JP5062085B2 - Compressor - Google Patents

Description

  The present invention is provided with an oil separator that separates the lubricating oil contained in the refrigerant gas discharged from the compression mechanism, and an oil discharge port that discharges the lubricating oil separated from the refrigerant gas is formed in the oil separator. The present invention relates to a compressor in which a gas discharge port for refrigerant gas is formed.

  For example, as disclosed in Patent Document 1, in a vane compressor, a cylinder block is accommodated in a housing, and side plates are joined to both ends of the cylinder block. A rotor is rotatably accommodated inside the cylinder block. A plurality of vane grooves are formed in the rotor, and vanes are accommodated in the respective vane grooves. An operating chamber (compression chamber) is formed in the cylinder block by these vanes. The refrigerant gas is compressed in the working chamber by rotating the rotor and the vane.

  In Patent Document 1, an oil storage chamber is defined between the rear end face of the rear side plate and the inner surface of the housing. An oil separator is accommodated in the oil storage chamber. The oil separator includes an oil separation chamber formed in the case, and an oil separation cylinder provided in an upper portion of the oil separation chamber. Further, the case is formed with an oil passage (oil discharge port) through which the lubricating oil flows from the oil separation chamber to the oil storage chamber. Further, a guide plate is integrally provided in the case, and the oil level of the lubricating oil stored in the lower portion of the oil storage chamber is stabilized by the guide plate. In addition, the rear side plate is formed with an oil supply passage having one end communicating with the oil storage chamber and the other end communicating with the compression mechanism (vane groove or the like).

Then, when the refrigerant gas compressed in the working chamber is supplied to the oil separator, the refrigerant gas is blown onto the outer peripheral surface of the oil separation cylinder, and the lower part of the oil separation chamber is swung around the outer peripheral surface of the oil separation cylinder. Led. At this time, the lubricating oil is separated from the refrigerant gas by centrifugal separation. The lubricating oil separated from the refrigerant gas drops from the oil passage and is stored in the oil storage chamber. On the other hand, the refrigerant gas from which the lubricating oil has been separated moves upward in the oil separation cylinder, is discharged to the oil storage chamber, and is then led out of the vane compressor (for example, an external refrigerant circuit). Further, the lubricating oil stored in the oil storage chamber is supplied from the oil supply passage to the compression mechanism.
Japanese Patent Laid-Open No. 7-12072

  By the way, in the vane compressor of patent document 1, since the oil separator is accommodated in the oil storage chamber, refrigerant gas is directly discharged from the oil separator into the oil storage chamber. For this reason, the lubricating gas stored in the oil storage chamber is wound up by the refrigerant gas discharged to the oil storage chamber, and there is a problem that the amount of lubricating oil in the oil storage chamber is reduced and the oil level is lowered. If the oil level fluctuates due to the vibration of the vane compressor or the like with the oil level lowered, the refrigerant gas enters the oil supply passage and is supplied from the oil supply passage to the compression mechanism. On the other hand, if the amount of lubricating oil stored in the oil storage chamber increases too much, the volume of the oil storage chamber, which has a large effect of reducing the discharge pulsation, decreases, and abnormal noise due to the discharge pulsation of the vane compressor increases. End up.

  The present invention has been made paying attention to such problems existing in the prior art, and the object thereof is to eliminate the rolling-up of the lubricating oil in the oil storage chamber and the refrigerant gas enters the oil supply passage. An object of the present invention is to provide a compressor that can prevent discharge pulsation.

  In order to solve the above-mentioned problems, the invention according to claim 1 is characterized in that the partition member provided in the housing discharges the inside of the housing to the compression mechanism side and the refrigerant gas compressed by the compression mechanism. An oil separator that separates the lubricating oil contained in the refrigerant gas discharged from the compression mechanism is provided on an end surface of the partition member that faces the discharge chamber, and the oil separator includes the oil separator. A compressor in which an oil discharge port for discharging lubricating oil separated from the refrigerant gas is formed and a gas discharge port for the refrigerant gas is formed, and is opposed to the discharge chamber in the partition member in the discharge chamber. A storage chamber partition portion is joined to the end surface, and an oil storage chamber for storing the lubricating oil is defined between the end surface and the inner surface of the storage chamber partition portion, and the oil discharge port is provided in the oil storage chamber. Communicate Together, the partition member is formed with an oil supply passage having one end communicating with the oil storage chamber and the other end communicating with the compression mechanism, and further, the storage chamber partition portion in the discharge chamber, A first muffler portion formed by a space between an outer surface of the storage chamber partitioning portion and an inner surface of the housing facing the outer surface, and a space other than the first muffler portion and wider than the first muffler portion. The 2nd muffler part is divided and the said gas exhaust port is opening toward the said 2nd muffler part.

  According to this, in the discharge chamber, the oil storage chamber is partitioned by the end surface of the partition member and the inner surface of the storage chamber partition portion, and the first muffler portion and the second muffler portion are partitioned outside the storage chamber partition portion. Has been. That is, the oil storage chamber is a separate space isolated from the first and second muffler sections in the discharge chamber. The lubricating oil separated by the oil separator is stored in the oil storage chamber instead of the first and second muffler portions. For this reason, even if the refrigerant gas is discharged from the gas discharge port of the oil separator to the first and second muffler parts, the lubricating oil in the oil storage chamber is not wound up by the refrigerant gas, and the amount of lubricating oil accompanying the lifting is reduced. A decrease can be prevented. As a result, the lubricating oil can always be held in the oil storage chamber, and the opening on the oil storage chamber side in the oil supply passage can be sealed with the lubricating oil to prevent the refrigerant gas from entering the oil supply passage. it can.

  Further, since the lubricating oil separated by the oil separator is stored in the oil storage chamber in a space different from the first muffler portion and the second muffler portion, the lubricating oil may be stored in the first muffler portion and the second muffler portion. No. For this reason, it can prevent that the volume of the 1st muffler part and the 2nd muffler part which has a buffering action of discharge pulsation decreases by storing lubricating oil. Furthermore, the first muffler portion and the second muffler portion having different sizes coexist in the discharge chamber. Therefore, the discharge pulsation when the refrigerant gas is discharged into the discharge chamber by the first muffler portion and the second muffler portion can be effectively reduced.

  The gist of the storage chamber partition is integrally formed with the oil separator. According to this, for example, the oil separator can be made compact and the storage chamber section can be assembled to the oil separator as compared with the case where the storage chamber section is provided separately from the oil separator. The manufacturing cost of the compressor can be reduced by eliminating the work.

  Further, the oil separator is composed of a cylindrical case body in which an oil separation cylinder is accommodated and an oil separation chamber is formed, and the storage chamber partition part integrally formed on the lower side of the case body, The outer surface, which is the outer surface of the storage chamber section, has an arc shape extending along the inner peripheral surface of the housing forming the discharge chamber, and the upper end surface, which is the outer surface of the storage chamber section, has a planar shape, The case main body extends from the center of the upper end surface. According to this, the first muffler portion and the second muffler portion having different sizes can be reliably formed in the discharge chamber.

  According to the present invention, it is possible to prevent the refrigerant gas from entering the oil supply passage by eliminating the rolling-up of the lubricating oil in the oil storage chamber, and it is possible to reduce the discharge pulsation.

  Hereinafter, an embodiment in which the compressor of the present invention is embodied as a vane compressor will be described with reference to FIGS. In the following description, “front” and “rear” of the vane compressor are the directions of the arrow Y1 shown in FIG. 1, and “upper” and “lower” are the directions of the arrow Y2 shown in FIG. The vertical direction.

  As shown in FIG. 1, the housing H of the vane compressor 10 is formed of a rear housing 11 and a front housing 12 joined to a front end surface (one end surface) of the rear housing 11. A cylindrical cylinder block 13 is accommodated in the rear housing 11 (housing H). The inner peripheral surface of the cylinder block 13 is formed in an elliptical shape (see FIG. 2).

  In the housing H, a front side plate 14 is joined to the front end face (one end face) of the cylinder block 13, and a rear side plate 15 as a partition member is attached to the rear end face (other end face) of the cylinder block 13. Are joined. Between the outer peripheral surface of the cylinder block 13, the inner peripheral surface of the rear housing 11 (housing H) facing the outer peripheral surface, and the end surfaces facing the cylinder block 13 in the front side plate 14 and the rear side plate 15. The discharge space Da is partitioned. In the front side plate 14, a back pressure groove 14 a is recessed in the end surface facing the cylinder block 13, and in the rear side plate 15, a back pressure groove 15 a is recessed in the end surface facing the cylinder block 13. .

  A rotating shaft 17 is rotatably supported by the front side plate 14 and the rear side plate 15, and the rotating shaft 17 passes through the cylinder block 13. In the cylinder block 13, a cylindrical rotor 18 is fixed to the rotary shaft 17 so as to be integrally rotatable with the rotary shaft 17. As shown in FIG. 2, a plurality of vane grooves 18 a extending in the entire axial direction of the rotor 18 are formed on the outer peripheral surface of the rotor 18, and the vanes 20 are accommodated in the respective vane grooves 18 a so as to be able to appear and retract. ing. Each vane groove 18a is formed such that the front end (one end) can communicate with the back pressure groove 14a of the front side plate 14, and the rear end (other end) can be communicated with the back pressure groove 15a of the rear side plate 15. ing.

  When the tip surface of the vane 20 comes into contact with the inner peripheral surface of the cylinder block 13 due to the rotation of the rotor 18 accompanying the rotation of the rotating shaft 17, the outer peripheral surface of the rotor 18 and the inner peripheral surface of the cylinder block 13 are adjacent to the vane. A compression chamber 21 is defined between the front side plate 14 and the rear side plate 15. In the vane compressor 10, a stroke in which the compression chamber 21 increases in volume with respect to the rotation direction of the rotor 18 is a suction stroke, and a stroke in which the compression chamber 21 decreases in volume is a compression stroke. Therefore, the rear housing 11, the cylinder block 13, the front side plate 14, the rear side plate 15, the rotating shaft 17, the rotor 18, and the vane 20 constitute a compression mechanism C of the vane compressor 10.

  As shown in FIG. 1, in the vane compressor 10, a suction port 24 is formed in the upper part of the front housing 12, and a suction space Sa communicating with the suction port 24 is formed in the front housing 12. Yes. Further, the front side plate 14 is formed with a suction port 14b communicating with the suction space Sa. Further, the cylinder block 13 is formed with a suction passage 13b penetrating the cylinder block 13 in the entire axial direction. The compression chamber 21 and the suction space Sa in the suction stroke are communicated with each other through the suction port 14b and the suction passage 13b.

  As shown in FIG. 2, a notch 13 d is formed in each of the outer peripheral surfaces located at the center in the vertical direction of the cylinder block 13 and on both sides of the cylinder block 13 to be recessed from the outer peripheral surface of the cylinder block 13. Has been. Both the notches 13d are formed so as to extend over the entire axial direction of the cylinder block 13, and form a part of the discharge space Da. Further, the cylinder block 13 is formed with a discharge port 13a so as to communicate the compression chamber 21 and the discharge space Da during the compression stroke. A discharge valve 22 is attached to the outer peripheral surface of the cylinder block 13 forming the notch 13d, and the discharge port 13a can be opened and closed by the discharge valve 22. Then, the refrigerant gas compressed in the compression chamber 21 pushes out the discharge valve 22 and is discharged to the notch 13d (discharge space Da) through the discharge port 13a.

  As shown in FIG. 1, a discharge chamber 30 is defined by a rear side plate 15 on the rear side of the rear housing 11. That is, the interior of the rear housing 11 is partitioned by the rear side plate 15 into the compression mechanism C side and the discharge chamber 30 side.

  As shown in FIGS. 1 and 3, a passage forming portion 15 c that bulges toward the discharge chamber 30 is formed in the rear side plate 15. A pair of discharge passages 15b is formed in the passage forming portion 15c. Each discharge passage 15b has a groove 15f recessed in the rear end surface of the passage forming portion 15c, and a throttle portion 15g communicating with the lower end (one end) of the groove 15f and extending through the passage forming portion 15c in the thickness direction. Formed from. The throttle portion 15g has a front end (one end) that opens toward the discharge space Da and communicates with the discharge space Da, and a rear end (other end) communicates with the lower end (one end) of the groove portion 15f. Since the refrigerant gas in the discharge space Da passes through the throttle portion 15g and the groove portion 15f of the discharge passage 15b and is supplied to the discharge chamber 30, the discharge chamber 30 has a lower pressure atmosphere than the discharge space Da.

  An oil supply passage 15d is formed in the passage forming portion 15c. The oil supply passage 15 d is formed so as to extend linearly from the lower end surface of the passage forming portion 15 c toward the rotation shaft 17 and to extend toward the back pressure groove 15 a of the rear side plate 15. And the oil supply channel | path 15d has the supply port 15e opened to the lower end surface of the channel | path formation part 15c in a lower end (one end).

  As shown in FIG. 1, in the vane compressor 10, an oil separator 40 for separating the lubricating oil contained in the refrigerant gas is provided in the discharge chamber 30, and the oil separator 40 discharges in the oil separator 40. The pressure is the same as that in the chamber 30 and is lower than the discharge space Da. The oil separator 40 is bonded and fixed to the rear end face of the passage forming portion 15c via the gasket G so as to cover both the discharge passages 15b.

  As shown in FIG. 6, the oil separator 40 has a cylindrical case main body 42 integrally formed with a plate-shaped joining plate portion 41, and a storage integrally formed on the lower side of the case main body 42. A chamber partition 50 is provided. A cylindrical oil separation chamber 43 with a bottom is formed in the case main body 42, and a cylindrical oil separation cylinder 44 is fitted and fixed to the upper portion of the oil separation chamber 43 in the case main body 42. The case body 42 is formed with a pair of communication passages 42 a so as to communicate with the upper end (the other end) of each discharge passage 15 b, and the communication passage 42 a is formed so as to face the outer peripheral surface of the oil separation cylinder 44. ing. A gas discharge port 42b is formed in the upper portion of the case main body 42, and the refrigerant gas that has passed through the oil separation cylinder 44 is discharged from the case main body 42 through the gas discharge port 42b. Further, an oil discharge port 42 c for discharging the lubricating oil in the oil separation chamber 43 to the outside of the oil separator 40 is formed at the lower part of the case body 42.

  As shown in FIGS. 4 and 5, the storage chamber partition 50 has a semicircular rear end surface 50 a, and the outer surface 50 b of the outer surface of the storage chamber partition 50 forms the discharge chamber 30. The rear housing 11 is formed in an arc shape extending along the inner peripheral surface. Furthermore, the upper end surface 50c of the outer surface of the storage chamber partition 50 is flat, and the upper end surface 50c of the storage chamber partition 50 is a horizontal plane when the oil separator 40 is joined to the rear side plate 15. The case main body 42 extends upward from the center of the upper end surface 50c of the storage chamber partition 50.

  In addition, the storage chamber partition 50 is formed so that the rear end surface 50 a bulges to the rear side from the joining plate portion 41 to a position flush with the rear end of the case main body 42. As shown in FIG. 1, FIG. 5 and FIG. 6, the space inside the storage chamber partition 50 is formed in a substantially U shape so as to surround the lower portion of the case main body 42. The oil discharge port 42 c formed in the case main body 42 opens toward the space inside the storage chamber partition 50.

  As shown in FIG. 1, in the state where the oil separator 40 is joined to the end surface of the rear side plate 15 that faces the discharge chamber 30, the front end surface 50 d that faces the rear side plate 15 of the storage chamber partition 50 is formed on the rear side plate 15. Are closely in contact with the end surface of the discharge chamber 30 side. The oil storage chamber 31 is defined by a space surrounded by the end surface of the rear side plate 15 and the inner surface of the storage chamber partition 50, and the oil storage chamber 31 is independent from the discharge chamber 30 by the storage chamber partition 50. It becomes the sealed space formed. An oil discharge port 42c is opened in the oil storage chamber 31, and the oil separation chamber 43 and the oil storage chamber 31 communicate with each other through the oil discharge port 42c. Further, a supply port 15 e of the oil supply passage 15 d is opened in the oil storage chamber 31, and the oil supply passage 15 d communicates with the oil storage chamber 31. The oil storage chamber 31 and the vane groove 18a are connected via the oil supply passage 15d and the back pressure grooves 14a and 15a.

  Further, the space W1 between the rear end surface 50a of the storage chamber partition 50 and the inner end surface 11a of the rear housing 11 facing the rear end surface 50a, the outer surface 50b of the storage chamber partition 50, and the outer surface 50b. A first muffler portion 51 of the refrigerant gas is partitioned in the discharge chamber 30 by a space W2 (see FIG. 6) between the inner peripheral surface 11b of the rear housing 11 and the rear housing 11. Each of the spaces W1, W2 is a minute gap.

  On the other hand, as shown in FIG. 6, in the discharge chamber 30, there is a second muffler portion of the refrigerant gas in a space above the upper end surface 50 c of the storage chamber partition portion 50 and surrounded by the upper periphery of the case body 42. 52 is partitioned. That is, in the discharge chamber 30, the second muffler part 52 is partitioned in a space other than the first muffler part 51. The second muffler part 52 is a large space with respect to both the spaces W1 and W2 of the first muffler part 51. Note that the gas discharge port 42 b in the oil separator 40 opens toward the second muffler portion 52.

  Then, the storage chamber partition 50 is disposed in the discharge chamber 30, whereby the oil storage chamber 31 in the discharge chamber 30, and the first muffler portion 51 and the second muffler space that are separate from the oil storage chamber 31. A muffler portion 52 is partitioned.

Next, the operation of the vane compressor having the above configuration will be described.
When the rotating shaft 17 is rotated, the rotor 18 and the vane 20 are rotated, and the refrigerant gas is sucked into the compression chamber 21 during the suction stroke from the suction space Sa through the suction port 14b and the suction passage 13b. Then, the refrigerant gas sucked into the compression chamber 21 is compressed by reducing the volume of the compression chamber 21 during the compression stroke. The compressed refrigerant gas is discharged from the discharge port 13a to the discharge space Da.

  The refrigerant gas discharged into the discharge space Da is throttled by the throttle portion 15g and then flows into the groove portion 15f. The refrigerant gas flows into the communication passage 42a from the groove 15f, and is supplied to the oil separator 40 from the communication passage 42a. The refrigerant gas is blown from the communication passage 42 a to the outer peripheral surface of the oil separation cylinder 44 and guided to the lower side of the oil separation chamber 43 while turning the outer peripheral surface of the oil separation cylinder 44. At this time, the lubricating oil is separated from the refrigerant gas by centrifugal separation. Then, the lubricating oil separated from the refrigerant gas is dropped into the oil storage chamber 31 from the oil discharge port 42 c and discharged into the storage chamber section 50, and is stored in the oil storage chamber 31.

  In the oil separator 40, the refrigerant gas from which the lubricating oil has been separated moves upward in the oil separation cylinder 44 and is discharged from the gas discharge port 42 b to the second muffler portion 52 in the discharge chamber 30. At this time, the refrigerant gas is discharged to the second muffler part 52 which is a wider space than the inside of the oil separation cylinder 44 and expands in the second muffler part 52. Further, the refrigerant gas flows into the first muffler part 51 that is narrower than the second muffler part 52 and is throttled by the first muffler part 51.

According to the above embodiment, the following effects can be obtained.
(1) In the vane compressor 10 in which the oil separator 40 is provided in the discharge chamber 30, the storage chamber partition 50 is integrally formed in the oil separator 40. Then, by joining the storage chamber partition 50 to the rear side plate 15, the oil storage chamber 31 is partitioned into a space surrounded by the end surface of the rear side plate 15 and the inner surface of the storage chamber partition 50 in the discharge chamber 30. At the same time, the first muffler portion 51 and the second muffler portion 52 were partitioned outside the oil storage chamber 31 across the storage chamber partition portion 50. Therefore, the lubricating oil separated by the oil separator 40 is stored in the oil storage chamber 31 in another space isolated from the first muffler part 51 and the second muffler part 52. For this reason, when the refrigerant gas is discharged from the gas discharge port 42b of the oil separator 40 to the second muffler portion 52, the lubricating oil in the oil storage chamber 31 is not wound up by the refrigerant gas. As a result, the lubricating oil can always be held in the oil storage chamber 31, and the oil level of the lubricating oil can be kept high around the supply port 15e. For this reason, the supply port 15e can be sealed with lubricating oil to prevent the refrigerant gas from entering the oil supply passage 15d from the supply port 15e.

  (2) In a state where the oil separator 40 is provided in the discharge chamber 30, the first muffler portion 51 is partitioned by the storage chamber partition portion 50. Further, a second muffler portion 52 wider than the first muffler portion 51 is defined around the upper portion of the case main body 42 in the oil separator 40. Therefore, two muffler parts 51 and 52 having different sizes coexist in the discharge chamber 30. As a result, the first muffler unit 51 and the second muffler unit 52 can effectively reduce the discharge pulsation when the refrigerant gas is discharged into the discharge chamber 30, and can reduce abnormal noise due to the discharge pulsation. it can.

  (3) By providing the storage chamber partition 50 in the discharge chamber 30, the oil storage chamber 31 is provided in a space separate from the first muffler 51 and the second muffler 52 in the discharge chamber 30. . For this reason, it is possible to reduce the discharge pulsation by preventing the volumes of the first muffler part 51 and the second muffler part 52 having the buffering action of the discharge pulsation from decreasing due to the accumulation of the lubricating oil.

  (4) The storage chamber section 50 is integrally formed with the oil separator 40. For this reason, for example, compared with the case where the case main body 42 (oil separator 40) including the oil separation chamber 43 and the oil separation cylinder 44 and the storage chamber partition 50 are formed separately, the oil separator 40 The manufacturing cost of the vane compressor 10 can be reduced by eliminating the work of assembling the case main body 42 and the storage chamber partition 50.

  (5) The storage chamber partition 50 has a semicircular shape when viewed from the rear end surface 50a, the outer surface 50b has an arc shape, and the upper end surface 50c has a planar shape. The case main body 42 is extended upward from the central portion of the upper end surface 50 c of the storage chamber partition 50. Therefore, in a state where the storage chamber partition 50 is housed in the cylindrical rear housing 11, the first muffler 51 is partitioned outside the storage chamber partition 50 in the discharge chamber 30, and the first muffler The second muffler portion 52 can be reliably partitioned in a space other than the portion 51.

In addition, you may change the said embodiment as follows.
The storage chamber partition 50 may be formed separately from the case main body 42 of the oil separator 40, and the storage chamber partition 50 is joined to the case main body 42 and the storage chamber partition 50 is attached to the rear side plate 15. The oil storage chamber 31 may be partitioned in the discharge chamber 30 by joining.

  In order to prevent the lubricating oil from accumulating in the first muffler part 51, the oil drainage that communicates the lowermost part of the first muffler part 51 with an atmosphere (for example, the suction passage 13b) lower in pressure than the first muffler part 51. A separate passage may be provided.

  The present invention may be embodied in a scroll compressor as a compressor. In this case, the compression mechanism C is a scroll type and the partition member is formed by a fixed scroll end plate.

Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
(1) The compressor is a scroll type, The compressor according to any one of claims 1 to 3.

A longitudinal section showing a vane compressor of an embodiment. The 2-2 sectional view taken on the line of FIG. 1 which shows the inside of the vane compressor of embodiment. The figure which shows a rear side plate. The perspective view which shows an oil separator. The perspective view which shows the inner side of a storage chamber division part. FIG. 6 is a cross-sectional view taken along line 6-6 in FIG. 1 showing the inside of the oil separator.

Explanation of symbols

  C ... compression mechanism, H ... housing, 10 ... vane compressor as compressor, 11a ... inner end surface as inner surface of housing, 11b ... inner peripheral surface as inner surface of housing, 15 ... rear side plate as partition member, 15d ... Oil supply passage, 30 ... discharge chamber, 31 ... oil storage chamber, 40 ... oil separator, 42 ... case body, 42b ... gas discharge port, 42c ... oil discharge port, 43 ... oil separation chamber, 44 ... oil separation cylinder, DESCRIPTION OF SYMBOLS 50 ... Storage chamber division part, 50a ... Rear end surface as an outer surface, 50b ... Outer surface as an outer surface, 50c ... Upper end surface as an outer surface, 51 ... 1st muffler part, 52 ... 2nd muffler part.

Claims (3)

By the partition member provided in the housing, the inside of the housing is partitioned into a compression mechanism side and a discharge chamber side from which the refrigerant gas compressed by the compression mechanism is discharged, and an end surface of the partition member facing the discharge chamber In addition, an oil separator for separating the lubricating oil contained in the refrigerant gas discharged from the compression mechanism is provided, and an oil discharge port for discharging the lubricating oil separated from the refrigerant gas is formed in the oil separator. And a compressor in which a gas discharge port for the refrigerant gas is formed,
In the discharge chamber, a storage chamber partition portion is joined to an end surface of the partition member facing the discharge chamber, and an oil storage chamber for storing the lubricating oil between the end surface and the inner surface of the storage chamber partition portion. The oil discharge port communicates with the oil storage chamber, and the partition member is formed with an oil supply passage having one end communicating with the oil storage chamber and the other end communicating with the compression mechanism. And
Furthermore, a first muffler portion including a space between an outer surface of the storage chamber partition portion and an inner surface of the housing facing the outer surface is provided in the discharge chamber by the storage chamber partition portion, and the first muffler portion. And a compressor having a second muffler section that is wider than the first muffler section, and the gas discharge port is open toward the second muffler section.   The compressor according to claim 1, wherein the storage chamber section is integrally formed with the oil separator.   The oil separator includes a cylindrical case main body in which an oil separation cylinder is accommodated and an oil separation chamber is formed, and the storage chamber partition portion integrally formed on a lower side of the case main body. The outer side surface, which is the outer surface of the chamber partition portion, has an arc shape extending along the inner peripheral surface of the housing forming the discharge chamber, and the upper end surface, which is the outer surface of the storage chamber partition portion, has a planar shape, The compressor according to claim 2, wherein the case main body extends from a central portion of the compressor.

Images