gas compressed by the compression mechanism flows into the first space portion, and the space between the outer peripheral surface of the cylindrical member and the inner peripheral surface of the first space portion is about the axis. To turn. The oil contained in the refrigerant gas is separated from the refrigerant gas by centrifugal force during swirling, adheres to the inner peripheral surface of the first space, and is transmitted along the inner peripheral surface and is disposed in the second space located below in the direction of gravity. It is led to the circumference. The oil guided to the inner circumferential surface of the second space moves downward by gravity to form an oil sump below the second space.
The refrigerant gas from which the oil is separated in the first space portion is led from the inlet formed in the small diameter portion of the cylindrical member to the internal space of the cylindrical member and further led to the discharge piping. Below the small diameter portion of the cylindrical member, a large diameter portion having an outer diameter larger than that of the small diameter portion is formed. Therefore, when the refrigerant gas swirling in the first space portion reaches the lower end of the small diameter portion, the distance between the inner peripheral surface of the first space portion and the outer peripheral surface of the large diameter portion is small. A large amount of introduction to the lower second space is suppressed. Therefore, it is suppressed that a large amount of refrigerant gas rolls up the oil accumulation below the 2nd space part.

Thus, according to the compressor of the aspect, the oil is separated from the refrigerant gas in the first space above the oil separation space, and an oil reservoir is formed in the second space below the first space. Can. Since it is not necessary to separately provide a space for oil separation and a space for oil accumulation, it is possible to suppress an increase in size of the device and an increase in manufacturing cost.
In addition, since a large amount of the swirling flow of the refrigerant gas is guided from the first space portion to the second space portion to prevent the oil reservoir from being wound up, oil can be reliably separated from the refrigerant gas.

In the compressor according to one aspect of the present invention, the large diameter portion is formed in a tapered shape in which the outer diameter gradually increases from the first outer diameter to the second outer diameter from the upper side to the lower side in the gravity direction. It may be
In this way, it is possible to appropriately prevent the refrigerant gas from being guided to the second space while circulating the swirling flow of the refrigerant gas led to the large diameter portion without disturbance.

In the compressor according to one aspect of the present invention, the refrigerant gas compressed by the compression mechanism flows in from above the small diameter portion, and the inlet is formed at the lower end of the small diameter portion in the gravity direction. It is also good.
In this manner, the swirling flow of the refrigerant gas can be formed in a wide range from the upper side to the lower side of the first space portion, and the oil can be appropriately separated from the refrigerant gas.

In the compressor according to one aspect of the present invention, the compression mechanism arranges the pair of fixed scrolls and the orbiting scroll to face each other, and rotationally drives the orbiting scroll with respect to the stationary scroll to rotate the refrigerant gas It may be a mechanism for compressing the
In this way, in the scroll compressor, the oil can be reliably separated from the refrigerant gas while suppressing the increase in size of the device and the increase in manufacturing cost.

According to the present invention, it is possible to provide a compressor capable of reliably performing oil separation from a refrigerant gas while suppressing an increase in size of the device and an increase in manufacturing cost.

It is a longitudinal section of a scroll compressor concerning one embodiment of the present invention. It is AA arrow sectional drawing of a scroll compressor shown in FIG. It is the elements on larger scale of the oil separation space part of the rear housing shown in FIG. It is the elements on larger scale which show the modification of the oil separation space part of the rear housing shown in FIG. It is the side view which looked at the rear housing shown in FIG. 1 from the compression mechanism side.

Hereinafter, an embodiment of a compressor according to the present invention will be described with reference to the drawings.
FIG. 1 shows a longitudinal sectional view of a scroll compressor according to an embodiment of the present invention, and FIG. 2 shows a sectional view taken along the line AA of FIG.

As shown in FIG. 1, the scroll compressor 1 according to the present embodiment includes a cylindrical housing 2 forming an outer shell, a compression mechanism 13 housed inside the housing 2, and oil formed in the housing 2. A separation space So and a separation cylinder (cylindrical member) 30 disposed above the oil separation space So are provided.
The housing 2 has a front housing 3 and a rear housing 4. The front housing 3 and the rear housing 4 are fastened by fastening bolts (not shown) so as to form a suction space Ss of the refrigerant gas inside.

On the front housing 3 side inside the housing 2, a crankshaft 5 is rotatably supported around an axis X1 via a main bearing 6 and a sub bearing (not shown). One end side (left side in FIG. 1) of the crankshaft 5 penetrates the front housing 3 and protrudes to the left side of FIG. 1, and the electromagnetic clutch 7 and the pulley 8 are provided at the protruding portion. Power is input to the pulley 8 from a drive source such as an engine via a drive belt (not shown). A mechanical seal or lip seal is provided between the main bearing 6 and the sub-bearing to seal between the inside of the housing 2 and the atmosphere.

On the other end side (right side in FIG. 1) of the crankshaft 5, a crank pin 9 whose center axis is offset by a predetermined dimension with respect to the axis X1 is integrally provided. The crank pin 9 is connected to an orbiting scroll 15 described later via a drive bush 10 and a drive bearing 11. The orbiting scroll 15 pivots around the axis X1 by transmitting the driving force with which the crankshaft 5 rotates around the axis X1 via the crank pin 9.

The drive bush 10 is integrally formed with a balance weight 12 for removing an unbalanced load generated when the orbiting scroll 15 pivots about the axis X1. The balance weight 12 pivots about the axis X1 together with the orbiting scroll 15. A driven crank mechanism (not shown) is provided between the drive bush 10 and the crankpin 9 to make the turning radius of the turning scroll 15 variable.

Inside the housing 2, a compression mechanism 13 constituted by a pair of fixed scroll 14 and orbiting scroll 15 is incorporated. The compression mechanism 13 is a mechanism that compresses the refrigerant gas flowing into the suction space Ss and discharges the compressed refrigerant gas to the discharge space Sd. The fixed scroll 14 is composed of an end plate 14A and a spiral wrap 14B erected from the end plate 14A. The orbiting scroll 15 is composed of an end plate 15A and a spiral wrap 15B erected from the end plate 15A.

The fixed scroll 14 and the orbiting scroll 15 are provided with

step portions

14C, 15C and 14D, 15D at predetermined positions along the spiral direction of the tooth crests and tooth bottoms of the spiral wraps 14B, 15B as shown in FIG. It is supposed to be configured. The tooth tip surface on the outer peripheral side in the direction of the pivot axis is high and the tooth tip surface on the inner peripheral side is low on the tooth tip side with the

step portions

14C, 15C and 14D, 15D as boundaries. Further, on the tooth base side, the tooth base on the outer peripheral side in the direction of the pivot axis is low, and the tooth base on the inner peripheral side is high. Thus, in the spiral wraps 14B and 15B, the wrap height on the outer peripheral side is higher than the wrap height on the inner peripheral side.

The fixed scroll 14 and the orbiting scroll 15 are disposed in such a manner that the central axes of the fixed scroll 14 and the orbiting scroll 15 are displaced by the distance of the orbiting radius of the orbiting scroll 15 and the spiral wraps 14B and 15B face each other. The fixed scroll 14 and the orbiting scroll 15 mesh the spiral wraps 14B and 15B by shifting the phase of the spiral wraps 14B and 15B 180 degrees so that a slight clearance (tens of tens) is obtained between the tip and bottom surfaces of the spiral wraps 14B and 15B. To several hundred microns). As a result, a pair of suction volumes (compression chambers) 16 formed by the

end plates

14A, 15A and the spiral wraps 14B, 15B between the fixed scroll 14 and the orbiting scroll 15 is 180 degrees with respect to the central axis. It is formed by phase difference.

In the suction volume 16, the height of the spiral wraps 14B and 15B is higher than the height on the inner peripheral side on the outer peripheral side, and the refrigerant gas is compressed in both the circumferential direction and height direction of the spiral wraps 14B and 15B. The compression mechanism 13 is capable of three-dimensional compression. Although the compression mechanism 13 is provided with the

step portions

14C, 15C and 14D, 15D, it may be a compression mechanism having no step portion.

The fixed scroll 14 is fixed to the inner surface of the rear housing 4 via a fastening bolt (not shown). In the orbiting scroll 15, a crank pin 9 provided on one end side of the crankshaft 5 is connected via a drive bush 10 and a drive bearing 11 to a bearing boss provided on the back of the end plate 15A. There is. Further, the orbiting scroll 15 has a back surface of the end plate 15A supported by the thrust bearing surface 3A of the front housing 3 via a rotation preventing mechanism (not shown) provided between the thrust bearing surface 3A and the back surface of the end plate 15A. The rotation is driven to revolve around the fixed scroll 14 while rotation is prevented.

In the fixed scroll 14, a discharge port 17 for discharging the refrigerant gas compressed by the compression mechanism 13 is formed at a central portion of the end plate 14 </ b> A. A discharge reed valve 19 is installed at the discharge port 17 via a retainer 18. Further, a seal member (not shown) is disposed between the rear surface on the outer peripheral side of the end plate 14A of the fixed scroll 14 and the inner surface of the rear housing 4. Between the rear surface of the end plate 14A and the inner surface of the rear housing 4, a discharge space Sd divided from the suction space Ss of the housing 2 is formed. The high temperature / high pressure refrigerant gas compressed by the compression mechanism 13 is discharged to the discharge space Sd via the discharge port 17.

The suction space Ss in the housing 2 communicates with the suction port 20 provided in the upper portion of the front housing 3. The low temperature low pressure refrigerant gas is supplied to the suction port 20 from the refrigeration cycle side. The low-temperature low-pressure refrigerant gas supplied to the suction space Ss is drawn into two suction volumes (compression chambers) 16 formed with a phase difference of 180 degrees with the fixed scroll 14 by the turning drive of the turning scroll 15. It is compressed.

As shown in FIGS. 1 and 2, the low temperature refrigerant gas sucked into the suction space Ss from the suction port 20 is sucked into the suction volume (compression chamber) 16 on the side near the suction port 20 as shown by the arrow a. Be done. On the other hand, the low temperature refrigerant gas sucked from the suction port 20 into the suction space Ss is sucked into the suction volume (compression chamber) 16 on the side far from the suction port 20 as shown by the arrow b. The refrigerant gas sucked into the suction volume 16 is compressed and led from the discharge port 17 to the discharge space Sd.

Next, a mechanism for separating oil from the refrigerant gas compressed by the compression mechanism 13 and guided to the discharge space Sd and guiding the refrigerant gas from which the oil is separated to the discharge pipe 40 will be described. This mechanism is a mechanism for separating the refrigerant gas flowing from the discharge space Sd into the oil separation space So in the oil separation space So by the separation cylinder 30.
Hereinafter, description will be made with reference to FIG. 1, FIG. 3, and FIG. FIG. 3 is a partially enlarged view of the oil separation space So of the rear housing 4 shown in FIG. FIG. 4 is a side view of the rear housing 4 shown in FIG. 1 as viewed from the compression mechanism 13 side.

As shown in FIG. 1, an oil separation space So is formed in the rear housing 4 to separate oil from the refrigerant gas compressed by the compression mechanism 13 and guide the oil to the discharge pipe 40. The oil separation space So is a space having a circular cross-sectional view in the horizontal direction, and is formed along an axis X2 extending in the vertical direction. As shown in the partial enlarged view of FIG. 3, the diameter of the cross section in the horizontal direction of the oil separation space So is a constant first inner diameter Di1 at any position in the vertical direction. Therefore, the oil separation space So can be formed by a relatively simple operation of forming a hole of a predetermined first inner diameter Di1 along the axis X2 after the rear housing 4 is manufactured by casting.

As shown in FIGS. 1 and 3, in the oil separation space So, a separation cylinder 30 is disposed along an axis X2 extending in the vertical direction. The separation cylinder 30 is a cylindrical member formed so as to have a circular outer diameter and an inner diameter in a horizontal cross section.
As shown in FIG. 3, the separation cylinder 30 has a small diameter portion 31 having a first outer diameter Do1, and a large diameter formed below the small diameter portion 31 and having a second outer diameter Do2 larger than the first outer diameter Do1. It has a portion 32, an inlet 33 formed in the small diameter portion 31 for guiding the refrigerant gas to the internal space Si of the separation cylinder 30, and a flange 34 for sealing the opening at the upper end of the oil separation space So.

As shown in FIG. 3, the large diameter portion 32 is formed in a tapered shape in which the outer diameter gradually increases from the first outer diameter Do1 to the second outer diameter Do2 from the upper side to the lower side in the vertical direction. Further, the inlets 33 are formed at a plurality of locations around the axis X2 (for example, 2 locations spaced 180 degrees around the axis X2, or 4 locations spaced 90 degrees around the axis X2) .

As shown in FIG. 3, the flange portion 34 is formed with a recess 34 a into which the tip portion 40 a of the discharge pipe 40 for transporting the refrigerant gas guided from the internal space Si of the separation cylinder 30 is inserted. As shown in FIG. 1, a through hole 34 b is formed in the flange portion 34, and a through hole 41 is formed in the discharge pipe 40. In addition, a fastening hole 21 is formed in the rear housing 4. The discharge piping 40 and the flange portion 34 of the separation cylinder 30 are fixed to the rear housing 4 by fastening fastening bolts (not shown) inserted into the through holes 34 b and the through holes 41 to the fastening holes 21.

In the scroll compressor 1 according to the present embodiment, the front end portion 40a of the discharge pipe 40 is not directly inserted into the oil separation space So, but is formed in the flange portion 34 of the separation cylinder 30 inserted into the oil separation space So. Are inserted into the recess 34a. Therefore, for example, the inner diameter of the oil separation space So can be increased without changing the shape of the distal end portion 40 a of the discharge pipe 40.

For example, as shown in the modification of FIG. 4, the inner diameter of the oil separation space So is set to a second inner diameter Di2 larger than the first inner diameter Di1 shown in FIG. 3 without changing the shape of the tip portion 40a of the discharge piping 40. be able to. By increasing the inner diameter of the oil separation space So, it is possible to increase the centrifugal force for separating the oil when forming the swirling flow Fs of the refrigerant gas described later, and to improve the oil separation performance.
In FIG. 4, the shape of the flange portion 34A and the recess 34Aa of the separation cylinder 30A is set according to the second inner diameter Di2 of the oil separation space So, without changing the shape of the tip portion 40a of the discharge piping 40. The inner diameter of the oil separation space So is increased.

As shown in FIG. 3, the oil separation space So includes a separation portion (first space portion) So1 in which the small diameter portion 31 and the large diameter portion 32 are disposed, and oil storage disposed below the separation portion So1 in the vertical direction. And a part (second space part) So2. As shown in FIG. 3, the first inner diameter Di1 of the separation portion So1 is larger than the second outer diameter Do2 of the large diameter portion 32.

Here, a mechanism for separating the oil from the refrigerant gas in the oil separation space So in which the separation cylinder 30 is disposed will be described.
The refrigerant gas compressed by the compression mechanism 13 and guided to the discharge space Sd flows from the two inlets 22 to the upper side of the separation part So1 of the oil separation space So. Since the small diameter portion 31 of the separation cylinder 30 is disposed in the separation portion So1, the separation portion So1 is a cylindrical space extending along the axis X2. Therefore, the refrigerant gas flowing into the separation part So1 from the inflow port 22 forms a swirling flow Fs, and is guided to the introduction port 33 formed at the lower end of the small diameter portion 31 while swirling around the axis X2.

The oil contained in the refrigerant gas is separated from the refrigerant gas by the centrifugal force when the refrigerant gas turns into the swirling flow Fs and swirls the separation part So1. The oil separated from the refrigerant gas adheres to the inner peripheral surface of the separation portion So1, and is guided along the inner peripheral surface to the inner peripheral surface of the lower oil storage portion So2. The oil guided to the inner circumferential surface of the oil storage portion So2 moves downward by gravity, and forms an oil reservoir Os below the oil storage portion So2.

As shown in FIG. 5, the position at which the inlet 22 for flowing the refrigerant gas from the discharge space Sd into the oil separation space So is located is closer to the inner circumferential surface of the oil separation space So than the axis X2. There is. This is in order to form a swirling flow Fs in which the refrigerant gas flowing into the oil separation space So swirls around the axis X2. By causing the refrigerant gas to flow along the inner peripheral surface of the oil separation space So, a swirling flow Fs in which the refrigerant gas swirls around the axis X2 is obtained.

The values of the first inner diameter Di1 and the second outer diameter Do2 described above are desirably determined so that the value of Do2 / Di1 is 0.8 or more and 0.9 or less. By setting the value of Do2 / Di1 to 0.8 or more, the gap between the outer peripheral surface of the large diameter portion 32 and the inner peripheral surface of the separation portion So1 is narrowed, and the refrigerant gas is separated from the separation portion So1 to the oil storage portion So2. A large amount of swirling flow can be suppressed. In addition, by setting the value of Do2 / Di1 to 0.9 or less, a gap between the outer peripheral surface of the large diameter portion 32 and the inner peripheral surface of the separation portion So1 is secured at least a certain amount. It is possible to promote the inflow of oil separated from the refrigerant gas.

The operation and effects of the scroll compressor 1 of the present embodiment described above will be described.
According to the scroll compressor 1 of the present embodiment, the refrigerant gas compressed by the compression mechanism 13 flows into the separation portion So1, and the space between the outer peripheral surface of the separation cylinder 30 and the inner peripheral surface of the separation portion So1 is It turns around an axis X2 along the vertical direction. The oil contained in the refrigerant gas is separated from the refrigerant gas by centrifugal force during swirling, adheres to the inner peripheral surface of the separation portion So1, and is guided along the inner peripheral surface to the inner peripheral surface of the lower oil storage portion So2. The oil guided to the inner circumferential surface of the oil storage portion So2 moves downward by gravity, and forms an oil reservoir Os below the oil storage portion So2.

The refrigerant gas from which the oil is separated in the separation part So1 is introduced from the inlet 33 formed in the small diameter part 31 of the separation cylinder 30 to the internal space Si of the separation cylinder 30, and is further introduced to the discharge piping 40. Below the small diameter portion 31 of the separation cylinder 30, a large diameter portion 32 having an outer diameter larger than that of the small diameter portion 31 is formed. Therefore, when the refrigerant gas swirling in the separation portion So1 reaches the lower end of the small diameter portion 31, the distance between the inner peripheral surface of the separation portion So1 and the outer peripheral surface of the large diameter portion 32 is small. It is suppressed that it is led to the lower oil storage part So2. Therefore, it is suppressed from rolling up oil accumulation Os below the oil storage part So2.

Thus, according to the scroll compressor 1 of the present embodiment, the oil is separated from the refrigerant gas in the separation part So1 above the oil separation space So, and the oil reservoir Os is formed in the oil storage part So2 below the separation part So1. can do. Since it is not necessary to separately provide a space for oil separation and a space for oil accumulation, it is possible to suppress an increase in size of the device and an increase in manufacturing cost.
In addition, since a large amount of the swirling flow Fs of the refrigerant gas is introduced from the separation unit So1 to the oil storage unit So2 to prevent the oil reservoir from being wound up, oil can be reliably separated from the refrigerant gas.

In the scroll compressor 1 of the present embodiment, the large diameter portion 32 is formed in a tapered shape in which the outer diameter gradually increases from the first outer diameter Do1 to the second outer diameter Do2 from the upper side to the lower side in the vertical direction. There is.
By doing this, it is possible to appropriately prevent the refrigerant gas from being guided to the oil storage portion So2 while circulating the swirling flow of the refrigerant gas led to the large diameter portion 32 without disturbing it.
The shape of the large diameter portion 32 does not have to be a tapered shape, and may be formed, for example, in a cylindrical shape having a constant second outer diameter Do2 along the vertical direction.

In the scroll compressor 1 of the present embodiment, the refrigerant gas compressed by the compression mechanism 13 flows in from above the small diameter portion 31, and the inlet 33 is formed at the lower end of the small diameter portion 31 in the vertical direction.
In this manner, the swirling flow Fs of the refrigerant gas can be formed in a wide range from the upper side to the lower side of the separation portion So1, and oil can be appropriately separated from the refrigerant gas.

In the present embodiment, a scroll compression mechanism is used as the compression mechanism 13, but another compression mechanism may be used.

In the present embodiment, the axis X2 extends in the vertical direction, and the oil separation space So and the separation cylinder 30 are disposed along the axis X2, but other modes may be employed.
For example, the axis X2 may be an axis extending in a direction inclined by a predetermined angle (for example, an angle of 13 ° or more) from the horizontal direction. In this case, the separation cylinder 30 is disposed along the axis X2 above the direction of gravity of the oil separation space So. Further, the large diameter portion 32 of the separation cylinder 30 is formed below the small diameter portion 31 in the gravity direction. Even if the axis X2 does not extend in the vertical direction, the oil contained in the refrigerant gas forms an oil reservoir Os below the oil storage portion So2 as long as it extends in a direction inclined from the horizontal direction. That is, the oil contained in the refrigerant gas is separated from the refrigerant gas by the centrifugal force during swirling, adheres to the inner peripheral surface of the separation portion So1, and is transmitted to the inner peripheral surface of the lower oil storage portion So2 along the inner peripheral surface. He moves below the oil reservoir So2 by gravity.

DESCRIPTION OF SYMBOLS 1 scroll compressor 2 housing 3 front housing 4 rear housing 5 crankshaft 6 main bearing 7 electromagnetic clutch 8 pulley 9 crank pin 10 drive bush 11 drive bearing 12 balance weight 13 compression mechanism 14 fixed scroll 15 orbiting scroll 16 suction volume 17 discharge port 18 Retainer 19 Discharge reed valve 20 Suction port 21 Fastening hole 22 Inlet 30 Separate cylinder (cylindrical member)
31 small diameter portion 32 large diameter portion 33 inlet 34 flange portion 40 discharge piping Di1 first inner diameter Do1 first outer diameter Do2 second outer diameter Os oil reservoir Sd discharge space Si internal space So oil separation space So1 separation portion (first space Department)
So2 oil reservoir (2nd space)
Ss Inhalation space X1, X2 axis

Claims

A housing that forms a suction space for the refrigerant gas inside;
A compression mechanism disposed in the housing for compressing the refrigerant gas flowing into the suction space;
An oil separation space formed in the housing so as to extend in the direction of gravity and separating oil from the refrigerant gas compressed by the compression mechanism and guiding the oil to a discharge pipe;
And a cylindrical member disposed along the axis of the oil separation space above the oil separation space in the direction of gravity.
The cylindrical member is
A small diameter portion having a first outer diameter,
A large diameter portion formed below the small diameter portion in the direction of gravity and having a second outer diameter larger than the first outer diameter;
And an inlet formed in the small diameter portion for guiding the refrigerant gas to the internal space of the cylindrical member,
The oil separation space is
A first space portion disposed with the small diameter portion and the large diameter portion and having a first inner diameter larger than the second outer diameter;
And a second space disposed below the first space in the direction of gravity,
The compressor in which the refrigerant gas compressed by the compression mechanism flows into the first space portion.
2. The compressor according to claim 1, wherein the large diameter portion is formed in a tapered shape in which the outer diameter gradually increases from the first outer diameter to the second outer diameter from the upper side to the lower side in the gravity direction.
The refrigerant gas compressed by the compression mechanism flows in from above the small diameter portion,
The compressor according to claim 1, wherein the introduction port is formed at a lower end of the small diameter portion in the gravity direction.
The compression mechanism is a mechanism in which a pair of fixed scrolls and orbiting scrolls are disposed to face each other, and the refrigerant gas is compressed by driving the orbiting scrolls to revolve with respect to the stationary scrolls. The compressor as described in any one of 3.