JP2003336588A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor at a low cost by eliminating a separating pipe conventionally arranged in a centrifugal separation type oil separating chamber. <P>SOLUTION: The layout around the oil separating chamber is adjusted, and thereby the separating pipe is eliminated. Thus, only fluid introduced into the separating chamber exists in the separating chamber. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor for compressing a fluid, and more particularly to a compressor used in an air conditioner for automobiles.

[0002]

2. Description of the Related Art In such a compressor, part of the lubricating oil that lubricates the sliding portion of the compression mechanism is discharged from the compressor together with the compressed fluid and circulates in the refrigeration / air conditioning cycle. It is well known that the system efficiency (thermal efficiency) decreases as the amount of lubricating oil discharged together with a fluid is discharged during a cycle.

Under such circumstances, in order to improve the system efficiency, the lubricating oil contained therein is separated from the fluid compressed by the compression mechanism as much as possible, and then the fluid is discharged during the system cycle. As such an example, a compressor in which a centrifugal separation chamber for separating lubricating oil from a compressed fluid is provided on the discharge side of a compression mechanism is known (see, for example, Patent Documents 1 and 2).

In such a compressor, a high-pressure refrigerant gas compressed by a compression mechanism and containing lubricating oil is introduced into a centrifugal separation chamber, swirls in a substantially cylindrical separation chamber, and the centrifugal force generated by swirling produces a refrigerant gas. The contained mist-like lubricating oil is separated from the refrigerant gas by contacting the inner wall of the separation chamber.

[0005]

[Patent Document 1] Japanese Unexamined Patent Publication No. 11-82352 (4th
(Page, Figure 1, Figure 3, Figure 4)

[Patent Document 2] Japanese Unexamined Patent Publication No. 2001-295767 (page 3, FIG. 1, FIG. 2)

[0006]

By the way, the known compressor provided with the centrifugal separation chamber is not limited to the one disclosed in the above-mentioned patent document, and is referred to as a separation tube in the separation chamber. The refrigerant gas introduced into the separation chamber is configured to swirl in a cylindrical space having an annular cross section formed between the outer peripheral surface of the separation tube and the peripheral surface of the separation chamber.

As described above, the separation pipe is generally considered to be an essential component of the centrifugal separation type lubricating oil separation system.
That is, in order to obtain a high separation efficiency of the lubricating oil, it is necessary to reliably swirl the refrigerant gas in the separation chamber,
For that purpose, it is considered necessary to provide a separation tube in the separation chamber and swirl the refrigerant gas around this.

However, as described in Patent Documents 1 and 2, when the separation tube is provided in the separation chamber, not only does the size of the separation chamber increase, but also the number of parts increases and the separation tube manufacturing cost increases. It was necessary to consider the number of steps for assembling the separation pipe, which was an obstacle to reducing the manufacturing cost of the compressor.

In view of the above problems, it is an object of the present invention to provide a compressor which has a high efficiency of separating lubricating oil, and can reduce the size of the separation chamber to reduce the manufacturing cost.

[0010]

In order to achieve the above object, in the compressor according to the first invention of the present application, it is ensured that there is nothing in the separation chamber other than the fluid introduced therein. It has a feature. That is, the separation tube is not placed in the separation chamber, which is a nuisance.

With such a feature, in the compressor according to the present invention, it is not necessary to secure a space for arranging the separation pipe in the separation chamber.

In order to achieve the above-mentioned object, in the compressor according to the second invention of the present application, the gas fluid is introduced into the separation chamber from the central axis of the columnar space of the separation chamber in which the introduced gas fluid swirls. The ratio L / R of the shortest distance L to the projection line obtained by projecting the opening of the introducing hole to be parallel to the central axis of the introducing hole and the distance R from the central axis of the columnar space portion to the inner peripheral wall of the columnar space portion. The relationship between the ratio L / R and the oil circulation rate is investigated by changing the ratio L / R for the case with a separation pipe and the case without a separation pipe. It is characterized in that the value is equal to or greater than the ratio value corresponding to the intersection point of.

That is, the separation efficiency of the lubricating oil varies depending on the degree of eccentricity of the introduction hole for introducing the compressed gas fluid into the separation chamber from the center axis of the separation chamber, and it is introduced depending on whether the separation pipe is provided or not. Considering that the graph curves showing the relationship between the degree of eccentricity of the holes and the oil circulation rate during the cycle intersect,
The feature is that the eccentricity of the introduction hole is such that a lower oil circulation rate (higher oil separation efficiency) can be obtained without the separation pipe.

With such a feature, in the compressor according to the present invention, it is possible to maintain or enhance the low oil circulation rate (high oil separation efficiency) even if the separation pipe is abolished.

In order to achieve the above object, in the compressor according to the third aspect of the present invention, the separation chamber side opening of the gas discharge hole for discharging the gas fluid from the separation chamber is a columnar space of the separation chamber. It is characterized in that it is connected to the outer peripheral portion on one end side of the portion via a reduced diameter portion.

Due to such a feature, a high-density, high-velocity gas-fluid containing a large amount of lubricating oil mist and introduced into the separation chamber is exhausted from the separation chamber without swirling in the separation chamber. Is suppressed.

In order to achieve the above-mentioned object, in the compressor according to the fourth invention of the present application, the gas-fluid introduced into the separation chamber from the introduction hole is directed in the direction away from the gas discharge hole opening. It is characterized by being introduced into the separation chamber.

With such a feature, in the compressor according to the present invention, the gas-fluid containing a large amount of lubricating oil mist and introduced into the separation chamber is kept away from the gas discharge hole opening, and the separation chamber is crushed. Exhaust from the separation chamber without swirling is suppressed.

In order to achieve the above-mentioned object, in the compressor according to the fifth aspect of the present application, the introduction hole is provided in the guide passage for guiding the gas fluid from the discharge port of the compression mechanism to the introduction hole of the separation chamber. It is characterized in that an elongated passage portion formed so as to be continuous with is provided.

With such a feature, in the compressor according to the present invention, the elongated passage portion has a function of rectifying the refrigerant gas introduced into the separation chamber, so that the flow of the gas fluid flowing into the separation chamber is reduced. Disturbance and diffusion are suppressed, and not only the static pressure of the high-pressure refrigerant gas protruding from the compression mechanism but also the dynamic pressure can be utilized for swirling the refrigerant gas in the separation chamber.

In order to achieve the above-mentioned object, in the compressor according to the sixth aspect of the present application, the compressor is connected between the upper part of the oil storage chamber where the lubricating oil separated in the separation chamber is stored and the separation chamber. A passage is provided, and an opening of the communication passage on the side of the separation chamber is opened in a direction that does not hinder swirling of the gas-fluid in the separation chamber by the fluid flowing into the separation chamber from the passage.

With such a feature, in the compressor according to the present invention, the fluid flowing from the oil storage chamber through the communication passage is prevented from interfering with the swirling of the gas-fluid in the separation chamber.

[0023]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the invention according to the present application will be described below with reference to the drawings. 11 is a longitudinal sectional view of a compressor to which a part of the invention according to the present application is applied, FIG. 2 is a sectional view taken along the line AA of FIG. 11 (a sectional view of a working chamber), and FIG. 3 is a sectional view taken along the line B- of FIG. It is a B sectional view (the figure which looked at the high pressure case from the working chamber side).

The compressor shown in the figure is a so-called vane rotary type compressor, and as shown in the drawing, a substantially cylindrical rotor 2 is arranged in a cylinder 11 having a cylindrical inner wall.

A part of the outer circumference of the rotor 2 is a cylinder 11
It is placed at a position that forms a minute gap with the inner wall of the. The rotor 2 is provided with a plurality of vane slots 3, and vanes 4 are slidably inserted in the respective vane slots 3.

The rotor 2 is a drive shaft 5 which is rotatably supported.
It is formed integrally with. The cylinder 1 and the rotor 2 are sandwiched between the front side plate 6 and the rear side plate 7 in the rotational axis direction of the rotor 2, and both ends of the cylinder 1 are closed by these, and a working chamber 8 for fluid compression is formed in the cylinder.
Are formed.

A suction hole 9 and a discharge hole 10 are communicated with the working chamber 8. A gas fluid such as a refrigerant gas is sucked into the working chamber 8 from the suction hole 9 and compressed, and then discharged from the discharge hole 10. At the outlet of the discharge hole 10, the discharge valve 1 including, for example, a reed valve
1 is provided.

A high pressure case 12 is attached to the rear side of the rear side plate 7, and the high pressure case 12 separates and collects mist-like lubricating oil contained in the refrigerant gas compressed in the working chamber 8. 51 is provided.

The gas-fluid compressed in the working chamber 8 and discharged from the discharge hole 10 is guided by a guide passage 13 provided continuously to the cylinder 1, the rear side plate 7 and the high pressure case 12, and is guided to the side wall of the separation chamber 51. It is introduced into the separation chamber 51 through the formed introduction hole 53.

A gas discharge hole 58 for exhausting the refrigerant gas from which the lubricating oil has been separated in the separation chamber is opened at the upper part of the separation chamber 51, and a gas is separated and collected from the refrigerant gas in the lower part of the separation chamber 51 in the separation chamber. An oil discharge hole 54 through which the generated lubricating oil is discharged is opened.

The refrigerant gas discharged from the separation chamber 51 through the gas discharge hole 58 circulates in the refrigeration / air-conditioning cycle, and eventually returns to the suction hole 9 described above, is compressed again, and circulates in the cycle.

An oil drain hole 54 opened in the lower part of the separation chamber 51 communicates with an oil storage chamber 52 formed between the high pressure case 12 and the rear side plate 7. Therefore, the lubricating oil separated and collected from the refrigerant gas in the separation chamber is supplied to the oil storage chamber 5 through the oil drain hole 54.
It is stored in 2.

The lubricating oil stored in the oil storage chamber 52 passes through the oil supply passage 18 and the rotor 2, the vanes 4, which constitute the compression mechanism,
It is supplied to the inner wall of the cylinder 1 and the like to lubricate each part, and is also supplied to the vane back pressure chamber 17 to urge the vane 4 to the outside of the rotor 2 by its pressure.

The lubricating oil is supplied from the oil storage chamber 52 through the oil supply passage 18 for supplying the lubricating oil to the compression mechanism.
Lubricating oil stored in the oil storage chamber is supplied to 8 through a vane back pressure adjusting device 16. Vane back pressure adjusting device 16
Controls the supply pressure and amount of lubricating oil supplied to the compression mechanism in accordance with the refrigerant gas pressure around the compression mechanism.

The operation of the compressor according to the above embodiment will be described below.

When the drive shaft 5 and the rotor 2 rotate clockwise in FIG. 2 in response to power transmission from a drive source such as an in-vehicle engine, low-pressure refrigerant gas flows into the working chamber 8 through the suction port 9 accordingly. To do.

The high-pressure refrigerant gas compressed with the rotation of the rotor 2 pushes up the discharge valve 11 from the discharge hole 10 and flows into the guide passage 13. Further, the high-pressure refrigerant gas is introduced into the introduction hole 5
The lubricating oil contained in the refrigerant gas is separated and collected in the separation chamber 51 after being introduced into the separation chamber 51.

By the way, the separation chamber 51 is a so-called centrifugal separation type oil separator, and as shown in FIG. 1, it is composed of a cylindrical space portion and an inverted conical space portion which are connected to each other.

No conventional separation pipe is provided inside the separation chamber, and the separation chamber is messy, and there is nothing inside except the introduced refrigerant gas (including the lubricating oil contained therein). I haven't.

No ridges, projections or irregularities are formed in the separation chamber, which obstruct the swirling of the refrigerant gas introduced into the separation chamber. The introduction hole 53 is provided eccentrically from the central axis of the cylindrical space portion of the separation chamber 51 so as to guide the refrigerant gas introduced into the separation chamber in the tangential direction of the cylindrical space portion, that is, the refrigerant gas is introduced into the cylindrical space portion. It is provided so that it can be introduced into the separation chamber 51 along the inner peripheral surface 49 thereof.

Therefore, the refrigerant gas introduced into the separation chamber 51 swirls in the circumferential direction in the separation chamber, and the centrifugal force of the swirling causes the lubricating oil having a large specific gravity to come into contact with the inner wall of the separation chamber to be separated from the refrigerant gas. It

The separated lubricating oil moves downward along the inner peripheral surface 49 and is condensed in the central portion by the inverted conical space portion.

A communication passage 57 is provided between the upper part of the oil storage chamber 52 and the separation chamber 51 so as to communicate them with each other. The communication passage 57, like the introduction hole 53, has the separation chamber 5
1 is provided eccentrically from the central axis and guides the fluid introduced into the separation chamber via the communication passage 57 in the tangential direction of the columnar space portion, that is, the fluid is guided to the inner peripheral surface 4 of the columnar space portion.
9 is provided so that it can be introduced into the separation chamber 51.

By doing so, the fluid flowing from the oil storage chamber 52 through the communication passage 57 into the separation chamber 51 is
It is possible to smoothly join the swirl of the refrigerant gas in the separation chamber and prevent the swirl of the refrigerant gas from being disturbed.

Further, even if the lubricating oil in the oil storage chamber 52 reaches the communication passage 57 due to some factor, the lubricating oil is introduced into the separation chamber 51 through the communication passage 57.
As described above, since the direction of inflow to the separation chamber merges with the swirl flow in the separation chamber as described above, even if the lubricating oil is introduced into the separation chamber via the communication passage 57, it does not hinder the swirling of the refrigerant gas in the separation chamber. .

In the case of the compressor described, the oil storage chamber-side opening of the oil drain hole 54 opens vertically below the oil level of the oil storage chamber 52. Therefore, the high pressure refrigerant gas pressure discharged by the compression mechanism acts to push down the oil surface of the lubricating oil collected in the lower portion of the separation chamber 51, while pushing up the lubricating oil surface in the oil storage chamber 52.

However, when the lubricating oil in the oil storage chamber 52 is pushed up, the gas-fluid (mainly the refrigerant gas) accumulated in the upper part of the oil storage chamber 52 may hinder the pushing up of the lubricating oil surface in the oil storage chamber 52. .

Therefore, in this embodiment, which is described below, a communication passage 57 is provided between the upper part of the oil storage chamber 52 and the separation chamber 51 to allow fluid movement therebetween. Communication passage 5
Since 7 acts as a gas vent for gas fluid such as refrigerant gas accumulated in the upper part of the oil storage chamber 52, the lubricating oil surface in the oil storage chamber 52 can be pushed up smoothly.

It is sufficient that the communication passage 57 is provided so that the fluid flowing from the oil storage chamber 52 into the separation chamber 51 does not hinder the swirling of the refrigerant gas in the separation chamber. That is, if the inflow direction of the fluid flowing from the oil storage chamber to the separation chamber does not have a directional component that directly collides with the swirl flow near the outlet of the communication passage, it is considered that the swirl flow is not hindered. Therefore,
The communication passage may be provided along a direction intersecting with the central axis of the separation chamber at a right angle.

In this embodiment, the opening of the oil drain hole 54 on the oil storage chamber 52 side is opened vertically below the oil surface of the oil storage chamber, but it may be opened above the oil surface. .

In this case, the effect of pushing up the oil surface by the high pressure refrigerant gas cannot be expected, but since the communication passage 57 is provided, the blowback from the oil discharge hole 54 due to the pulsation of the refrigerant gas is suppressed. . Therefore, the oil collected in the lower portion of the separation chamber 51 is also prevented from scattering into the separation chamber due to blowback.

By the way, the compressor according to the invention of the present application is characterized in that it has a so-called centrifugal separation chamber but does not have a separation tube in the separation chamber. The following several technical matters can be considered as factors that could eliminate the separation tube.

One of such technical matters is the relative positional relationship between the introduction chamber for introducing the compressed refrigerant gas into the separation chamber and the separation chamber. The relative positional relationship here means the degree of eccentricity of the introduction hole from the central axis of the separation chamber. The degree of eccentricity will be described in some detail.

As shown in FIG. 4, the distance from the central axis M of the separation chamber 51 to the inner peripheral wall of the columnar space is R, and the central axis M
Let L be the shortest distance from the projection line to the projection line projecting the opening of the introduction hole 53 in the tangential direction of the columnar space (direction parallel to the central axis of the introduction hole), the ratio L / R of R and L is eccentric. It represents the degree.

Assuming that the size of L is 0 at the minimum and R at the maximum, the eccentricity L / R takes a value of 0 to 1, and the larger the value, the more eccentric the introduction hole is with respect to the separation chamber. Becomes Regarding the relationship between the degree of eccentricity and the oil circulation rate, comparing the case with and without the separation pipe in the separation chamber,
The inventor of the present application speculates that the result is qualitatively as shown in FIG.

That is, as shown in FIG. 5, when the degree of eccentricity is small, the oil circulation rate is smaller with the separation pipe (the oil separation efficiency is higher), and as the degree of eccentricity increases, the difference in the oil circulation rate varies. When decreasing and both curves (curve with separation pipe and curve without separation pipe) reach a certain eccentricity, they intersect and the oil circulation rate of each curve is reversed.

Therefore, in order to provide a highly efficient refrigeration / air-conditioning system by eliminating the separation pipe, it is desirable that the degree of eccentricity be equal to or greater than the degree of eccentricity corresponding to the intersection of the curves shown in FIG. The inventor of the present invention desires a specific degree of eccentricity L / R
Is estimated to be 0.4 or more.

Here, the above-mentioned oil circulation rate is as defined in Japanese Industrial Standards (JIS B8606),
It is represented by the mass of the lubricating oil in the mixed liquid with respect to the mass of the mixed liquid of the liquid refrigerant and the lubricating oil circulating in the cycle.

In FIG. 5, OCR is abbreviated and shown as a percentage value. The graph curve shown in FIG. 5 is based on assumptions made by the inventor's experience so far, and the shape of the graph curve is considered to change depending on the configuration of the compressor, the design around the separation chamber, and the like. Although not always consistent with what is shown, the inventor is convinced that curves with and without separation tubes intersect.

It is also possible to use the distance from the central axis M of the separation chamber to the center of gravity of the cross section of the introduction hole as L.
In this case, although the eccentricity is 0.7 or more, depending on the shape of the introduction hole, the present inventor can provide a highly efficient refrigeration / air-conditioning system with a low oil circulation rate without the separation pipe. Infer.

Further, as a factor of eliminating the separation tube, the following technical matters can be mentioned in addition to the above technical matters. That is how the gas discharge hole 58 for discharging the refrigerant gas after oil separation from the separation chamber is opened to the separation chamber 51.

In the embodiment shown in FIG. 1, the gas discharge hole opening is provided at the center of the upper end side of the columnar space of the separation chamber, and the cross sectional area of the gas discharge hole opening is equal to that of the columnar space. It is formed smaller than the cross-sectional area.

The gas discharge hole opening does not extend to the outer peripheral portion of the cylindrical space, and the inner diameter of the cylindrical space is reduced to the inner diameter of the gas discharge hole opening on the upper end surface of the cylindrical space. 56
Will be formed.

That is, the opening of the gas discharge hole 58 is connected to the outer circumference of the upper end side of the cylindrical space through the reduced diameter portion 56. As a result, the high-density, high-speed refrigerant gas containing a large amount of lubricating oil mist and introduced into the separation chamber is prevented from being exhausted from the separation chamber without swirling in the separation chamber 51.

That is, assuming that the flow velocity of the refrigerant gas introduced into the separation chamber does not decrease during swirling, the refrigerant gas containing a large amount of lubricating oil mist having a large specific gravity (high density) has a columnar outer peripheral portion of the swirling flow. It is thought that it swirls along the inner wall of the space and gradually moves to the center of swirling as it is pushed away by the high-density refrigerant gas as the separation of the lubricating oil progresses, and is eventually exhausted from the gas discharge holes. To be

In practice, it is considered that the flow velocity of the refrigerant gas immediately after flowing into the separation chamber is the highest, and the flow velocity gradually decreases during the swirling. As the flow velocity decreases, the centrifugal force acting on the coolant gas also decreases. Therefore, the high-density, high-speed refrigerant gas containing the lubricating oil mist swirls along the outer peripheral portion of the swirling flow along the inner wall of the cylindrical space of the separation chamber, and the separation of the lubricating oil progresses, and the density and speed decrease. It is considered that the refrigerant gas moves to the center of the swirl and is discharged from the gas discharge hole.

As a result, it is possible to prevent the high-density, high-speed refrigerant gas containing a large amount of lubricating oil mist and being introduced into the separation chamber from being exhausted from the separation chamber without swirling in the separation chamber.

In the embodiment shown in FIGS. 1 and 4, the reduced diameter portion 56 is formed as the upper end surface perpendicular to the central axis of the cylindrical space portion, but the invention is not limited to this.
The reduced diameter portion may be formed as an inclined surface that is obliquely inclined with respect to the central axis of the cylindrical space portion, or may be formed as a gentle curve continuous from the outer periphery of the cylindrical space portion. further,
The central axis of the gas discharge hole and the center of the separation chamber may be eccentric as long as the reduced diameter portion exists over the entire circumference of the opening of the gas discharge hole.

In addition to the above-mentioned technical matters, the following technical matters can be cited as a factor of eliminating the separation tube. As shown in FIG. 6, the refrigerant gas introduced into the separation chamber by adjusting the direction of the elongated passage portion 21 connected to the introduction hole is introduced into the separation chamber in the direction away from the gas discharge hole opening. To do so.

By doing so, it is possible to keep the refrigerant gas, which contains at least a large amount of lubricating oil mist, and is introduced into the separation chamber 51 immediately after the introduction from the gas discharge hole opening portion, and a large amount of the lubricating oil mist immediately after the introduction. It is possible to prevent the contained refrigerant gas from being supplied to the refrigeration / air conditioning system from the gas discharge hole.

If the inclination angle α of the elongated passage portion 21 with respect to the center axis of the separation chamber is too small, the flow velocity of the refrigerant gas introduced into the separation chamber cannot be used for swirling in the separation chamber, and the oil separation efficiency will be reduced. Therefore, in order to obtain high oil separation efficiency, it is desirable that the inclination angle α is 60 ° ≦ α ≦ 90 °.

If the inner peripheral wall of the columnar space portion is formed so that the inner periphery of the columnar space portion expands away from the gas discharge hole, the high-density and high-speed refrigerant gas introduced into the separation chamber Since it is guided to the most expanded inner peripheral portion by receiving the centrifugal force, the refrigerant gas that contains a large amount of lubricating oil mist and is introduced into the separation chamber even if the elongated passage portion 21 is not inclined with respect to the separation chamber central axis. Is considered preferable because it can be kept away from the opening of the gas discharge hole.

Further, in addition to the above-mentioned technical matters, the following technical matters can be cited as a factor of eliminating the separation tube. It is an elongated passage portion 13a (FIG. 7) formed in a guide passage that guides the refrigerant gas from the discharge port of the compression mechanism to the introduction hole to the separation chamber, which is continuous with the introduction hole 53.
21) (see FIG. 1).

By doing so, since these elongated passage portions have a function of rectifying the refrigerant gas introduced into the separation chamber 51, turbulence and diffusion of the flow of the gas fluid flowing into the separation chamber can be suppressed and Therefore, not only the static pressure of the high-pressure refrigerant gas discharged from the compression mechanism but also the dynamic pressure can be utilized for swirling the refrigerant gas in the separation chamber.

In the above description, a plurality of technical matters considered to be factors that can eliminate the separation tube have been individually described, but it is also possible to combine a plurality of technical matters with each other. In that case, a synergistic effect of each technical item can be expected. In addition, the individual technical matters described in the present specification can be combined with any other technical matters.

In the above-mentioned embodiment, the columnar space portion is used as an example of the columnar space portion of the separation chamber, but
The columnar space portion may have any cross-sectional shape as long as it does not hinder the swirling of the introduced refrigerant gas, and may have, for example, an elliptical cross section or a quadrangular shape with rounded corners.

Although the sliding vane type rotary compressor has been described as an example of the compressor in the above embodiment, the present invention is not limited to this, and other compressors such as a rolling piston type, a scroll type, etc. It is also applicable to.

[0078]

As described above, in the compressor of the present invention, the separation pipe of the centrifugal separation type oil separation chamber can be abolished, so that the manufacturing cost of the compressor accompanying the production and assembly of the separation pipe is reduced. It became possible to reduce.

Since the separation tube is no longer required, it is not necessary to provide a space for installing the separation tube in the separation chamber, regardless of whether or not the separation chamber is actually downsized. Will also be possible.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a compressor showing an embodiment to which a part of the invention according to the present application is applied.

2 is a cross-sectional view of the compressor shown in FIG. 1 taken along the line AA (cross-sectional view of the working chamber).

FIG. 3 is a cross-sectional view of the compressor shown in FIG. 1 taken along the line BB (a view of the high pressure case as seen from the working chamber side).

4 is a cross-sectional view taken along the line CC of the compressor shown in FIG. 1 near the separation chamber.

FIG. 5 is a graph showing the relationship between the eccentricity L / R of the introduction hole with respect to the separation chamber and the oil circulation rate OCR.

6 is a vertical cross-sectional view showing a modified example of the high-pressure case of the embodiment shown in FIG.

7 is a cross-sectional view of the vicinity of the separation chamber showing a modification of the elongated passage portion of the embodiment shown in FIG.

[Explanation of symbols]

1 shilling 2 b overnight 3 vane slots 4 vanes 5 drive shaft 6 Front side plate 7 Rear side plate 8 working chambers 9 Intake port 10 discharge holes 11 discharge valve 12 high pressure case 13 guidance passage 14 High pressure chamber 16 vane spine application device 17 vane back shojo 18 Oil supply passage 21 Elongated passage 51 separation room 52 oil storage room 53 introduction hole 54 Oil drain hole 56 Reduced diameter part 57 communication passage 58 gas exhaust hole

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F04C 29/02 351 F04C 29/02 351D (72) Inventor Takeshi Kawada 1006 Kadoma, Kadoma City, Osaka Matsushita Electric Sangyo Co., Ltd. (72) Inventor Kenji Okuzono 1006 Kadoma, Kadoma City, Osaka Prefecture Matsushita Electric Industrial Co., Ltd. (72) Nobuna Tsuchida 1006 Kadoma, Kadoma City, Osaka Matsushita Electric Industrial Co., Ltd. (Reference) 3H003 AA05 AC03 BG09 BH03 CD01 3H029 AA05 AA17 AB03 BB04 CC45 3H040 AA09 BB05 BB11 CC15 DD01 DD28 DD33 DD40

Claims (6)

[Claims] 1. A compression mechanism for compressing a gas-fluid containing a lubricating oil, and a gas-fluid compressed by the compression mechanism is introduced and swirled, and at least the lubricating oil contained in the gas-fluid is centrifugally generated by the swirling. A compressor provided with a separation chamber which is partly separated, wherein there is nothing other than the fluid introduced therein in the separation chamber. 2. The compressor according to claim 1, wherein the separation chamber has a columnar space portion in which the introduced gas fluid swirls, and the gas fluid compressed by the compression mechanism is introduced into the separation chamber. From the central axis of the columnar space portion to the projection line obtained by projecting the opening of the introduction hole parallel to the central axis line of the introduction hole, and from the central axis of the columnar space portion to the projection line. Ratio L to the distance R to the inner wall of the columnar space
The value of / R is the curve with the separation pipe when the relationship between the ratio L / R and the oil circulation rate is investigated and graphed by changing the ratio L / R with and without the separation pipe. A compressor characterized in that the ratio is equal to or greater than the value corresponding to the intersection of curves without separation tubes. 3. The compressor according to claim 1, wherein the separation chamber has a columnar space in which the introduced gas-fluid swirls, and a gas discharge hole through which the introduced gas-fluid is exhausted. The compressor is characterized in that the opening of the gas discharge hole on the side of the separation chamber is connected to the outer peripheral portion on one end side of the columnar space through a reduced diameter portion. 4. The compressor according to claim 1, further comprising an introduction hole for introducing the gas fluid compressed by the compression mechanism into the separation chamber, and the gas fluid introduced into the separation chamber is exhausted. The gas discharge hole is opened, and the gas-fluid introduced into the separation chamber from the introduction hole is introduced into the separation chamber in a direction away from the opening of the gas discharge hole. Compressor. 5. The compressor according to claim 1, wherein the gas fluid discharged from the compression mechanism is discharged, and the gas fluid discharged from the discharge port is introduced into the separation chamber. A compressor characterized by having a hole and a guide passage for guiding a gas fluid from the discharge port to the introduction hole, and the guide passage having an elongated passage portion formed so as to be continuous with the introduction hole. 6. The compressor according to claim 1, wherein the compressor is provided between an oil storage chamber in which the lubricating oil separated from the gas fluid in the separation chamber is stored, and between the upper part of the oil storage chamber and the separation chamber. And a communication passage that allows fluid movement between them, and the separation chamber-side opening of the communication passage allows a fluid flowing into the separation chamber from an upper portion of the oil storage chamber to swirl gas-fluid in the separation chamber. A compressor characterized by opening in an unobstructed direction.