JP2010144548A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gas compressor preventing starting performance deterioration even if a liquid refrigerant is accumulated inside of a housing. <P>SOLUTION: A cyclone block 70 is attached to a compressor body in such a manner that a body portion 71 and the shaft 73 of an inner cylinder portion 72 are inclined by an angle θ around a rotating shaft 51 with respect to a vertical line V so that a part of the lower end edge 72a of the inner cylinder portion 72 of the cyclone block 70 (oil separator) is exposed higher than the liquid level Rm of the liquid refrigerant G'. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

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

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

  Here, a general compressor compresses refrigerant gas into a housing, and discharges oil such as refrigerating machine oil from the compressed refrigerant gas (compressed gas refrigerant) discharged from the compressor main body. It has a configuration including an oil separator for separation.

As an oil separator, for example, it has a main body part that forms a substantially columnar inner space, and a substantially cylindrical (pipe-shaped) inner cylinder part that is provided substantially coaxially with the inner space in this inner space. Compressed refrigerant gas discharged from the compressor body is included in the compressed refrigerant gas while swirling from above to below in a substantially cylindrical oil separation space defined by the inner surface of the main body and the outer surface of the inner cylinder. What separates the refrigerating machine oil is known (patent documents 1 and 2).
JP 2008-008259 A Japanese Patent Laid-Open No. 7-12072

  By the way, in an environment where the outside air temperature is low, such as in winter, the opportunity to circulate the refrigerant gas through the system and operate the air conditioning system is reduced, and if the standing time in such a low temperature environment becomes long, the refrigerant gas in the system Most of the liquid is liquefied and collected inside the compressor. As a result, the liquid level of the liquefied refrigerant (liquid refrigerant; oil content such as refrigeration oil is also included) is at the lower edge of the inner cylinder of the oil separator It will be in the state which rose to the upper part.

  Here, the compressed refrigerant gas swirls outside the inner cylinder part to below the lower end edge of the inner cylinder part, reflects off the bottom surface of the main body part, passes through the inside of the inner cylinder part, and then goes outside the housing. In order to discharge, in a state where the lower end edge of the inner cylinder portion of the oil separator is immersed in the liquid refrigerant (a state in which the liquid refrigerant liquid surface is located above the lower end edge of the inner cylinder portion), the compressed refrigerant gas The discharge path is blocked.

  Then, when the operation of the compressor is resumed in this state, the refrigerant gas discharged from the compressor body passes through the outside of the inner cylinder portion and pushes down the liquid refrigerant liquid level, but the liquid level of the inner cylinder portion is reduced. If it is not pushed down below the lower edge, the refrigerant gas is not discharged out of the housing, which hinders normal operation of the system.

  In addition, by continuing to push down the liquid refrigerant, the pressure difference between the high pressure and the low pressure is less likely to occur inside the compressor, resulting in poor startability.

  In addition, the above-described oil separator by centrifugal separation has a high performance for separating the refrigerating machine oil from the refrigerant gas. Therefore, even if the refrigerant gas does not liquefy, the refrigerating machine oil separated from the refrigerant gas is contained in the housing. When a large amount is accumulated, the liquid level of the refrigerating machine oil rises similarly to the liquid level rise of the liquid refrigerant described above, and the refrigerating machine oil may block the discharge path straddling the lower end edge of the inner cylinder portion.

  The present invention has been made in view of the above circumstances, and provides a gas compressor that can prevent the start-up performance from being deteriorated even when liquid refrigerant or refrigerating machine oil is accumulated inside the housing. The purpose is to provide.

  In the gas compressor according to the present invention, the oil separator has a cylindrical shape above the liquid level of the liquid refrigerant or refrigerating machine oil even in a state where the liquid refrigerant or refrigerating machine oil in which the gaseous refrigerant is liquefied is accumulated inside the housing. Gas refrigerant discharged from the compressor body and discharged to the outside of the inner cylinder part from the communicating part to the inside of the inner cylinder part by having a structure in which the outer side and the inner side of the inner cylinder part communicate with each other Thus, it is possible to prevent the startability of the gas compressor from being deteriorated.

  That is, the gas compressor according to the present invention separates oil from the compressor main body that compresses the supplied gas refrigerant into a high-pressure compressed gas refrigerant inside the housing, and the compressed gas refrigerant discharged from the compressor main body. An oil separator, and the oil separator includes a main body portion that forms a substantially cylindrical inner space, a substantially cylindrical inner cylinder portion that is provided in the inner space and substantially coaxial with the inner space. The compressed gas refrigerant discharged from the compressor main body swivels from above to below in a substantially cylindrical oil separation space defined by the inner surface of the main body portion and the outer surface of the inner cylinder portion. In the gas compressor for separating the refrigerating machine oil contained in the compressed gas refrigerant, the oil separator is stored in the housing as a liquid refrigerant in which the gaseous refrigerant is liquefied (or the refrigerating machine oil is inside the housing). In the state of Can have an outer and inner side of the inner cylinder part in above the liquid level of the liquid refrigerant (the refrigerant oil) is characterized in that it is formed in communication.

  According to the gas compressor according to the present invention configured as described above, even when liquid refrigerant or refrigeration oil is accumulated in the housing, it is discharged from the compressor body and discharged to the outside of the inner cylinder portion. The gas refrigerant can escape to the inside of the inner cylinder part through the part communicating with the outside and the inside of the inner cylinder part above the liquid level of the liquid refrigerant (refrigeration oil). It can prevent that the starting property of a gas compressor falls.

  In the gas compressor according to the present invention, the oil separator includes the main body portion and the inner cylinder so that at least a part of the lower end edge of the inner cylinder portion is exposed above the liquid surface of the liquid refrigerant. It is preferable that the axial line of the part is attached to the compressor body with the axis thereof tilted with respect to the vertical direction.

  According to the gas compressor according to the present invention that is preferably configured as described above, the oil separator is attached to the compressor main body with the axis of the main body and the inner cylinder being inclined with respect to the vertical direction. Even when the refrigerant or refrigerating machine oil is accumulated inside the housing, at least a part of the lower end edge of the inner cylinder part is exposed above the liquid level of the liquid refrigerant or refrigerating machine oil. The gas refrigerant that has passed through the outside of the part can escape to the inside of the inner cylinder part across the lower end edge part of the inner cylinder part exposed above the liquid level.

  Therefore, it is possible to prevent the startability of the gas compressor from being lowered.

  Moreover, the gas compressor according to the present invention having a preferred configuration can be realized with a simple structure in which the oil separator is attached to the compressor body in a state inclined with respect to the vertical line.

  In the gas compressor according to the present invention, the oil separator has a communication hole that communicates the outside and the inside of the inner cylinder part in a portion of the inner cylinder part above the liquid level of the liquid refrigerant. Preferably it is formed.

  According to the gas compressor according to the present invention that is preferably configured as described above, the oil separator includes an outer side and an inner side of the inner cylinder part at a portion of the inner cylinder part above the liquid level of the liquid refrigerant. Since the communication hole is formed to communicate, even when the liquid refrigerant or the refrigeration oil is accumulated inside the housing, the gas refrigerant that has passed through the outside of the inner cylinder portion is more than the liquid refrigerant or the refrigeration oil liquid level. Further, it can escape to the inside of the inner cylinder portion through the communication hole formed in the inner cylinder portion at the upper side.

  Therefore, it is possible to prevent the startability of the gas compressor from being lowered.

  In addition, the gas compressor according to the present invention having a preferred configuration has a communication hole formed only in the upper part of the inner cylinder part (the part above the assumed maximum liquid level position of the liquid refrigerant or refrigerating machine oil). It can be realized with a simple structure.

  In the gas compressor according to the present invention, the compressor body includes discharge ports for discharging the compressed gas refrigerant at two positions that are point-symmetric about the rotation axis in the vane rotary type gas compression mechanism, The oil separator has a single inlet for introducing the compressed gas refrigerant into the oil separation space, and two compressed gas refrigerant passages for communicating the two discharge ports and the single inlet, respectively. It is preferable that both of the two compressed gas refrigerant passages have an upward inclination from the discharge port toward the single introduction port.

  According to the gas compressor according to the present invention that is preferably configured as described above, the two compressed gas refrigerant passages that respectively communicate the two discharge ports and the single introduction port are both provided from the discharge port to the single introduction port. Therefore, the energy loss when the compressed gas passes through the both compressed gas refrigerant passages becomes substantially equal.

  Therefore, one compressed gas refrigerant passage passes through both the compressed gas refrigerant passages in a conventional gas compressor in which the other compressed gas refrigerant passage is a route that travels in an upward slope and the other compressed gas refrigerant passage is a route that travels in a downward slope. The non-uniform energy loss of the compressed gas can be corrected with the preferred gas compressor of the present invention.

  Further, in the conventional gas compressor, since one of the two discharge ports is located considerably below the other, the discharge port located below is immersed in the liquid refrigerant or refrigerator oil accumulated in the housing. This may cause resistance when compressed gas refrigerant is discharged from the discharge port, and liquid refrigerant or refrigeration oil may flow into the compression chamber from the discharge port. However, according to the gas compressor having a preferable configuration of the present invention, since the two discharge ports are substantially at the same high position, both the discharge ports may be clogged with liquid refrigerant or refrigerating machine oil. It is possible to reduce and prevent deterioration of startability.

  According to the gas compressor according to the present invention, it is possible to prevent the start-up performance from being deteriorated even when the liquid refrigerant or the refrigerating machine oil is accumulated in the housing.

DESCRIPTION OF EXEMPLARY EMBODIMENTS The best mode for carrying out the gas compressor of the invention will be described below with reference to the drawings.
(Embodiment 1)
FIGS. 1 and 2 are views respectively showing a longitudinal section and a transverse section of a vane rotary compressor 100 which is an example of a gas compressor, which is a premise of an embodiment of the gas compressor according to the present invention.

  2 shows a cross section (transverse section) along the line AA in FIG. 1, and FIG. 1 shows a cross section (longitudinal section) along the line BB in FIG.

  The illustrated compressor 100 is configured, for example, as a part of an air conditioning system (hereinafter simply referred to as an air conditioning system) that performs cooling using the heat of vaporization of a cooling medium, and condensing that is another component of the air conditioning system. Along with a condenser, an expansion valve, an evaporator, and the like (all not shown), they are provided on a cooling medium circulation path.

  The compressor 100 compresses the refrigerant gas G 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 liquefies the compressed refrigerant gas G 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 compressor 100 is attached to the compressor body 60 housed in the housing 10 including the case 11 and the front head 12 and the front head 12, and transmits a driving force from a driving source (not shown) to the compressor body. A transmission mechanism 80.

  The case 11 has a cylindrical body with one end closed, and the front head 12 is assembled so as to cover the end of the case 11 on the opened side. The front head 12 is formed with a suction port 12a through which a low-pressure refrigerant gas G is drawn from the evaporator. On the other hand, the case 11 uses the high-pressure refrigerant gas G compressed by the compressor body as a condenser. A discharge port 11a for discharging is formed.

  The compressor main body 60 accommodated in the housing 10 includes a rotary shaft 51 that is driven to rotate about the axis by the driving force transmitted by the transmission mechanism 80, and a columnar rotor 50 that rotates integrally with the rotary shaft 51. And a cylinder 40 having a substantially elliptical inner peripheral surface 49 surrounding the outer peripheral surface of the rotor 50 and open at both ends, embedded in the rotor 50, and supplied to both end surfaces of the rotor 50. Under the back pressure of the refrigerating machine oil R (oil component), it is possible to project outward from the outer peripheral surface of the rotor 50 (toward the inner peripheral surface 49 of the cylinder 40), and the tip of the projecting side is the end of the cylinder 40. The amount of protrusion is variable so as to follow the contour shape of the inner peripheral surface 49, and five plate-like vanes 58 embedded in the rotor 50 at equal angular intervals around the rotation shaft 51, and both side end surfaces of the cylinder 40 From the outside Made from a fixed front side block 30 and the rear side block 20. so as to cover an end face of respectively.

  The two side blocks 20, 30 have bearings 22, 32 that respectively support portions of the rotating shaft 51 that protrude from both end faces of the rotor 50.

  The volume of each compression chamber 48 defined 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 rotary shaft 51 is transferred by the transmission mechanism 80. By repeating the increase / decrease according to the rotation of the rotating shaft 51 and the rotor 50 by the transmitted driving force, the refrigerant gas G sucked into each compression chamber 48 is compressed, and oil is separated through the discharge passage of the rear side block 20. It is discharged into the discharge chamber 21 through a cyclone block 70 that is a container.

  The discharge chamber 21 is a chamber in which the high-pressure refrigerant gas G discharged from the compressor body 60 is discharged, and is formed by the rear side block 20 and the case 11.

  While the high-pressure refrigerant gas G passes through the cyclone block 70 from the compression chamber 48, the refrigerating machine oil R mixed in the refrigerant gas G is separated and dropped at the bottom of the discharge chamber 21, and the refrigerating machine oil R is discharged into the discharge chamber 21. Stored at the bottom.

  The stored refrigerating machine oil R lubricates, cools, and cleans the sliding portion of the compressor 100, and causes the vane 58 to protrude toward the inner peripheral surface 49 of the cylinder 40, with the tip thereof being the inner peripheral surface. For example, a back pressure is applied to the vane 58 so as to be biased to a state where it is brought into contact with 49.

  In the rear side block 20 of the compressor main body 60, an oil guide that guides the refrigerating machine oil R, which is stored at the bottom of the discharge chamber 21 and becomes high pressure by the pressure of the refrigerant gas G discharged into the discharge chamber 21, to the end face of the rotor 50. A path 23 is formed.

  The oil guide path 23 extends to the bearing 22 along a substantially vertical direction, and the refrigerating machine oil R guided to the bearing 22 passes through a slight gap between the bearing 22 and the outer peripheral surface of the rotating shaft 51 and passes through the rear side block. 20 is supplied to the Sarai groove 25 formed on the end face of the steel plate 20.

  On the other hand, the cylinder 40 and the front side block 30 are also formed with oil guide passages 43 and 33 that guide the refrigerating machine oil R to the end face of the rotor 50, similarly to the rear side block 20.

  As shown in FIG. 2, the compressor body 60 is set to have a posture around the rotation shaft 51 so that a straight line connecting the oil guide path 43 and the center of the rotation shaft 51 is along the vertical direction.

  The oil guide path 33 extends to the bearing 32, and the refrigerating machine oil R guided to the bearing 32 through the oil guide paths 23, 43, 33 passes through a slight gap between the bearing 32 and the outer peripheral surface of the rotating shaft 51. Then, it is supplied to the Sarai groove 35 formed on the end surface of the front side block 30.

  Here, the rotor 50 is formed with five slit-like vane grooves 56 (FIG. 2) in which the above-described vanes 58 are embedded at equal angular intervals around the rotation center of the rotor 50. Each of the vanes 58 is embedded in a centrifugal force generated by the rotation of the rotor 50 and the refrigerating machine oil R applied to the back pressure chamber 59 defined by the bottom surface of the vane groove 56 and the vane 58. Can be protruded toward the inner peripheral surface 49 of the cylinder 40 by the hydraulic pressure (back pressure) due to the pressure, and the protruding tip of the vane 58 is urged to rotate in contact with the inner peripheral surface 49 of the cylinder 40. As the shaft 51 rotates, the vane 58 advances and retreats in the vane groove 56.

  Thereby, each compression chamber 48 repeats a change in volume according to the rotation of the rotor 50, and sucks the refrigerant gas G from the suction chamber during a period when the volume increases, and sucks the refrigerant gas G sucked during a period when the volume decreases. The high-pressure refrigerant gas G obtained by compressing the gas is alternately discharged into two discharge chambers 45, 45 provided at point-symmetric positions around the rotation shaft 51, and is discharged from the discharge chambers 45, 45. Then, the air is introduced into the cyclone block 70 through the discharge ports 28 a and 28 b formed in the rear side block 20, and is discharged into the discharge chamber 21 through the cyclone block 70.

  The back pressure chamber 59 is opened through to both end surfaces of the rotor 50, and the refrigerating machine oil R reaching the salai groove 25 of the rear side block 20 is supplied, and the back pressure chamber 59 is opened at the end surface of the rotor 50. However, the refrigeration oil R is supplied from the salai groove 25 to the back pressure chamber 59 during the period facing the salai groove 25.

  Similarly, the refrigerating machine oil R is supplied to the back pressure chamber 59 from the salai groove 35 of the front side block 30 while the opening of the back pressure chamber 59 on the end face of the rotor 50 faces the salai groove 35 of the front side block 30. The

  As shown in FIG. 3, the cyclone block 70 includes a main body 71 that is attached to the outer surface of the rear side block 20 in the discharge chamber 21 and has a substantially cylindrical inner space 71 h, and an inner space 71 h in the inner space 71 h. A substantially cylindrical inner cylinder portion 72 provided substantially coaxially with the axis of the substantially cylindrical shaft, and the compressed refrigerant gas G discharged from the discharge chambers 45 and 45 of the compressor body 60 is The refrigerating machine oil R contained in the compressed refrigerant gas G is swirled while descending from the top to the bottom of the substantially cylindrical oil separation space 75 defined by the inner surface and the outer surface of the inner cylinder portion 72. To separate.

  The separated refrigerating machine oil R is dropped into the discharge chamber 21 through an oil drain hole 71 g formed in the bottom of the main body 71 and discharged.

  On the other hand, the compressed refrigerant gas G from which the refrigerating machine oil R has been separated is reflected and rises at the bottom of the internal space 71 h of the main body 71, and is discharged to the discharge chamber 21 through the inner space 76 of the inner cylinder 72. It is supplied from the chamber 21 to the condenser of the air conditioning system via the discharge port 11a.

  In FIG. 3, reference numeral 71c is a single inlet formed on the outer surface of the main body 71 (surface attached to the outer surface of the rear side block 20), and reference numeral 71f extends from the inlet 71c to the internal space 71h. This is an introduction path for introducing the refrigerant gas G.

  Reference numeral 71d denotes one of two compressed refrigerant gas passages (compressed gas refrigerant passages) that communicate the two discharge ports 28a and 28b of the rear side block 20 and the single inlet port 71c, which will be described in detail later. It is.

  The above is the basic premise of the compressor 100, and the features of the present invention will be described below with reference to the embodiments shown in FIGS.

  In the compressor 100 of this embodiment, the cyclone block 70 is provided such that the main body portion 71 and the shaft 73 of the inner cylinder portion 72 are inclined with respect to the vertical direction V by a predetermined angle θ. .

  The cyclone block 70 is provided with an inclination angle θ with respect to the vertical direction for the following reason.

  That is, in an environment where the outside air temperature is low, such as in winter, when there is little opportunity to circulate the refrigerant gas G to the air conditioning system and leave the system to operate for a long time, a large amount of the refrigerant gas G in the system Is liquefied and accumulated in the discharge chamber 21 of the compressor 100. As a result, the liquid level Rm of the liquefied refrigerant (liquid refrigerant G ′; including the refrigerating machine oil R dissolved in the liquid refrigerant G ′) is, for example, As shown in FIG. 4A, the discharge chamber 21 is raised to a height position, for example, nearly half.

  Here, since the oil drain hole 71g is formed in the bottom of the main body 71 of the cyclone block 70, the compressor 100 shown in FIGS. 1, 2, and 3 which is the premise of the present embodiment has a high discharge chamber 21. When the liquid refrigerant G ′ is accumulated up to the position, the liquid refrigerant G ′ enters the internal space 71h of the main body portion 71 through the oil drain hole 71g, and the lower end edge 72a of the inner cylinder portion 72 is completely immersed. It becomes a state.

  In this case, the compressed refrigerant gas G sent to the oil separation space 75 pushes down the liquid level Rm of the liquid refrigerant G ′ accumulated in the internal space 71 h so that the liquid level Rm is the lower end of the inner cylindrical portion 72. At the moment when the refrigerant gas G is pushed down below the edge 72a, the refrigerant gas G is sent to the inner space 76 of the inner cylindrical portion 72 and is discharged through the discharge chamber 21 to the condenser of the system.

  However, since the discharged refrigerant gas G consumes the energy when the liquid level Rm of the liquid refrigerant G ′ accumulated in the internal space 71h is pushed down, the energy of the compressed refrigerant gas G is reduced. There was a risk that it would deteriorate and interfere with the normal operation of the system.

  Therefore, in the present embodiment shown in FIG. 4, the cyclone block 70 has a vertical line V so that a part of the lower end edge 72a of the inner cylindrical portion 72 is exposed above the liquid level Rm of the liquid refrigerant G ′. On the other hand, it is attached at an angle θ.

  The angle θ is assumed in the discharge chamber 21 by the total amount of the amount of the refrigerating machine oil R and the amount of the liquid refrigerant G ′ that is condensed while the refrigerant gas G is saturated at a low temperature. So that a part of the lower end edge 72a of the inner cylinder part 72 is higher than the height of the liquid level Rm, that is, a part of the lower end edge 72a of the inner cylinder part 72 is higher than the liquid level Rm. Is set to be exposed.

  According to the compressor 100 of the embodiment configured as described above, as shown in FIG. 4A, the liquid refrigerant G ′ is exposed above the liquid level Rm and above the liquid level Rm. Since the oil separation space 75 (outer side) and the inner space 76 (inner side) of the inner cylinder part 72 communicate with each other across the lower end edge 72a, the oil in the inner cylinder part 72 is discharged from the compressor body 60. The refrigerant gas G discharged into the separation space 75 can escape to the inner space 76 across the lower end edge 72a of the inner cylinder part 72 without pushing down the liquid level Rm. As a result, the refrigerant gas G has The system can be discharged without losing energy, and the start-up performance of the compressor 100 can be prevented from being lowered.

  Here, FIG. 4B is a view of the surface of the main body 71 of the cyclone block 70 according to the present embodiment attached to the rear side block 20 as viewed from an arrow E in FIG. 3, and FIG. Show.

  In the main body 71, discharge port recesses 71a and 71b are formed at positions facing the two discharge ports 28a and 28b of the rear side block 20, respectively. Further, these two discharge port recesses 71a and 71b Two compressed refrigerant gas passages 71d and 71e (compressed gas refrigerant passages) communicating with the single inlet 71c described above are formed.

  The lengths of these two compressed refrigerant gas passages 71d and 71e are set to be equal to each other.

  Here, the two discharge port recesses 71a and 71b need to be formed at positions facing the two discharge ports 28a and 28b of the rear side block 20, respectively. As shown in FIG. When the block 70 is provided in a state where the block 70 is rotated about the rotation shaft 51 by an angle θ (the shaft 73 of the cyclone block 70 is inclined by the angle θ with respect to the vertical line V), the discharge port recesses 71a and 71b and the rear side block 20 are provided. The discharge ports 28a and 28b are displaced.

  Therefore, similarly to the cyclone block 70, the compressor main body 60 also needs to be rotated by an angle θ around the rotation shaft 51 as shown in FIG.

  Then, at first glance, when the compressor main body 60 and the cyclone block 70 are integrally rotated by the angle θ around the rotation shaft 51, in an extreme case, the entire compressor 100 is simply rotated around the rotation shaft 51 by the angle θ. It looks like there is no difference from the state of rotating and arranging.

  However, when the conventional compressor is simply rotated around the rotation shaft 51 by the angle θ, the oil guide path 23 for pumping the refrigerating machine oil R from the bottom of the discharge chamber 21 to the vane groove 56 is also perpendicular to the vertical line V. Therefore, the height position of the lower end opening of the oil guide passage 23 is significantly higher than the required low position (position close to the bottom surface of the discharge chamber 21). There is a possibility that the refrigerating machine oil R cannot be introduced into the oil guide passage 23.

  Therefore, the state in which the conventional compressor is simply rotated around the rotation shaft 51 by the angle θ cannot essentially exhibit the function of the compressor.

  On the other hand, the compressor 100 of the present embodiment is in a state where the compressor main body 60 is rotated by the angle θ around the rotation shaft 51 as shown in FIG. Further, as shown in FIG. 5B, the oil guide passage 23 is formed so as to extend along the vertical line V.

  As the oil guide passage 23 is formed at an angular position different from the conventional one, the oil guide passage 43 communicating with the oil guide passage 23 is also provided with parentheses in the conventional position (FIG. 5A). And a position rotated by an angle θ around the rotation shaft 51. Similarly, the oil guide passage 33 of the front side block 30 is also formed at a position rotated by an angle θ.

  Then, since the oil guide passages 23, 43, 33 are formed at angular positions different from the conventional ones, the cyclone block 70 and the compressor main body 60 are respectively rotated about the rotation shaft 51 by an angle θ ( Also in the embodiment provided in the state shown in FIGS. 4 and 5, the refrigerating machine oil R at the bottom of the discharge chamber 21 can be appropriately introduced into the oil guide passages 23, 43 and 33.

  On the outer surface of the rear side block 20, grooves 28c and 28d are formed in portions facing the two compressed refrigerant gas passages 71d and 71e of the cyclone block 70, respectively. The grooves 28c and 28d of the rear side block 20 and the cyclone are formed. The compressed refrigerant gas passages 71d and 71e of the block 70 are opposed to each other so that the cross-sectional area through which the compressed refrigerant gas G can pass can be increased, and the flow resistance corresponding to the cross-sectional area of the passage is reduced. can do.

  Further, in the compressor 100 of the present embodiment, the compressor main body 60 and the cyclone block 70 are rotated around the rotation shaft 51 by an angle θ. At this time, as shown in FIG. Since both the passages 71d and 71e are formed to have an upward slope from the discharge port recesses 71a and 71b corresponding to the discharge ports 28a and 28b toward the introduction port 71c, both the compressed refrigerant gas passages 71d and 71e are formed. The energy loss when the compressed refrigerant gas G passes through can be made substantially uniform between both the passages 71d and 71e.

  Further, the difference in height position between both discharge ports 28a and 28b is the difference in height position between both discharge ports 28a and 28b in a conventional compressor (the compressor shown in FIGS. 1 and 2 which is the premise of this embodiment). As compared with the prior art, it is possible to correct that only one discharge port (the discharge port 28b in FIG. 2) is disposed at a low position as in the prior art.

Accordingly, it is possible to prevent only one of the discharge ports 28b from being immersed in the liquid refrigerant G ′ or the refrigerating machine oil R. From this viewpoint, it is possible to prevent the startability from being lowered.
(Embodiment 2)
The compressor 100 according to the above-described embodiment has a configuration in which the cyclone block 70 is inclined so that the lower end edge 72a of the inner cylinder portion 72 is exposed above the liquid level Rm of the liquid refrigerant G ′. The outer side (oil separation space 75) and the inner side (inner space 76) of the part 72 are communicated above the liquid level Rm of the liquid refrigerant G ′. It is not limited to the configuration in which the cyclone block 70 is inclined as in the first embodiment.

  That is, for example, as shown in FIGS. 1 to 3, the cyclone block 70 is provided with its axis along the vertical line V as in the prior art (the cyclone block 70 has its axis on the vertical line V). 6, the oil separation space of the inner cylinder portion 72 is located above the liquid level Rm of the liquid refrigerant G ′ in the inner cylinder portion 72, as shown in FIG. 6. If it is a compressor in which the communicating hole 72b which connects 75 and the inner space 76 is formed, it will be embodiment of the gas compressor which concerns on this invention.

  Then, according to the compressor 100 of the embodiment configured as described above, the cyclone block 70 is configured so that the oil in the inner cylinder portion 72 is in the portion of the inner cylinder portion 72 above the liquid level Rm of the liquid refrigerant G ′. Since the communication hole 72b that connects the separation space 75 and the inner space 76 is formed, even if the liquid refrigerant G ′ immerses the entire lower end edge 72a of the inner cylindrical portion 72, the outer side ( The refrigerant gas G passing through the oil separation space 75) can escape to the inner side (inner space 76) of the inner cylinder part 72 through the communication hole 72b formed in the inner cylinder part 72.

  Therefore, it is possible to prevent the startability of the compressor 100 from being lowered.

  Moreover, the compressor 100 of the present embodiment has a simple structure in which the communication hole 72b is simply formed in the upper portion of the inner cylinder portion 72 (the portion above the assumed maximum liquid level Rm of the liquid refrigerant G ′). Can be realized.

It is a longitudinal cross-sectional view (cross-sectional view in alignment with the BB line of FIG. 2) which shows the vane rotary type compressor used as the premise of one Embodiment of the gas compressor which concerns on this invention. It is sectional drawing (cross-sectional view) which shows the cross section along the AA in FIG. It is the figure which expanded the cyclone block in FIG. 1, (a) shows the cross section equivalent to FIG. 1, (b) shows the cross section along CC line in (a), respectively. (A) is the figure seen from the arrow D in FIG. 3 which shows the attachment attitude | position of the cyclone block in the compressor of Embodiment 1, (b) is the cyclone block shown in (a) in FIG. It is the figure seen by arrow E. (A) is a cross-sectional view corresponding to FIG. 2 of the compressor body in the compressor of Embodiment 1, and (b) is a view of the cyclone block shown in FIG. FIG. It is a figure which shows the cyclone block in other embodiment (Embodiment 2) of this invention, (a) The cross section equivalent to FIG. 1, (b) is the cross section along the C'-C 'line in (a). Each is shown.

Explanation of symbols

70 Cyclone block (oil separator)
71 Body 72 Inner cylinder 72a Lower edge 73 Axis 100 Compressor (gas compressor)
V Vertical line (vertical direction)
R Refrigerating machine oil G Refrigerant gas G 'Liquid refrigerant

Claims (4)

A compressor body that compresses the supplied gas refrigerant into a high-pressure compressed gas refrigerant inside the housing, and an oil separator that separates oil from the compressed gas refrigerant discharged from the compressor body,
The oil separator includes a main body portion that forms a substantially columnar inner space, and a substantially cylindrical inner cylinder portion that is provided in the inner space and substantially coaxial with the inner space, and the compressor main body. Compressed gas refrigerant discharged from the cylinder is contained in the compressed gas refrigerant while turning from above to below in a substantially cylindrical oil separation space defined by the inner surface of the main body and the outer surface of the inner cylinder. In the gas compressor that separates the refrigerating machine oil,
The oil separator is formed in such a manner that the outer side and the inner side of the inner cylinder part communicate with each other above the liquid level of the liquid refrigerant even in a state where the gas refrigerant is accumulated in the housing as a liquid refrigerant in which the gaseous refrigerant is liquefied. A gas compressor characterized by being made.   The oil separator tilts the axis of the main body and the inner cylinder with respect to the vertical direction so that at least a part of the lower end edge of the inner cylinder is exposed above the liquid level of the liquid refrigerant. The gas compressor according to claim 1, wherein the gas compressor is attached to the compressor body.   The oil separator is characterized in that a communication hole that communicates the outside and the inside of the inner cylinder part is formed in a portion of the inner cylinder part above the liquid level of the liquid refrigerant. Item 2. The gas compressor according to Item 1. The compressor body includes discharge ports for discharging the compressed gas refrigerant at two positions that are point-symmetric about the rotation axis in a vane rotary type gas compression mechanism,
The oil separator has a single inlet for introducing the compressed gas refrigerant into the oil separation space, and two compressed gas refrigerant passages for communicating the two discharge ports and the single inlet, respectively. 4. The gas compressor according to claim 2, wherein both of the two compressed gas refrigerant passages have an upward inclination from the discharge port toward the single introduction port. 5.

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