JP2009221960A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor at low cost by eliminating a separating pipe provided in a conventional centrifugal separation type oil separation chamber. <P>SOLUTION: This compressor includes a compression mechanism for compressing airflow including a lubricant and a separation chamber 51, into which the airflow compressed by the compression mechanism is led and turned and in which at least one part of the lubricant included in the airflow is separated by centrifugal force generated by the turn of the airflow. The separation chamber 51 dose not have a separating pipe inside thereof, and the manufacturing cost of the compressor in manufacture and assembling of the separating pipe can be reduced, and since a necessity of providing a space for the separating pipe inside the separation chamber is eliminated, the separation chamber can be miniaturized. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a compressor that compresses a fluid, and particularly to a compressor that is used in an air conditioner for automobiles.

  In such a compressor, a 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 has been well known that the system efficiency (thermal efficiency) decreases as the amount of lubricating oil discharged together with the fluid increases in the cycle.

  For this reason, in order to improve the system efficiency, the lubricating oil contained therein is separated as much as possible from the fluid compressed by the compression mechanism, 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 the compression mechanism is known (for example, page 4 of Patent Document 1). FIG. 1, FIG. 3, FIG. 4 and the third page of Patent Document 2, FIG. 1, FIG. 2).

In such a compressor, high-pressure refrigerant gas compressed by a compression mechanism and containing lubricating oil is guided to a centrifugal separation chamber, swirls in a substantially cylindrical separation chamber, and mist contained in the refrigerant gas by centrifugal force due to swirling. The lubricating oil is separated from the refrigerant gas by contacting the separation chamber wall.
JP 11-82352 A JP 2001-295767 A

  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 a tube called a separation tube is arranged in the separation chamber. The refrigerant gas introduced into the chamber is configured to swirl in an annular cylindrical space formed between the outer peripheral surface of the separation tube and the outer peripheral surface of the separation chamber. As described above, the separation pipe is generally considered as an essential component in the centrifugal separation method of the lubricating oil. That is, in order to obtain a high separation efficiency of the lubricating oil, it is necessary to swirl the refrigerant gas in the separation chamber. To that end, it is necessary to provide a separation pipe in the separation chamber and swirl the refrigerant gas around this. It is considered.

  However, as described in Patent Documents 1 and 2, when the separation tube is provided in the separation chamber, not only does the separation chamber increase in size, but also the number of parts, the production cost of the separation tube, and the assembly of the separation tube are increased. It was necessary to allow for man-hours and the like, which was an obstacle to reducing the manufacturing cost of the compressor.

  SUMMARY OF THE INVENTION In view of the above problems, an object of the present invention is to provide a compressor that has a high separation efficiency of lubricating oil and that can reduce the size of the separation chamber and reduce the manufacturing cost.

  In order to achieve the above-described object, a compressor according to the present invention includes a compression mechanism that compresses a gas-fluid containing lubricating oil, and a gas fluid compressed by the compression mechanism and a swirl. And a separation chamber in which at least a part of the lubricating oil contained in the gas fluid is separated, wherein the separation chamber does not have a separation pipe therein. That is, the separation tube is not arranged in the separation chamber, and is in a troublesome manner.

  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 the compressor according to the present invention, since the separation pipe of the centrifugal oil separation chamber can be eliminated, it is possible to reduce the manufacturing cost of the compressor associated with the production and assembly of the separation pipe. In addition, since the separation tube is no longer necessary, it is possible to reduce the size of the separation chamber, because it is no longer necessary to provide a space for installing the separation tube in the separation chamber, whether or not the separation chamber is actually downsized. Become.

  A compressor according to a first aspect of the present invention includes a compression mechanism that compresses a gas-fluid containing lubricating oil, and the gas fluid compressed by the compression mechanism is introduced and swirled. And a separation chamber in which at least a part of the lubricating oil is separated, the separation chamber having no separation pipe therein, and the separation chamber includes It is characterized in that nothing exists other than the introduced fluid. That is, the separation pipe is not arranged in the separation chamber, and it is troublesome.

  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 the compressor according to the second invention, the opening of the introduction hole for introducing the gas fluid into the separation chamber from the center axis of the columnar space of the separation chamber in which the introduced gas fluid swirls is parallel to the center axis of the introduction hole. The value of the ratio L / R between the shortest distance L to the projection line projected onto the column line and the distance R from the central axis of the columnar space to the inner peripheral wall of the columnar space is the relationship between the ratio L / R and the oil circulation rate. In the case where the separation tube is present and the case where there is no separation tube, the ratio L / R is changed and the graph is made to be equal to or greater than the ratio corresponding to the intersection of the curve with and without the separation tube. Yes.

  That is, the separation efficiency of the lubricating oil varies depending on the degree of eccentricity of the introduction hole for introducing the compressed air fluid into the separation chamber from the central axis of the separation chamber, and the eccentricity of the introduction hole is different depending on whether the separation pipe is present or not. In view of the fact that the graph curve showing the relationship between the degree and the oil circulation rate during the cycle intersects, the degree of eccentricity of the introduction hole that can obtain a lower oil circulation rate (high oil separation efficiency) when there is no separation pipe; It is characterized by doing.

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

  In the compressor according to the third invention, the separation chamber side opening of the gas discharge hole for discharging the gas fluid from the separation chamber is coupled to the outer peripheral portion on one end side of the columnar space portion of the separation chamber via the reduced diameter portion. It is characterized by having.

  By having such a feature, it is possible to prevent the high-density and high-speed gas-fluid introduced into the separation chamber containing a large amount of lubricating oil mist from being exhausted from the separation chamber without swirling in the separation chamber. Is done.

  The compressor according to the fourth invention is characterized in that the gas fluid introduced from the introduction hole into the separation chamber is introduced into the separation chamber in a direction away from the opening of the gas discharge hole.

By having 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 opening of the gas discharge hole and swirls around the separation chamber. The exhaust from the separation chamber is suppressed.

  The compressor according to the fifth invention is characterized in that an elongate passage portion formed continuously to 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 said.

  By having such characteristics, 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 turbulence and diffusion of the gas-fluid flowing into the separation chamber Thus, 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 the rotation of the refrigerant gas in the separation chamber.

  In the compressor according to the sixth aspect of the invention, a communication path is provided between the upper part of the oil storage chamber in which the lubricating oil separated in the separation chamber is stored and the separation chamber, and the opening on the separation chamber side of the communication path is provided. From here, the fluid flowing into the separation chamber is opened in a direction that does not hinder the swirling of the gas fluid in the separation chamber.

  By having such a feature, in the compressor according to the present invention, it is possible to prevent the gas fluid flowing in the separation chamber from being hindered by the fluid flowing from the oil storage chamber through the communication path.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, this invention is not limited by this embodiment.

(Embodiment 1)
1 is a longitudinal sectional view of a compressor to which a part of the present invention is applied, FIG. 2 is a sectional view taken along the line AA of FIG. 1 (sectional view of the working chamber), and FIG. 3 is a sectional view taken along the line BB of FIG. FIG. 4 is a cross-sectional view taken along the line CC in the vicinity of the separation chamber of the compressor shown in FIG.

  The compressor shown in the figure is a so-called vane rotary type compressor, and as shown in the drawing, a substantially columnar rotor 2 is arranged in a cylinder 1 having a cylindrical inner wall. The rotor 2 is disposed at a position where a part of the outer periphery forms a minute gap with the inner wall of the cylinder 1. The rotor 2 is provided with a plurality of vane slots 3, and vanes 4 are slidably inserted into the vane slots 3. The rotor 2 is formed integrally with a drive shaft 5 that is rotatably supported. 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. Is formed.

  A suction hole 9 and a discharge hole 10 communicate with the working chamber 8, and a gas fluid such as refrigerant gas is sucked into the working chamber 8 from the suction hole 9 and compressed, and then discharged from the discharge hole 10. A discharge valve 11 made of, for example, a reed valve is disposed at the outlet of the discharge hole 10. A high pressure case 12 is attached to the rear side of the rear side plate 7, and the high pressure case 12 is provided with a separation chamber 51 for separating and collecting mist-like lubricating oil contained in the refrigerant gas compressed in the working chamber 8. It has been.

The gas fluid compressed in the working chamber 8 and discharged from the discharge hole 10 is guided by the guide passage 13 provided continuously in the cylinder 1, the rear side plate 7 and the high pressure case 12, and formed on the side wall of the separation chamber 51. It is introduced into the separation chamber 51 through the 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 opens in the upper portion of the separation chamber 51, and the lubrication separated and collected from the refrigerant gas in the separation chamber 51 is formed in the lower portion of the separation chamber 51. An oil drain hole 54 through which 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, eventually returns to the suction hole 9 described above, is compressed again, and circulates in the cycle. The oil drain hole 54 opened at 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 stored in the oil storage chamber 52 through the oil drain hole 54.

  The lubricating oil stored in the oil storage chamber 52 is supplied to the rotor 2, the vane 4, the inner wall of the cylinder 1, and the like constituting the compression mechanism via the oil supply passage 18, lubricates each part, and is supplied to the vane back pressure chamber 17. The pressure acts to urge the vane 4 to the outside of the rotor 2.

  Lubricating oil is supplied through an oil supply passage 18 for supplying the lubricating oil from the oil storage chamber 52 to the compression mechanism. The lubricating oil stored in the oil storage chamber via the vane back pressure adjusting device 16 is supplied to the oil supply passage 18. Supplied. The vane back pressure adjusting device 16 controls the oil supply pressure and the amount of oil supplied to the compression mechanism according to the refrigerant gas pressure around the compression mechanism.

  Hereinafter, the operation of the compressor according to the above-described embodiment will be described.

  When power is transmitted from a drive source such as an in-vehicle engine and the drive shaft 5 and the rotor 2 rotate clockwise in FIG. 2, a low-pressure refrigerant gas flows into the working chamber 8 from the suction port 9 accordingly. The high-pressure refrigerant gas compressed along 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 separation chamber 51 through the introduction hole 53, and the lubricating oil contained in the refrigerant gas is separated and collected in the separation chamber.

  By the way, the separation chamber 51 is a so-called centrifugal oil separator, and is composed of a cylindrical space portion and an inverted conical space portion coupled to each other as shown in FIG. A conventional separation pipe or the like is not provided in the separation chamber, and the separation chamber is troublesome. There is nothing inside except for the introduced refrigerant gas (including the contained lubricating oil). Further, the separation chamber has a smooth surface on which no protrusions, protrusions, or irregularities are formed so as to hinder 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. Therefore, the refrigerant gas introduced into the separation chamber 51 swirls in the circumferential direction in the separation chamber, and the lubricating oil having a large specific gravity comes into contact with the separation chamber wall and is separated from the refrigerant gas by the centrifugal force caused by the swirling.

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

  Note that a communication passage 57 is provided between the upper portion of the oil storage chamber 52 and the separation chamber 51 to communicate these with each other. Similarly to the introduction hole 53, the communication passage 57 is provided eccentrically from the central axis of the separation chamber 51, and guides the fluid introduced into the separation chamber via the communication passage 57 in the tangential direction of the cylindrical space portion. That is, it is provided so that the fluid can be introduced into the separation chamber 51 along the inner peripheral surface 49 of the cylindrical space portion. By doing in this way, the fluid which flows in into the separation chamber 51 through the communication path 57 from the oil storage chamber 52 can smoothly join the swirling of the refrigerant gas in the separating chamber, and can prevent the swirling of the refrigerant gas from being hindered. Even if the lubricating oil in the oil storage chamber 52 reaches the communication passage 57 due to some reason, the lubricating oil is introduced into the separation chamber 51 through the communication passage 57, but the direction of the inflow into the separation chamber 51 is different. As described above, since the direction is to join the swirling flow in the separation chamber, even if the lubricating oil is introduced into the separation chamber via the communication path 57, the rotation of the refrigerant gas in the separation chamber is not hindered.

In the case of the compressor being described, the oil storage chamber side opening of the oil discharge hole 54 opens downward in the vertical direction from the oil level of the oil storage chamber 52. For this reason, the high-pressure refrigerant gas pressure discharged by the compression mechanism acts to push down the lubricating oil level in the oil storage chamber 52 while pushing down the lubricating oil level collected in the lower part of the separation chamber 51. However, it is conceivable that when the lubricating oil in the oil storage chamber 52 is pushed up, the gas fluid (mainly refrigerant gas) accumulated in the upper portion of the oil storage chamber 52 prevents the lubricating oil surface in the oil storage chamber 52 from being pushed up.

  Therefore, in this embodiment being described, a communication passage 57 that allows fluid movement between the oil storage chamber 52 and the separation chamber 51 is provided. Since the communication passage 57 functions as a vent hole for gas fluid such as refrigerant gas accumulated in the upper portion of the oil storage chamber 52, the lubricating oil surface in the oil storage chamber 52 is pushed up smoothly.

  It is sufficient that the communication path 57 is provided so that the fluid flowing from the oil storage chamber 52 into the separation chamber 51 does not hinder the rotation of the refrigerant gas in the separation chamber. In other words, it is considered that the swirling flow is not hindered unless the inflow direction of the fluid flowing from the oil storage chamber into the separation chamber has a direction component that collides frontally with the swirling flow near the outlet of the communication path. Therefore, the communication path may be provided along a direction perpendicular to the central axis of the separation chamber.

  In this embodiment, the oil storage chamber 52 side opening of the oil discharge hole 54 opens downward in the vertical direction from the oil level of the oil storage chamber, but may open above the oil level. In this case, the effect of pushing up the oil level 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 part of the separation chamber 51 is also prevented from being scattered into the separation chamber by blowing back.

  By the way, the compressor according to the present invention is characterized by having a so-called centrifugal separation chamber and no separation tube in the separation chamber. The following technical matters can be considered as factors that could eliminate the separation tube.

  One such technical matter is the relative positional relationship between the separation chamber 51 and the introduction hole 53 for introducing the compressed refrigerant gas into the separation chamber 51. The relative positional relationship here means the degree of eccentricity of the introduction hole 53 from the central axis of the separation chamber. The degree of eccentricity will be described in some detail.

  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 opening of the introduction hole 53 from the central axis M is tangential to the columnar space (the central axis of the introduction hole). If the shortest distance to the projection line projected in the direction parallel to the direction L is L, the ratio L / R of R and L represents the degree of eccentricity. 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. Comparing the relationship between the degree of eccentricity and the oil circulation rate between the case where the separation chamber is provided and the case where the separation tube is not provided, qualitatively as shown in FIG. That is, as shown in FIG. 5, if the degree of eccentricity is small, the oil circulation rate is smaller with the separation pipe (the oil separation efficiency is higher), and the difference in oil circulation rate decreases as the degree of eccentricity increases. Both curves (curves with and without separating pipes) intersect when a certain degree of eccentricity is reached, and the oil circulation rate of each curve is reversed. Therefore, in order to eliminate the separation pipe and provide a highly efficient refrigeration / air-conditioning system, it is desirable that the degree of eccentricity is equal to or greater than the degree of eccentricity corresponding to the intersection of both curves shown in FIG. The inventor presumes that the desired specific degree of eccentricity L / R is 0.4 or more.

Here, the oil circulation rate mentioned above is the mass of lubricating oil in the mixed liquid with respect to the mixed liquid mass of liquid refrigerant and lubricating oil circulating in the cycle, as defined in Japanese Industrial Standards (JIS B8606). expressed. In FIG. 5, OCR is abbreviated as a percentage value. The graph curve shown in FIG. 5 is based on the estimation based on the experience of the inventors so far, and the shape of the graph curve is considered to change due to 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 confident that the curve with and without the separation tube intersects.

  It is also possible to use the distance from the center axis M of the separation chamber to the cross-sectional center of gravity axis of the introduction hole as L. In this case, although the degree of eccentricity is 0.7 or more, depending on the shape of the introduction hole. For example, the present inventor presumes that a high efficiency refrigeration / air-conditioning system with a low oil circulation rate can be provided without a separation pipe.

  In addition to the technical items described above, the following technical items can also be cited as factors that have eliminated the separation tube. It is a way of opening the gas discharge hole 58 for discharging the refrigerant gas after oil separation from the separation chamber 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 cylindrical space portion of the separation chamber, and the cross-sectional area of the gas discharge hole opening is the cross-sectional area of the cylindrical space portion. It is formed smaller. The gas discharge hole opening does not extend to the outer peripheral portion of the cylindrical space portion, and a reduced diameter portion 56 that reduces the inner diameter of the cylindrical space portion to the inner diameter of the gas discharge hole opening is formed on the upper end surface of the cylindrical space portion. Will be. That is, the opening part of the gas discharge hole 58 is coupled to the outer periphery on the upper end side of the cylindrical space part through the reduced diameter part 56. Thereby, it is possible to suppress the high-density and high-speed refrigerant gas that contains a large amount of lubricating oil mist and is introduced into the separation chamber from being exhausted from the separation chamber without swirling around the separation chamber 51.

  That is, if it is assumed 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) It is considered that the gas swirls along the inner wall, gradually moves to the center of the swirl as it is pushed away by the high-density refrigerant gas as the separation of the lubricating oil proceeds, and is finally exhausted from the gas discharge hole. Actually, the refrigerant gas immediately after flowing into the separation chamber has the fastest flow velocity, and it is thought that the flow velocity gradually decreases during turning, and the centrifugal force acting on the refrigerant gas also decreases as the flow velocity decreases. A high-density, high-speed refrigerant gas containing lubricating oil mist swirls around the outer periphery 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 refrigerant gas whose density and speed have decreased It is considered that the gas moves to the center of the turn and is exhausted from the gas exhaust hole. As a result, it is possible to prevent the high-density and high-speed refrigerant gas that is introduced into the separation chamber containing a large amount of lubricating oil mist from being exhausted from the separation chamber without swirling the separation chamber.

  In the embodiment shown in FIGS. 1 and 4, the reduced diameter portion 56 is formed as an upper end surface perpendicular to the central axis of the cylindrical space portion. However, the present invention is not limited to this, and the reduced diameter portion May be formed as an inclined surface inclined obliquely 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. Furthermore, if the reduced diameter portion exists over the entire circumference of the gas discharge hole opening, the center axis of the gas discharge hole and the center of the separation chamber may be eccentric.

  In addition to the technical items described above, the following technical items can also be cited as factors that have eliminated 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 51 in the direction away from the opening of the gas discharge hole 58. Is to be done. By doing so, the refrigerant gas immediately after introduction introduced into the separation chamber 51 containing at least a large amount of lubricating oil mist can be kept away from the opening of the gas discharge hole, and the refrigerant containing a large amount of lubricating oil mist just after introduction. The supply of gas from the gas discharge hole 58 to the refrigeration / air conditioning system can be suppressed. Note that if the inclination angle α of the elongated passage portion 21 with respect to the central axis of the separation chamber is too small, the flow rate of the refrigerant gas introduced into the separation chamber cannot be used for swirling in the separation chamber, and it is considered that the oil separation efficiency decreases. In order to obtain high oil separation efficiency, the inclination angle α is preferably 60 ° ≦ α ≦ 90 °.

  Note that if the inner peripheral wall of the columnar space is formed so that the inner periphery of the cylindrical space expands away from the gas discharge hole, the high-density and high-speed refrigerant gas introduced into the separation chamber has a centrifugal force. As a result, the refrigerant gas is guided to the most expanded inner peripheral portion, so that the refrigerant gas introduced into the separation chamber containing a large amount of lubricating oil mist is discharged without the elongate passage portion 21 being inclined with respect to the central axis of the separation chamber. It can be kept away from the hole opening, which is considered preferable.

  In addition to the above-described technical items, the following technical items can be cited as factors that could eliminate the separation tube. That is, an elongated passage portion 21 (see FIGS. 1, 6, and 7) formed continuously to the introduction hole 53 is provided in a guide passage for guiding the refrigerant gas from the discharge port of the compression mechanism to the introduction hole 53 to the separation chamber. Is to provide. By doing so, these elongate passage portions have an action of accelerating and rectifying the refrigerant gas introduced into the separation chamber 51 while giving a turning force to the introduction hole 53, so that the refrigerant flows into the separation chamber. In addition to suppressing disturbance and diffusion of the gas-fluid flow, 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 the rotation of the refrigerant gas in the separation chamber.

  In the above description, a plurality of technical matters that are considered to be factors that can eliminate the separation pipe have been individually described. However, it is also possible to combine a plurality of technical matters with each other. Can expect a synergistic effect of each technical matter. In addition, the individual technical matters described in the specification of the present application can be combined with any other technical matters.

  In the above-described embodiment, the columnar space portion is described as an example of the columnar space portion of the separation chamber. However, any cross-sectional columnar shape may be used as long as it does not prevent the introduced refrigerant gas from turning. For example, the space may be an elliptical cross section or a quadrilateral with rounded corners.

  In the above-described embodiment, a sliding vane type rotary compressor has been described as an example of the compressor. However, the present invention is not limited to this, and other compressors such as a rolling piston type and a scroll type are also described. Applicable.

  As described above, the compressor according to the present invention is suitable for a small compressor and the like because the separation efficiency of the lubricating oil by the separator is high and the separation chamber can be downsized and the manufacturing cost can be reduced. .

The longitudinal cross-sectional view of the compressor in Embodiment 1 of this invention AA sectional view (working chamber sectional view) of the compressor shown in FIG. BB sectional view of the compressor shown in FIG. 1 (view of the high pressure case seen from the working chamber side) CC sectional view near the separation chamber of the compressor shown in FIG. The figure which showed the graph showing the degree of eccentricity L / R of the introduction hole with respect to a separation chamber, and the relationship between the oil circulation rate OCR 1 is a longitudinal sectional view showing a modification of the high-pressure case according to Embodiment 1 shown in FIG. FIG. 1 is a cross-sectional view of the vicinity of the separation chamber showing a modification of the elongated passage portion of the first embodiment shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Shilling 2 Rotor 3 Vane slot 4 Vane 5 Drive shaft 6 Front side plate 7 Rear side plate 8 Actuation chamber 9 Suction port 10 Discharge hole 11 Discharge valve 12 High pressure case 13 Guide passage 14 High pressure chamber 16 Vane backrest grant device 17 Vane Back chamber 18 Oil supply passage 21 Elongated passage portion 51 Separation chamber 52 Oil storage chamber 53 Introduction hole 54 Oil drain hole 56 Reduced diameter portion 57 Communication passage 58 Gas exhaust hole

Claims (6)

A compression mechanism that compresses the gas-fluid containing the lubricating oil, and the gas fluid compressed by the compression mechanism is introduced and swirled, and at least a part of the lubricant contained in the gas-fluid is separated by the centrifugal force generated by the swirling. A compressor having a separation chamber, wherein the separation chamber does not have a separation pipe therein. 2. The compressor according to claim 1, wherein the separation chamber has a columnar space portion in which the introduced gas fluid is swirled, and has an introduction hole for introducing the gas fluid compressed by the compression mechanism into the separation chamber. And the shortest distance L from the central axis of the columnar space portion to a projection line obtained by projecting the opening of the introduction hole parallel to the central axis of the introduction hole, and the central axis of the columnar space portion to the inner peripheral wall of the columnar space portion The value of the ratio L / R with respect to the distance R in the graph was obtained by examining the relationship between the ratio L / R and the oil circulation rate by changing the ratio L / R with and without the separation pipe. A compressor having a ratio equal to or more than a ratio corresponding to an intersection of a curve with a separation pipe and a curve without a separation pipe. 2. The compressor according to claim 1, wherein the separation chamber has a columnar space portion in which the introduced gas fluid swirls and a gas discharge hole through which the introduced gas fluid is exhausted. The separation chamber side opening is coupled to the outer peripheral portion on one end side of the columnar space via a reduced diameter portion. 2. The compressor according to claim 1, wherein the separator has an introduction hole for introducing the gas fluid compressed by the compression mechanism into the separation chamber, and the gas discharge hole through which the introduced gas fluid is exhausted in the separation chamber. The compressor is characterized in that the gas fluid introduced into the separation chamber through the introduction hole is introduced into the separation chamber in a direction away from the opening of the gas discharge hole. 2. The compressor according to claim 1, wherein a discharge port through which compressed gas fluid is discharged from the compression mechanism, an introduction hole through which the gas fluid discharged from the discharge port is introduced into the separation chamber, and the discharge port. And a guide passage for guiding a gas-fluid from an outlet to the introduction hole, and the guide passage has an elongated passage portion formed continuously to the introduction hole. 2. The compressor according to claim 1, wherein the compressor is provided between an oil storage chamber in which lubricating oil separated from a gas fluid in the separation chamber is stored, an upper portion of the oil storage chamber, and the separation chamber. The separation chamber side opening of the communication passage opens in a direction in which the fluid flowing from the upper part of the oil storage chamber into the separation chamber does not hinder the swirling of the air-fluid in the separation chamber. A compressor characterized by that.