JP2013227890A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize a gas compressor by reducing the size along the elongation direction of a rotary shaft of an oil separator.SOLUTION: A gas compressor comprises a body member 71 having a columnar space 71b, and a cylindrical inner cylinder member 72 disposed in the columnar space 71b substantially coaxially with the columnar space 71b, and a cyclone block 70 (oil separator) provided for a compressor body 60 having a rotary shaft 51 adjacent to the elongation direction C of the rotary shaft 51 to for centrifugal separation of the refrigerating machine oil R by having a refrigerant gas G (gas) with a refrigerating machine oil R (oil) mixed therein passing through while swirling in a cylindrical oil separating space 73 partitioned by the inner circumferential surface of the body member 71 and the outer circumferential surface of the inner cylindrical part 72a of the inner cylinder member 72. The cross-section of the columnar space 71b has a length D1 in the elongation direction C of the rotary shaft 51 that is shorter than the length D2 in the direction K orthogonal to the elongation direction C of the rotary shaft 51.

Description

  The present invention relates to a gas compressor, and more particularly to an improvement in an oil separator that centrifuges oil from compressed gas discharged from a compressor body.

  Conventionally, a gas compressor (compressor) for compressing a gas such as a refrigerant gas and circulating the gas in the air conditioning system is used in an air conditioning system (hereinafter referred to as an air conditioning system).

  Here, the compressor includes a compressor main body that compresses and discharges gas, and an oil separator that separates oil components such as refrigeration oil from the compressed refrigerant gas discharged from the compressor main body.

  As an oil separator, for example, a main body member having a substantially cylindrical space whose lower end surface is closed by an end wall in which a drainage passage is formed, and a main body that is substantially coaxial with the substantially cylindrical space of the main body member A substantially cylindrical space (oil separation space) defined by the inner peripheral surface of the main body member and the outer peripheral surface of the inner cylindrical member. Is known in which refrigeration oil is centrifuged by passing compressed refrigerant gas while swirling (Patent Document 1).

JP 2009-235999 A

  However, since the oil separator occupies a certain amount of space in the discharge chamber, it is necessary to form the discharge chamber in a size that can accommodate the oil separator. As a result, the size of the gas compressor itself also increases.

  This invention is made | formed in view of the said situation, Comprising: It aims at providing the gas compressor which can make the magnitude | size along the direction where the rotating shaft extended small.

  In the gas compressor according to the present invention, the cross-sectional shape of the space inside the body member of the oil separator is along the direction orthogonal to the direction in which the rotation axis extends in the length along the direction in which the rotation axis extends. By reducing the size of the oil separator along the direction in which the rotating shaft extends, and reducing the discharge chamber by that amount, The size of the entire compressor is reduced.

  That is, the gas compressor according to the present invention includes a main body member having a columnar space with a lower end face closed, and a substantially cylindrical inner cylinder that is substantially coaxial with the columnar space and disposed in the columnar space. And a gas mixed with oil is passed through the substantially cylindrical oil separation space partitioned by the inner peripheral surface of the main body member and the outer peripheral surface of the inner cylindrical member, An oil separator that centrifuges the oil from a gas and that is provided adjacent to a compressor body having a rotating shaft in a direction in which the rotating shaft extends, and the columnar space of the main body member includes the rotating shaft. The length of the rotating shaft along the direction in which the rotating shaft extends is shorter than the length along the direction orthogonal to the direction in which the shaft extends.

  With the gas compressor according to the present invention, the size along the direction in which the rotating shaft extends can be reduced.

It is a longitudinal section showing a vane rotary type compressor which is one embodiment of a gas compressor concerning the present invention. It is a figure which shows the cross section along the AA in FIG. It is sectional drawing equivalent to FIG. 2 which shows a modification, and the inner cylinder part shows the cyclone block which has a cross section of the outer periphery outline shape of an ellipse. It is sectional drawing equivalent to FIG. 2 which shows another modification, and the outer edge outline shape of columnar space shows the cyclone block which has a semi-cylindrical cross section, for example.

  Hereinafter, specific embodiments of a gas compressor according to the present invention will be described in detail with reference to the drawings.

  A vane rotary compressor 100 (hereinafter simply referred to as a compressor 100), which is an embodiment of a gas compressor according to the present invention, is an air having an evaporator, a gas compressor, a condenser, and an expansion valve installed in an automobile or the like. Used as a gas compressor in harmony systems. This air conditioning system constitutes a refrigeration cycle by circulating a refrigerant gas G (gas).

  The compressor 100 compresses the refrigerant gas G (gas, compressed gas) as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas G to the condenser of the air conditioning system. . The condenser heat-exchanges the compressed refrigerant gas G with ambient air and the like to dissipate heat from the refrigerant gas G and liquefy it, and sends it to the expansion valve as a high-pressure liquid refrigerant.

  The high-pressure liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange with the heat of vaporization.

  The vaporized low-pressure refrigerant gas G returns to the compressor 100 and is compressed, and thereafter repeatedly passes through the condenser, the expansion valve, the evaporator, and the compressor 100, and circulates in the air conditioning system.

  The compressor 100 houses a compressor main body 60 and a cyclone block 70 that is a centrifugal oil separator in the housing 10.

  The housing 10 includes a main body case 11 having a cylindrical body with one end closed and the other end open, and a front head 12 covering the other open end of the main body case 11. A space for accommodating the compressor main body 60 and the cyclone block 70 (oil separator) is formed inside the housing 10 in a state assembled to the main body case 11.

  The compressor body 60 accommodated in the housing 10 divides the space inside the housing 10 into a left space and a right space sandwiching the compressor body 60 in FIG.

  Sealing members such as O-rings are respectively installed on the side blocks 20 and 30 (the front side block 20 and the rear side block 30) disposed on both sides of the compressor main body 60, and the sealing members for the front side block 20 are provided. By contacting the front head 12, the right space in FIG. 1 is kept airtight. On the other hand, the seal member of the rear side block 30 is in contact with the main body case 11, and the left space in FIG. 1 is kept airtight. .

  Of the two spaces partitioned inside the housing 10, the space on the right side facing the front side block 20 of the compressor main body 60 is supplied with low-pressure refrigerant gas G from the evaporator through a suction port 12 a formed in the front head 12. The suction chamber 13 in the low-pressure atmosphere to be introduced, and the left space where the rear side block 30 of the compressor main body 60 faces is discharged through the discharge port 11a formed in the main body case 11 to discharge the high-pressure refrigerant gas G to the condenser. The discharge chamber 14 is a high-pressure atmosphere.

  The compressor main body 60 includes a rotary shaft 51 that is driven to rotate about an axis C, a columnar rotor 50 that rotates integrally with the rotary shaft 51, and a cross-sectional contour that surrounds the outer periphery 52 of the rotor 50. A cylinder 40 having a substantially elliptical inner peripheral surface 49 and open at both ends, and embedded so as to protrude outward from the outer peripheral surface 52 of the rotor 50, and the tip of the protruding side is the inner peripheral surface of the cylinder 40 For example, five plate-like vanes 58 provided on the rotor 50 at equiangular intervals around the rotation shaft 51 and the open end faces on both sides of the cylinder 40 are made variable so as to follow the contour shape of 49. The front side block 20 and the rear side block 30 are fixed from the outside so as to cover the open end face.

  The volume of the compression chamber 48 partitioned by the two side blocks 20, 30, the rotor 50, the cylinder 40, and the two vanes 58, 58 that precede and follow the rotation direction of the rotation shaft 51 is used to rotate the rotation shaft 51. Therefore, by repeating the increase / decrease, the refrigerant gas G sucked into the compression chambers 48 from the suction port 12a via the suction chamber 13 and the front side block 20 is compressed, and the discharge port is discharged via the rear side block 30 and the discharge chamber 14. It is comprised so that it may discharge outside from 11a.

  One of the portions of the rotating shaft 51 that protrudes from both end surfaces of the rotor 50 is pivotally supported by the bearing portion of the front side block 20, and extends outward through the front head 12. It is connected to a driving force transmission unit 80 to which external power (not shown) is transmitted.

  The other side of the protruding portion of the rotating shaft 51 is pivotally supported by the bearing portion of the rear side block 30.

  Refrigerating machine oil R is stored at the bottom of the discharge chamber 14. The refrigerating machine oil R receives the pressure of the high-pressure refrigerant gas G discharged into the discharge chamber 14, and receives the rear side block 30, the cylinder 40, and the front side. The oil is supplied to the vane groove of the rotor 50 through the oil passages 32 a, 32 b, 44, and 22 formed in the block 20, and becomes a back pressure that causes the vane 58 to protrude outward from the outer peripheral surface 52 of the rotor 50.

  The refrigerating machine oil R exudes from the gap between the vane 58 and the vane groove, the gap between the rotor 50 and the side blocks 20, 30, etc. in addition to the back pressure described above, Lubricating and cooling functions are also exhibited at the contact portions between the side blocks 20 and 30 and at the contact portions between the vane 58 and the cylinder 40 and the side blocks 20 and 30.

  Since a part of the refrigerating machine oil R is mixed with the refrigerant gas G in the compression chamber 48 as described above, the refrigerating machine oil R is separated from the refrigerant gas G by the cyclone block 70.

  The cyclone block 70 is attached to the outer surface of the rear side block 30 adjacent to the compressor main body 60 in the direction in which the rotation shaft 51 extends, and the high pressure discharged from the compression chamber 48 through the rear side block 30. The refrigerating machine oil R (oil content) mixed in the refrigerant gas G is centrifuged from the refrigerant gas G.

  In detail, the cyclone block 70 has a columnar space 71b whose bottom end portion is closed to form a bottom portion 71a, and the bottom portion 71a has an oil discharge hole 71c communicating with the outside. It has a member 71 and a substantially cylindrical inner cylinder portion 72a having a smaller diameter than the columnar space 71b of the main body member 71, and is disposed substantially coaxially with the central axis F of the columnar space 71b in the columnar space 71b. The inner cylinder member 72 is provided.

  The refrigerant gas G mixed with the refrigerating machine oil R discharged from the compressor main body 60 is partitioned by the inner peripheral surface of the main body member 71 of the cyclone block 70 and the outer peripheral surface of the inner cylindrical portion 72a of the inner cylindrical member 72. The centrifugal oil acts on the refrigerating machine oil R mixed with the refrigerant gas G during the period of descending while spirally turning the cylindrical oil separation space 73 formed in this way, and the refrigerating machine oil R becomes the refrigerant gas. It is centrifuged from G, discharged from the cyclone block 70 through an oil discharge hole 71c formed in the bottom 71a, stored in the bottom of the discharge chamber 14, and used as the aforementioned back pressure or the like.

  On the other hand, the refrigerant gas G from which the refrigerating machine oil R has been separated is reflected and rises at the bottom 71a of the columnar space 71b, passes through the inner space of the inner cylindrical portion 72a, and passes through the discharge port 11a to the condenser. To be supplied.

  Here, as shown in FIG. 2, the columnar space 71 b of the main body member 71 has a rotational axis 51 that is longer than the length D <b> 2 along the direction K orthogonal to the direction (axial center C) in which the rotational axis 51 extends. The length D1 along the extending direction is formed to have a short outer edge contour cross section.

  Specifically, the contour shape is formed so that the curvature continuously changes. Specifically, the length D2 along the direction K orthogonal to the direction C in which the rotating shaft 51 extends is defined as the major axis. Further, it is formed in an elliptical contour shape having a short diameter of length D1 along the direction C in which the rotation shaft 51 extends.

  On the other hand, the inner cylinder part 72a has a substantially perfect outer edge contour shape and cross section of the inner edge contour shape.

  According to the compressor 100 of the present embodiment configured as described above, the columnar space 71b of the cyclone block 70 is longer than the length D2 along the direction K orthogonal to the direction C in which the rotation shaft 51 extends. By having a cross section in which the length D1 along the direction C in which the rotation shaft 51 extends has a short contour shape, the contour shape of the outer shape of the main body member 71 also has a length L along the direction C in which the rotation shaft 51 extends. Thus, the length of the discharge chamber 14 along the direction C in which the rotating shaft 51 extends can be shortened, and the size of the compressor 100 can be reduced.

  Moreover, since the direction K orthogonal to the direction C in which the rotating shaft 51 extends coincides with the diameter direction of the compressor main body 60, the length of the outer shape of the main body member 71 along the direction K is the compressor. Since the size of the outer shape of the compressor 100 is not affected even if it is increased to a range that matches the size of the main body 60 in the diameter direction, the length of the columnar space 71 of the main body member 71 along this direction K is not affected. It is not necessary to shorten D2 to the length D1 along the direction C in which the rotation shaft 51 extends.

  Therefore, the length D2 of the columnar space 71 of the main body member 71 along the direction K orthogonal to the direction C of the rotation shaft 51 is defined as the length D1 along the direction C of the rotation shaft 51. Is less likely to cause a reduction in the separation performance of the refrigerating machine oil R due to a significant increase in the flow resistance of the refrigerant gas G that swirls and passes through the oil separation space 73.

  In the compressor 100 of the present embodiment, the refrigerant gas G guided to the oil separation space 73 of the cyclone block 70 swirls along the outline of the columnar space 71b that forms the outer wall surface of the oil separation space 73. However, since the columnar space 71b has a cross-section with a contour shape formed so that the curvature continuously changes, the refrigerant gas G along the contour of the columnar space 71b is smoothly swirled. be able to.

  Specifically, the cross-section of the contour shape formed so that the curvature continuously changes has a length D2 along the direction K orthogonal to the direction C in which the rotation shaft 51 extends, as the major axis. The refrigerant gas G that passes through the oil separation space 73 has a portion with a large radius of curvature because it has a cross section of an elliptical contour with the length D1 along the direction C along which the shaft 51 extends. The magnitude of the acting centrifugal force changes abruptly when passing through a portion with a small radius of curvature, and the ability to separate the refrigerating machine oil R from the refrigerant gas G due to this sudden change in centrifugal force. Can be improved.

  In the compressor 100 of the above-described embodiment, the inner cylinder portion 72a of the cyclone block 70 has a cross section whose outer edge contour shape is a perfect circle. However, as shown in FIG. The length d1 along the direction C in which the rotation shaft 51 extends is shorter than the length d2 in the direction K orthogonal to the direction C in which the rotation shaft 51 extends, and has a cross-section with an outer edge contour shape. Moreover, according to the compressor 100 of the embodiment thus configured, the cylindrical oil separation space 73 partitioned by the inner peripheral surface of the main body member 71 and the outer peripheral surface of the inner cylindrical portion 72a, that is, the refrigerant gas G Fluctuations in the width of the passage that passes while turning can be suppressed, and fluctuations in the flow resistance of the refrigerant gas G can be suppressed.

  Further, in the cyclone block 70 shown in FIG. 2, the columnar space 71b has an elliptical cross section, but the gas compressor of the present invention is not limited to this form. As shown in Fig. 4, having a cross-section with a contour shape (for example, a semicylindrical cross-section, etc.) obtained by removing the corners of a rectangle and connecting adjacent sides with a smooth curve In addition, the contour shape may have a columnar space having a cross section of the contour shape formed so that the curvature continuously changes.

  The gas compressor according to the present invention may perform only one cycle of sucking, compressing and discharging gas during one rotation of the rotor, or sucking gas during one rotation of the rotor. The compression and the discharge may be performed for two cycles.

  Further, the gas compressor according to the present invention is not limited to the one having the five vanes 58 like the compressor 100 of the above-described embodiment, and the number of vanes is two, three, four, 6 or the like may be used, and the same operation and effect as the compressor 100 of the above-described embodiment can be obtained by a gas compressor including such a number of vanes.

DESCRIPTION OF SYMBOLS 10 Housing 20 Front side block 30 Rear side block 40 Cylinder 50 Rotor 51 Rotating shaft 58 Vane 60 Compressor main body 70 Cyclone block (oil separator)
71 Main body member 71b Columnar space 71c Oil discharge hole 72 Inner cylinder member 72a Inner cylinder part 73 Oil separation space 100 Vane rotary compressor (gas compressor)
C axis, direction D1, D2, d1, d2 length F central axis G refrigerant gas (gas)
K direction L length R refrigeration oil (oil content)

Claims (4)

A gas having oil mixed with a main body member having a columnar space with a lower end surface closed, and a substantially cylindrical inner cylinder member that is substantially coaxial with the columnar space and disposed in the columnar space. A rotating shaft that centrifuges the oil from the gas by passing through a substantially cylindrical oil separation space partitioned by the inner peripheral surface of the main body member and the outer peripheral surface of the inner cylinder member while turning. An oil separator provided adjacent to the direction of extension of the rotary shaft with respect to the compressor body having
The columnar space of the main body member has a contour-shaped cross section whose length along the direction in which the rotating shaft extends is shorter than the length along the direction orthogonal to the direction in which the rotating shaft extends. A gas compressor characterized by being.   The gas compressor according to claim 1, wherein the contour shape is formed such that the curvature continuously changes.   An elliptical outline in which the columnar space of the main body member has a major axis having a length along a direction orthogonal to a direction in which the rotating shaft extends and a minor axis having a length along the direction in which the rotating shaft extends. The gas compressor according to claim 1, wherein the gas compressor has a cross section having a shape.   The inner cylinder member has a cross section of an outer edge contour shape whose length along the direction in which the rotating shaft extends is shorter than the length along the direction orthogonal to the direction in which the rotating shaft extends. The gas compressor according to any one of claims 1 to 3, wherein: