JP2012036826A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor which includes a mechanism to prevent lubricating oil having dropped out of a bearing from being atomized and scattered to suppress the occurrence of oil move out.SOLUTION: A casing 10 stores lubricating oil therein. A compressor mechanism 15 compresses a refrigerant and ejects it into a high pressure space S1 within the casing. A crank shaft 17 performs a shaft rotary motion. A motor 16 drives the compressor mechanism through the crank shaft. An upper bearing 33 pivotally supports the crank shaft. A slinger 91 is disposed in the high pressure space and is fixed tightly to the outer circumferential surface of the crank shaft at the lower portion of the upper bearing. The slinger has an oil receiving part 91c on the upper face for receiving the lubricating oil having dropped downward from the upper bearing. The slinger suppresses the atomizing phenomenon in which the lubricating oil received on the oil receiving part is prevented from being atomized through a centrifugal force and scattered in the high pressure space.

Description

  The present invention relates to a compressor, and more particularly, to a compressor including a mechanism that suppresses lubricant oil falling from a bearing from being scattered in a mist form.

  In a conventional high-pressure dome type or high-low pressure dome type compressor, in order to suppress the occurrence of oil rising, which is a phenomenon in which lubricating oil inside the compressor is discharged to the outside of the compressor, An oil collecting member was provided.

  For example, in the compressor described in Patent Document 1 (Japanese Unexamined Patent Application Publication No. 2009-235948), an oil collecting member is provided on the lower surface of the housing. In this compressor, the lubricating oil dropped from the bearing is received by the upper surface of the oil collecting member and then returned to the oil storage space via the oil discharge passage provided in the housing. As a result, in this compressor, the lubricant that has fallen from the bearing adheres to the balance weight of the crankshaft and the rotor of the motor below the housing, and scatters in the form of a mist due to the centrifugal force due to the rotational movement of these shafts. It can be suppressed. Therefore, in this compressor, it is possible to suppress the occurrence of oil rising due to the lubricating oil scattered in a mist form being mixed into the compressed refrigerant and discharged to the outside of the compressor.

  However, even when an oil collecting member is provided on the lower surface of the housing, it is impossible to completely seal between the crankshaft and the oil collecting member, so that the lubricating oil leaks from the gap between the crankshaft and the oil collecting member. May be issued. Therefore, the leaked lubricating oil may adhere to the balance weight of the crankshaft or the rotor of the motor, and there may still be a problem that the lubricating oil is scattered in the form of mist by the action of the centrifugal force due to the rotational movement of these shafts.

  The subject of this invention is providing the compressor which can suppress generation | occurrence | production of oil rising by providing the mechanism which suppresses that the lubricating oil which fell from the bearing is scattered in mist form.

  A compressor according to a first aspect of the present invention includes a casing, a compression mechanism, a crankshaft, a motor, a bearing, and an annular member. The casing stores lubricating oil inside. The compression mechanism is accommodated in the casing, compresses the refrigerant, and discharges it to the high-pressure space in the casing. The crankshaft is housed in the casing and performs a shaft rotational motion. The motor is housed in the casing and drives the compression mechanism via the crankshaft. The bearing is accommodated in the casing and supports the crankshaft. The annular member is disposed in the high-pressure space, and is fixed in close contact with the outer peripheral surface of the crankshaft below the bearing. The annular member has an oil receiving portion on the upper surface for receiving the lubricating oil falling downward from the bearing. The annular member suppresses the mist phenomenon in which the lubricating oil received by the oil receiving portion is misted by centrifugal force and scattered in the high-pressure space.

  In the compressor which concerns on a 1st viewpoint, the lubricating oil which fell from the bearing is received by the oil receiving part in the upper surface of an annular member. Since the annular member is fixed in close contact with the outer peripheral surface of the crankshaft, the lubricating oil received by the oil receiving portion does not leak downward from between the crankshaft and the annular member. As a result, in the compressor according to the first aspect, the lubricating oil adheres to the balance weight of the crankshaft, the rotor of the motor, etc., and is scattered in a mist form in the high-pressure space by the action of the centrifugal force due to the rotational movement of these shafts. The mist generation phenomenon can be suppressed. When the lubricating oil is scattered in a mist form in the high-pressure space, the mist-like lubricating oil is caught in the flow of the compressed refrigerant in the high-pressure space. As a result, oil rising, which is a phenomenon in which the lubricating oil is discharged together with the compressed refrigerant to the outside of the compressor, occurs. Therefore, in the compressor which concerns on a 1st viewpoint, generation | occurrence | production of an oil rise can be suppressed by suppressing a mist formation phenomenon with an annular member.

  A compressor according to a second aspect of the present invention is the compressor according to the first aspect, further comprising a housing. The housing is fixed in the casing and supports the bearing. The annular member forms an oil storage space together with the housing and the bearing. The oil storage space is a part of the high-pressure space, and is a space below the bearing and above the annular member. The housing has an oil discharge hole that is a part of the high-pressure space and communicates the space below the annular member and the oil storage space. The annular member has a first oil guide portion. The first oil guide part guides the lubricating oil, which is received by the oil receiving part and is subjected to centrifugal force, to the oil discharge hole.

  In the compressor which concerns on a 2nd viewpoint, a centrifugal force acts on the lubricating oil received by the oil receiving part of the annular member because the annular member fixed to the crankshaft performs the shaft rotational motion. As a result, the lubricating oil moves to the outer peripheral side of the annular member and is guided to the oil discharge hole by the first oil guide portion provided in the annular member. The lubricating oil guided to the oil discharge hole is sent to the oil reservoir in which the lubricating oil below the crankshaft is stored without being scattered in the form of mist. Therefore, in the compressor according to the second aspect, the oil falling from the bearing is guided to the oil discharge hole by the first oil guide portion, thereby suppressing the occurrence of oil rise by suppressing the mist generation phenomenon. it can.

  The compressor concerning the 3rd viewpoint of the present invention is a compressor concerning the 2nd viewpoint, and a housing has the 2nd oil guide part. The second oil guide portion guides the lubricating oil received by the oil receiving portion and subjected to centrifugal force to the oil discharge hole.

  In the compressor according to the third aspect, the lubricating oil received by the oil receiving portion of the annular member is guided to the oil discharge hole by the first oil guide portion, and the oil discharge hole is provided by the second oil guide portion provided in the housing. Led to. Therefore, in the compressor according to the third aspect, the lubricating oil that has dropped from the bearing is guided to the oil discharge hole by the first oil guide portion and the second oil guide portion, thereby suppressing the mist generation phenomenon. Occurrence can be suppressed.

  The compressor concerning the 4th viewpoint of the present invention is further provided with a balance weight in the compressor concerning the 2nd viewpoint or the 3rd viewpoint. The balance weight is accommodated in the casing, is in close contact with the outer peripheral surface of the crankshaft, and is integrally formed with the annular member.

  The compressor which concerns on the 5th viewpoint of this invention is a compressor which concerns on a 1st viewpoint. WHEREIN: The oil receiving part of an annular member has an oil collecting part which can collect the received lubricating oil.

  In the compressor according to the fifth aspect, the lubricating oil received by the oil receiving portion of the annular member is collected on the upper surface of the annular member by the oil collecting portion. The lubricating oil collected by the oil collecting portion is scattered as oil droplets having a size larger than that of the mist-like oil droplets by the action of centrifugal force. Since the scattered oil droplets are large in size, they adhere to the inner wall of the casing or fall in the high-pressure space without being involved in the flow of the compressed refrigerant. Therefore, in the compressor which concerns on a 5th viewpoint, generation | occurrence | production of oil rise can be suppressed by suppressing the mist generation phenomenon by the oil collecting part of the annular member.

  In the compressor according to the sixth aspect of the present invention, in the compressor according to the fifth aspect, the oil collecting portion is a groove extending from the radially inner side to the radially outer side of the annular member.

  In the compressor according to the sixth aspect, the groove is provided on the upper surface of the annular member. The radially outer end of the groove is located on the outer periphery of the annular member. The lubricating oil collected in the groove is scattered from the radially outer end of the groove by the action of centrifugal force.

  A compressor according to a seventh aspect of the present invention is the compressor according to the sixth aspect, wherein the groove is curved in the direction opposite to the rotational direction of the annular member.

  In the compressor according to the seventh aspect, the lubricating oil collected in the groove tends to move outward in the radial direction by the action of centrifugal force. Therefore, in the compressor according to the seventh aspect, since the lubricating oil collected in the groove is more efficiently scattered from the end portion on the radially outer side of the groove, the occurrence of oil rising can be more efficiently suppressed. it can.

  A compressor according to an eighth aspect of the present invention is the compressor according to the fifth aspect, wherein the oil collecting portion is a ridge extending from the radially inner side to the radially outer side of the annular member.

  In the compressor according to the eighth aspect, the ridge is provided on the upper surface of the annular member. The ridge is a convex portion extending from the radially inner side to the radially outer side of the annular member. The radially outer end of the ridge is located on the outer periphery of the annular member. The lubricating oil received by the oil receiving portion of the annular member is collected on the side surface portion of the ridge by the action of centrifugal force, and is scattered from the end portion on the radially outer side of the ridge along the side surface portion of the ridge.

  A compressor according to a ninth aspect of the present invention is the compressor according to the eighth aspect, wherein the ridge is curved in a direction opposite to the rotational direction of the annular member.

  In the compressor according to the ninth aspect, the lubricating oil collected on the side surface portion of the ridge is likely to move outward in the radial direction by the action of centrifugal force. Therefore, in the compressor according to the ninth aspect, since the lubricating oil collected on the side surface portion of the ridge is more efficiently scattered from the end portion on the radially outer side of the ridge, the occurrence of oil rising is more efficiently suppressed. can do.

  In the compressor according to the tenth aspect of the present invention, in the compressor according to the fifth aspect, the oil collecting portion is a protrusion protruding from the radially inner side to the radially outer side of the annular member on the outer peripheral surface of the annular member. is there. The protrusion is curved in the direction opposite to the rotation direction of the annular member.

  In the compressor which concerns on a 10th viewpoint, the curved projection part is provided so that it may extend toward the radial direction outer side from the outer peripheral part of an annular member. Lubricating oil received by the oil receiving portion of the annular member tends to flow along the upper surface of the curved protruding portion by the action of centrifugal force. As a result, the lubricating oil is collected on the upper surface of the protruding portion and scattered from the radially outer end of the protruding portion by the action of centrifugal force.

  A compressor according to an eleventh aspect of the present invention is the compressor according to any one of the fifth aspect to the tenth aspect, further comprising a gas guide and a discharge pipe. The gas guide is housed in the casing and has a discharge port that guides the refrigerant compressed by the compression mechanism and discharges the refrigerant to the high-pressure space. The discharge pipe passes through the casing and opens into the high-pressure space via the opening. The annular member is disposed at a position where the lubricating oil is not scattered toward the discharge port and the opening.

  In the compressor according to the eleventh aspect, the annular member is fixed to the crankshaft at a position where the lubricating oil is not scattered toward the discharge port of the gas guide and the opening of the discharge pipe of the casing. Therefore, in the compressor according to the eleventh aspect, the scattered lubricating oil is unlikely to be caught in the flow of the compressed refrigerant, so that the occurrence of oil rising can be suppressed.

  A compressor according to a twelfth aspect of the present invention is the compressor according to the eleventh aspect, wherein the discharge port has a first discharge port that discharges the refrigerant in the vertical direction and a second discharge port that discharges the refrigerant in the circumferential direction of the casing. It consists of an exit. The lubricating oil is scattered from the annular member in the same direction as the direction in which the refrigerant discharged from the second discharge port flows.

  In the compressor according to the twelfth aspect, the relative speed of the lubricating oil scattered from the annular member with respect to the compressed refrigerant discharged from the gas guide in the casing circumferential direction is smaller than the absolute speed of the lubricating oil. Therefore, in the compressor according to the twelfth aspect, the scattered lubricating oil is unlikely to be caught in the flow of the compressed refrigerant, so that the occurrence of oil rising can be suppressed.

  The compressor which concerns on this invention can suppress generation | occurrence | production of oil rising by providing the mechanism which suppresses that the lubricating oil which fell from the bearing is scattered in mist form.

It is a longitudinal section of the scroll compressor concerning a 1st embodiment of the present invention. It is a detailed longitudinal cross-sectional view of the vicinity of the slinger of the scroll compressor which concerns on 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the scroll compressor which concerns on the modification 1A of 1st Embodiment of this invention. It is a detailed longitudinal cross-sectional view of the vicinity of the slinger of the scroll compressor which concerns on the modification 1B of 1st Embodiment of this invention. It is a detailed longitudinal cross-sectional view of the vicinity of the slinger of the scroll compressor which concerns on the modification 1C of 1st Embodiment of this invention. It is a detailed longitudinal cross-sectional view of the vicinity of the slinger of the scroll compressor which concerns on modification 1D of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the scroll compressor which concerns on 2nd Embodiment of this invention. It is a perspective view of the slinger which concerns on 2nd Embodiment of this invention. It is a figure showing the positional relationship of a slinger and a gas guide at the time of planarly viewing the scroll compressor concerning a 2nd embodiment of the present invention. It is a figure at the time of seeing the gas guide of the scroll compressor which concerns on 2nd Embodiment of this invention toward the radial direction outer side of a casing from the center of a casing. It is a perspective view of the slinger which concerns on the modification 2A of 2nd Embodiment of this invention. It is a perspective view of the slinger which concerns on 3rd Embodiment of this invention. It is a perspective view of the slinger which concerns on the modification 3A of 3rd Embodiment of this invention. It is a top view of the slinger which concerns on 4th Embodiment of this invention. It is a top view of the slinger which concerns on the modification 4B of 4th Embodiment of this invention.

<First Embodiment>
A compressor according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 6.

  The compressor in the present embodiment is a high and low pressure dome type scroll compressor. The scroll compressor is a compressor that compresses refrigerant by revolving at least one scroll of two scrolls meshing with each other without revolving with respect to the other scroll.

(1) Overall Configuration FIG. 1 shows a longitudinal sectional view of a scroll compressor 101 according to this embodiment. The scroll compressor 101 plays a role of compressing refrigerant gas in a refrigerant circuit that repeats a refrigeration cycle in which refrigerant is circulated.

  As shown in FIG. 1, the scroll compressor 101 according to this embodiment includes a casing 10, a compression mechanism 15, a housing 23, an upper bearing 33, an Oldham joint 39, a motor 16, a lower bearing 60, an oil separation plate 73, a crank The shaft 17, the slinger 91, the gas guide 58, the suction pipe 19 and the discharge pipe 20 are configured. Hereinafter, the components of the scroll compressor 101 will be described in detail.

(2) Detailed configuration (2-1) Casing The casing 10 includes a substantially cylindrical body casing part 11, and a bowl-shaped upper wall part 12 welded in an airtight manner to the upper end part of the body casing part 11, It is comprised from the lower end part of the trunk | drum casing part 11 with the bowl-shaped bottom wall part 13 welded airtightly. The casing 10 is formed of a rigid member that is unlikely to be deformed or damaged when pressure and temperature change inside and outside the casing 10. Moreover, the casing 10 is installed so that the substantially cylindrical axial direction of the trunk | drum casing part 11 may follow a perpendicular direction.

  Inside the casing 10, a compression mechanism 15, a housing 23 disposed below the compression mechanism 15, a motor 16 disposed below the housing 23, and the casing 10 are disposed so as to extend in the vertical direction. A crankshaft 17 and the like are accommodated. A suction pipe 19 and a discharge pipe 20 are welded to the wall of the casing 10 in an airtight manner.

  An oil storage portion P that is a space for storing lubricating oil is formed at the bottom of the casing 10. Lubricating oil is used to keep the lubricity of sliding parts such as the compression mechanism 15 good during the operation of the scroll compressor 101.

(2-2) Compression mechanism The compression mechanism 15 is accommodated in the casing 10, sucks and compresses low-temperature and low-pressure refrigerant gas, and discharges high-temperature and high-pressure refrigerant gas (hereinafter referred to as "compressed refrigerant"). The compression mechanism 15 includes a fixed scroll 24 and a turning scroll 26. Next, the fixed scroll 24 and the orbiting scroll 26 will be described respectively.

  The fixed scroll 24 has a first end plate 24a and a spiral (involute) first wrap 24b formed upright on the first end plate 24a. The fixed scroll 24 is formed with a main suction hole (not shown) and an auxiliary suction hole (not shown) adjacent to the main suction hole. The main suction hole communicates the suction pipe 19 and a compression chamber 40 described later. The auxiliary suction hole communicates a low-pressure space S2 described later and the compression chamber 40. A discharge hole 41 is formed at the center of the first end plate 24a, and an enlarged recess 42 communicating with the discharge hole 41 is formed at the upper surface of the first end plate 24a. The enlarged recess 42 is a space that is recessed in the upper surface of the first end plate 24a and extends in the horizontal direction. A lid 44 is fastened and fixed to the upper surface of the fixed scroll 24 by bolts 44 a so as to close the enlarged concave portion 42. And the muffler space 45 which consists of an expansion chamber which silences the driving | running sound of the compression mechanism 15 by covering the expansion recessed part 42 with the cover body 44 is formed. The fixed scroll 24 and the lid 44 are sealed by being brought into close contact with each other via a gasket (not shown). The fixed scroll 24 is formed with a first communication passage 46 that communicates with the muffler space 45 and opens on the lower surface of the fixed scroll 24.

  The orbiting scroll 26 has a second end plate 26a and a spiral (involute) second wrap 26b formed upright on the second end plate 26a. An upper end bearing 26c is formed at the center of the lower surface of the second end plate 26a. Oil supply pores 63 are formed in the second end plate 26a. The oil supply pore 63 communicates the outer peripheral portion of the upper surface of the second end plate 26a and the space inside the upper end bearing 26c.

  The fixed scroll 24 and the orbiting scroll 26 are spaces surrounded by the first end plate 24a, the first wrap 24b, the second end plate 26a, and the second wrap 26b when the first wrap 24b and the second wrap 26b are engaged with each other. A compression chamber 40 is formed. As will be described later, the compression chamber 40 compresses the refrigerant by reducing its volume by the revolving motion of the orbiting scroll 26.

(2-3) Housing The housing 23 is disposed below the compression mechanism 15 and is joined to the inner wall of the casing 10 in an airtight manner on the outer peripheral surface thereof. For this reason, the inside of the casing 10 is defined by a high-pressure space S <b> 1 below the housing 23 and a low-pressure section S <b> 2 above the housing 23. The housing 23 mounts the fixed scroll 24 by being fixed with a bolt or the like, and sandwiches the orbiting scroll 26 together with the fixed scroll 24 via an Oldham joint 39 described later. Further, a second communication passage 48 is formed through the outer peripheral portion of the housing 23 in the vertical direction. The second communication passage 48 communicates with the first communication passage 46 on the upper surface of the housing 23, and communicates with the high-pressure space S <b> 1 through the discharge port 49 on the lower surface of the housing 23.

  Further, the housing 23 has a housing through hole 31 provided so as to penetrate in a vertical direction from the center of the upper surface of the housing 23 to the center of the lower surface. Inside the housing through hole 31, the upper bearing 33 is fixed in close contact with the inner peripheral surface of the housing through hole 31. In the space in the housing through hole 31 above the upper bearing 33, an upper end bearing 26c of the orbiting scroll 26 is disposed. A slinger 91 described later is disposed below the upper bearing 33. Hereinafter, the space in the housing through hole 31 located below the upper bearing 33 and above the slinger 91 is referred to as an oil storage space S3. The housing 23 is provided with an oil discharge hole 92 that allows the oil storage space S3 and the high-pressure space S1 to communicate with each other via the second communication passage 48.

(2-4) Upper Bearing The upper bearing 33 is a rolling bearing having an inner ring 33a, a plurality of rolling elements 33b, and an outer ring 33c. The inner ring 33a is fixed in close contact with an outer peripheral surface of a crankshaft 17 described later. The outer ring 33 c is fixed in close contact with the inner peripheral surface of the housing through hole 31. The rolling element 33b is fitted between the inner ring 33a and the outer ring 33c so as to roll freely. The rolling element 33b is, for example, a sphere or a roller. The upper bearing 33 rotatably supports the crankshaft 17.

(2-5) Oldham Joint The Oldham Joint 39 is an annular member for preventing the orbiting scroll 26 from rotating. The Oldham coupling 39 is fitted into an oblong Oldham groove 26 d formed in the housing 23.

(2-6) Motor The motor 16 is a brushless DC motor housed in the casing 10 and disposed below the housing 23. The motor 16 includes a stator 51 fixed to the inner wall of the casing 10 and a rotor 52 that is rotatably accommodated with a slight gap (air gap) provided inside the stator 51.

  The stator 51 has a coil part (not shown) around which a conducting wire is wound, and a coil end 53 formed above and below the coil part. Further, the outer peripheral surface of the stator 51 is provided with a plurality of core cut portions (not shown) that are notched from the upper end surface to the lower end surface of the stator 51 and at a predetermined interval in the circumferential direction. ing. The core cut portion forms a motor cooling passage 55 extending in the vertical direction between the body casing portion 11 and the stator 51.

  The rotor 52 is connected to the crankshaft 17 that passes through the center of rotation in the vertical direction. The rotor 52 is connected to the compression mechanism 15 via the crankshaft 17.

(2-7) Lower Bearing The lower bearing 60 is disposed below the motor 16 and is joined to the inner wall of the casing 10 in an airtight manner on the outer peripheral surface thereof. The lower bearing 60 supports a crankshaft 17 described later.

(2-8) Oil Separation Plate The oil separation plate 73 is a flat member housed inside the casing 10. The oil separation plate 73 is fixed to the upper end surface of the lower bearing 60.

(2-9) Crankshaft The crankshaft 17 is housed inside the casing 10 and is disposed such that its axial direction is along the vertical direction. As shown in FIG. 1, the crankshaft 17 has a shape in which the shaft center of the upper end portion thereof is slightly eccentric with respect to the shaft center of the portion excluding the upper end portion. A slinger 91, which will be described later, is fixed to the crankshaft on the outer peripheral surface located below the upper bearing 33 and above the motor 16. Further, the balance weight 18 is fixed to the crankshaft on the outer peripheral surface located below the slinger 91 and above the motor 16.

  The crankshaft 17 passes through the rotation center of the rotor 52 in the vertical direction and is connected to the rotor 52. The crankshaft 17 passes through the inner ring 33 a of the upper bearing 33 and is connected to the upper bearing 33. The crankshaft 17 rotates in a counterclockwise direction when viewed from above, and its outer peripheral surface slides with the upper end bearing 26 c and the lower bearing 60. The crankshaft 17 is connected to the orbiting scroll 26 by fitting the upper end portion of the crankshaft 17 into the upper end bearing 26c. The crankshaft 17 rotates the shaft to drive the orbiting scroll 26.

  The crankshaft 17 has an oil supply passage 61 extending in the axial direction. The upper end of the oil supply passage 61 communicates with an oil chamber 83 formed by the upper end surface of the crankshaft 17 and the lower surface of the second end plate 26a. The oil chamber 83 communicates with a sliding portion (hereinafter referred to as a “sliding portion of the compression mechanism 15”) between the fixed scroll 24 and the orbiting scroll 26 via an oil supply hole 63 of the second end plate 26a. It finally communicates with the low-pressure space S2 through the chamber 40. Further, the lower end of the oil supply passage 61 communicates with the oil storage portion P of the high-pressure space S1.

  Further, the crankshaft 17 has a first oil supply horizontal hole 61 a and a second oil supply horizontal hole 61 b branched from the oil supply passage 61. The first oil supply horizontal hole 61 a and the second oil supply horizontal hole 61 b are formed orthogonal to the oil supply path 61. The first oil supply lateral hole 61a opens in the outer peripheral surface of the crankshaft 17 that slides with the upper end bearing 26c. The second oil supply lateral hole 61 b opens in the outer peripheral surface of the crankshaft 17 that slides with the lower bearing 60.

(2-10) Slinger The slinger 91 is an annular member fixed in close contact with the outer peripheral surface of the crankshaft 17. As shown in FIG. 2, the slinger 91 has a shaft support portion 91a on its inner peripheral portion, a first oil guide portion 91b on its outer peripheral portion, and a link between the shaft support portion 91a and the first oil guide portion 91b. An oil receiving portion 91c is provided between them. The shaft support portion 91 a is fixed such that its radially inner side surface is in close contact with the outer peripheral surface of the crankshaft 17. The first oil guide portion 91b is inclined so that the upper surface thereof is positioned upward from the radially inner side of the slinger 91 toward the radially outer side. As shown in FIG. 2, the upper end of the outer peripheral surface of the first oil guide portion 91 b is located in the vicinity of the lower end of the oil discharge hole 92. Further, a gap 31 a is formed between the outer peripheral surface of the first oil guide portion 91 b and the inner peripheral surface of the housing through hole 31. Since the crankshaft 17 rotates in the counterclockwise direction when viewed from above, the slinger 91 in close contact with the crankshaft 17 also rotates in the counterclockwise direction as viewed from above.

(2-11) Gas Guide The gas guide 58 is a member for guiding the compressed refrigerant discharged from the discharge port 49 on the lower surface of the housing 23 to the high-pressure space S1. The gas guide 58 is fixed to the trunk casing 11 and forms a space for guiding the refrigerant to the high-pressure space S1 together with the inner peripheral surface of the trunk casing 11.

(2-12) Suction Pipe The suction pipe 19 is a tubular member for introducing the refrigerant of the refrigerant circuit from the outside of the casing 10 to the compression mechanism 15. The suction pipe 19 is fitted into the upper wall portion 12 of the casing 10 in an airtight manner. The suction pipe 19 penetrates the low pressure space S <b> 2 in the vertical direction, and an inner end portion is fitted in the fixed scroll 24.

(2-13) Discharge pipe The discharge pipe 20 is a tubular member for discharging the compressed refrigerant from the high-pressure space S1 to the outside of the casing 10. The discharge pipe 20 is fitted in the body casing part 11 of the casing 10 in an airtight manner. The discharge pipe 20 penetrates the high-pressure space S <b> 1 in the horizontal direction, and an opening 20 a in the casing 10 is located in the vicinity of the housing 23.

(3) Operation The operation of the scroll compressor 101 in this embodiment will be described. Initially, the flow of the refrigerant | coolant which circulates through a refrigerant circuit provided with the scroll compressor 101 is demonstrated. Next, the flow of the lubricating oil in the scroll compressor 101 will be described.

(3-1) Flow of refrigerant First, the rotor 52 is rotated by driving the motor 16. As a result, the crankshaft 17 fixed to the rotor 52 performs shaft rotation motion. The rotational movement of the crankshaft 17 is transmitted to the orbiting scroll 26 via the upper end bearing 26c. The axis of the upper end portion of the crankshaft 17 is eccentric with respect to the axis of the rotational movement of the crankshaft 17, and the orbiting scroll 26 is prevented from rotating by the Oldham joint 39. Thereby, the orbiting scroll 26 performs a revolving motion.

  The low-temperature and low-pressure refrigerant before compression is sucked into the compression chamber 40 of the compression mechanism 15 from the suction pipe 19 via the main suction hole or from the low-pressure space S2 via the auxiliary suction hole. Due to the orbiting motion of the orbiting scroll 26, the compression chamber 40 moves from the outer peripheral portion of the fixed scroll 24 toward the center portion while gradually decreasing the volume. As a result, the refrigerant in the compression chamber 40 is compressed into a compressed refrigerant. The compressed refrigerant is discharged from the discharge hole 41 to the muffler space 45, and then introduced from the discharge port 49 to the high-pressure space S1 via the first communication passage 46 and the second communication passage 48. Then, the compressed refrigerant flows downward in the space between the gas guide 58 and the body casing portion 11. The compressed refrigerant descends the motor cooling passage 55 and reaches the space below the motor 16. Thereafter, the compressed refrigerant reverses the flow direction, and the other motor cooling passage 55 and the air gap rise. Finally, the compressed refrigerant is discharged from the discharge pipe 20 to the outside of the scroll compressor 101.

(3-2) Flow of lubricating oil First, the rotor 52 is rotated by driving the motor 16. As a result, the crankshaft 17 fixed to the rotor 52 performs shaft rotation motion. When the compression mechanism 15 is driven by the rotational movement of the crankshaft 17 and the compressed refrigerant is discharged into the high-pressure space S1, the pressure in the high-pressure space S1 rises. Further, the upper end of the oil supply passage 61 communicates with the low pressure space S <b> 2 through the oil chamber 83 and the oil supply hole 63. As a result, a pressure difference is generated between the upper end and the lower end of the oil supply passage 61. As a result, the oil supply passage 61 itself acts as a differential pressure pump, so that the lubricating oil stored in the oil storage portion P is sucked and ascends the oil supply passage 61.

  The lubricating oil that has moved up the oil supply passage 61 and reached the oil chamber 83 is supplied to the sliding portion of the compression mechanism 15 through the oil supply holes 63. The lubricating oil that has slid along the sliding portion of the compression mechanism 15 leaks into the low pressure space S2 and the compression chamber 40. At this time, the lubricating oil that is originally high temperature and pressure superheats the refrigerant before compression existing in the low pressure space S2 and the compression chamber 40. Lubricating oil is contained in the compressed refrigerant in the form of oil droplets. The lubricating oil contained in the compressed refrigerant is discharged from the compression chamber 40 to the high-pressure space S1 through the same path as the compressed refrigerant. Thereafter, a part of the lubricating oil collides with the oil separation plate 73 after descending the motor cooling passage 55 together with the compressed refrigerant. At this time, the lubricating oil adhering to the oil separation plate 73 falls in the high pressure space S1 and is stored in the oil storage portion P.

  On the other hand, most of the lubricating oil rising in the oil supply passage 61 is supplied to the first oil supply horizontal hole 61a and the second oil supply horizontal hole 61b. The lubricating oil flowing through the first oil supply lateral hole 61a and a part of the lubricating oil in the oil chamber 83 are supplied to the upper bearing 33 after lubricating the sliding portion between the crankshaft 17 and the upper end bearing 26c. The lubricating oil dropped from the upper bearing 33 to the oil storage space S3 is received by the upper surface of the oil receiving portion 91c of the slinger 91. Since the slinger 91 performs shaft rotational movement together with the crankshaft 17, a centrifugal force directed radially outward of the casing 10 acts on the lubricating oil received by the oil receiving portion 91c as shown in FIG. The lubricant oil moves upward in the radial direction by the action of centrifugal force, and then moves upward and radially outward through the upper surface of the first oil guide portion 91b. Most of the lubricating oil that has reached the outer peripheral portion of the first oil guide portion 91b is sent to the oil discharge hole 92, and a part thereof is supplied to the gap 31a. The lubricating oil sent to the oil discharge hole 92 is sent to the high-pressure space S1 via the second communication passage 48 and falls to the oil storage part P. On the other hand, the lubricating oil supplied to the gap 31a leaks from the lower end of the gap 31a to the high-pressure space S1 while being transmitted along the outer periphery of the first oil guide portion 91b. At this time, the lubricating oil leaked into the high-pressure space S1 is scattered from the outer peripheral portion of the first oil guide portion 91b toward the outer side in the circumferential direction of the casing 10 by the action of centrifugal force.

  Further, the lubricating oil flowing through the second oil supply lateral hole 61b lubricates the sliding portion between the crankshaft 17 and the lower bearing 60 and leaks into the high-pressure space S1, and then falls in the high-pressure space S1 to the oil storage portion P. .

(4) Features (4-1)
In the present embodiment, the lubricating oil dropped from the upper bearing 33 is received on the upper surface of the oil receiving portion 91c of the slinger 91, and then sent to the oil discharge hole 92 by the action of centrifugal force and scattered in a mist form. Without being sent to the high-pressure space S1. Thereby, in this embodiment, the lubricating oil that has dropped from the upper bearing 33 falls in the high-pressure space S1, adheres to the crankshaft 17 and the balance weight 18, and suppresses a mist phenomenon that is scattered in a mist form. Can do. Here, when the lubricating oil is scattered in a mist shape in the high-pressure space S1, the lubricating oil is caught in the flow of the compressed refrigerant in the high-pressure space S1. As a result, the oil rising, which is a phenomenon in which the compressed refrigerant mixed with the lubricating oil is discharged from the discharge pipe 20 to the outside of the scroll compressor 101 occurs, the seizure of the sliding portion of the compression mechanism 15 and the scroll compressor 101 occur. Problems such as abnormal internal temperature rise occur. Therefore, in this embodiment, the occurrence of oil rising can be suppressed by suppressing the mist generation phenomenon by the slinger 91.

(4-2)
In the present embodiment, most of the lubricating oil dropped from the upper bearing 33 is sent to the oil discharge hole 92, and a part is sent to the gap 31a. The lubricating oil supplied to the gap 31a leaks into the high-pressure space S1 while being transmitted along the outer periphery of the first oil guide portion 91b. That is, the lubricating oil that has leaked from the gap 31a into the high-pressure space S1 adheres to the outer peripheral portion of the first oil guide portion 91b. The lubricating oil is scattered toward the outside in the radial direction of the casing 10 by the axial rotation of the slinger 91. Therefore, in the present embodiment, it is possible to suppress the mist phenomenon due to the lubricating oil leaking into the high-pressure space S1 from the gap 31a adhering to the balance weight 18.

(4-3)
In the present embodiment, the gap 31 a is located on the radially outer side of the casing 10 with respect to the outer edge portion of the balance weight 18. Accordingly, even if the lubricating oil leaked from the gap 31a into the high pressure space S1 falls in the high pressure space S1, the lubricating oil is difficult to adhere to the balance weight 18. Therefore, in the present embodiment, it is possible to suppress the mist phenomenon due to the lubricating oil leaking into the high-pressure space S1 from the gap 31a adhering to the balance weight 18.

(5) Modification (5-1) Modification 1A
In the present embodiment, the slinger 91 is fixed in close contact with the outer peripheral surface of the crankshaft 17 in the space above the balance weight 18, but the slinger 91 is connected to the balance weight 18 as shown in FIG. It may be integrally molded and fixed in close contact with the outer peripheral surface of the crankshaft 17.

(5-2) Modification 1B
In the present embodiment, the slinger 91 has the first oil guide portion 91 b for guiding the lubricating oil to the oil discharge hole 92, but the housing 23 also has a second oil guide for guiding the lubricating oil to the oil discharge hole 92. You may have an oil guide part. FIG. 4 shows a longitudinal sectional view of the housing 23 having the second oil guide portion 23a. The second oil guide portion 23 a is a member that is closely fixed to the inner peripheral surface of the housing through hole 31. The upper surface of the second oil guide portion 23a is inclined downward from the radially inner side of the casing 10 toward the radially outer side. The outer peripheral surface of the first oil guide portion 91b of the slinger 91 forms a gap 31b together with the inner peripheral surface of the second oil guide portion 23a.

  In this modification, the lubricating oil that has moved to the outer peripheral portion of the first oil guide portion 91b by the action of centrifugal force is received by the upper surface of the second oil guide portion 23a and guided to the oil discharge hole 92. Therefore, in this modification, the second oil guide portion 23a provided on the inner peripheral surface of the housing through hole 31 receives the lubricating oil from the first oil guide portion 91b, so that the lubricating oil is efficiently supplied to the oil discharge hole 92. And the return of the lubricating oil from the oil discharge hole 92 to the oil receiving portion 91c of the slinger 91 can be suppressed.

(5-3) Modification 1C
In the present embodiment, the slinger 91 forms a gap 31 a having a non-contact seal function with the housing 23, but the slinger 91 has another type of non-contact seal with the housing 23. A space having the above function may be formed.

  For example, as shown in FIG. 5, the slinger 91 may form a vertical labyrinth seal 131 a with the housing 23. In the present modification, the lubricating oil in the oil storage space S3 is stored in the labyrinth space formed between the slinger 91 and the housing 23. Therefore, in this modification, since the labyrinth seal 131a can realize higher sealing performance than the gap 31a of the present embodiment, it is more effectively suppressed that the lubricating oil leaks from the oil storage space S3 to the high-pressure space S1. can do.

(5-4) Modification 1D
In the present embodiment, the first oil guide portion 91 b guides the lubricating oil to the oil discharge hole 92, but the lubricating oil received by the oil receiving portion 91 b may be scattered near the lower surface of the housing 23. FIG. 6 shows a detailed longitudinal sectional view in the vicinity of the slinger 91 in this modification. In this modified example, as shown in FIG. 6, the housing 23 may not have the oil discharge hole 92.

  In the present modification, the slinger 91 is fixed to the crankshaft 17 so that the outer peripheral end of the first oil guide portion 91 b is positioned below the lower surface of the housing 23. In this modification, the lubricating oil dropped from the upper bearing 33 is received by the oil receiving portion 91c, and then scattered in the high-pressure space S1 from the outer peripheral portion of the first oil guide portion 91b toward the radially outer side of the casing 10. Is done. As a result, the mist phenomenon due to the lubricant adhering to the balance weight 18 can be suppressed.

(5-5) Modification 1E
In the present embodiment, the scroll compressor 101 includes the compression mechanism 15 including the fixed scroll component 24 and the orbiting scroll component 26, but may be a compression mechanism that is driven by the rotational movement of the crankshaft 17. For example, another type of compression mechanism may be provided. For example, a rotary type compression mechanism or a screw type compression mechanism may be provided.

Second Embodiment
A compressor according to a second embodiment of the present invention will be described with reference to FIGS. Since the basic configuration, operation, and features of the present embodiment are the same as those of the compressor according to the first embodiment, only differences from the first embodiment will be described.

(1) Configuration FIG. 7 shows a longitudinal sectional view of the scroll compressor 201 according to this embodiment. In this embodiment, the housing 123 does not have the oil discharge hole 92 provided in the housing 23 in the first embodiment. Further, in the present embodiment, the slinger 191 does not have the shaft support portion 91a and the first oil guide portion 91b provided in the slinger 91 in the first embodiment, and four on the upper surface where the oil receiving portion 91c is provided. Groove 91c1. As shown in FIG. 8, these four grooves 91 c 1 are formed at positions having a four-fold rotational symmetry with respect to the rotation axis of the crankshaft 17. The groove 91c1 extends while curving in a direction opposite to the rotation direction of the crankshaft 17 from the radially inner side of the slinger 191 to the radially outer side. In the present embodiment, the slinger 191 is fixed to the outer peripheral surface of the crankshaft 17 such that the slinger 191 is positioned below the lower surface of the housing 123 and the upper surface thereof is positioned above the opening 20a of the discharge pipe 20. Yes. As shown in FIG. 9, the slinger 191 performs an axial rotation motion counterclockwise as viewed from above.

  In the present embodiment, as shown in FIGS. 9 and 10, the gas guide 58 has a first discharge port 58 a for discharging the refrigerant downward in the vertical direction and a refrigerant for discharging the refrigerant in the circumferential direction of the casing 10. A second discharge port 58b is provided. FIG. 9 is a diagram illustrating the positional relationship between the slinger 191 and the gas guide 58 when viewed from above in the vertical direction. FIG. 10 is a diagram illustrating the shape of the gas guide 58 when the gas guide 58 is viewed from the center of the casing 10 toward the radially outer side of the casing 10.

(2) Operation In this embodiment, the lubricating oil dropped from the upper bearing 33 is collected by the groove 91c1 after being received by the oil receiving portion 91c of the slinger 191. The lubricating oil collected in the groove 91c1 moves from the radially inner side to the radially outer side of the slinger 191 by the action of the centrifugal force due to the rotational movement of the crankshaft 17. The lubricating oil that has moved to the outer edge of the slinger 191 that is the radially outer end of the groove 91c1 is scattered as oil droplets in the high-pressure space S1. As shown in FIG. 9, the oil droplets of the lubricating oil are scattered toward the inner peripheral surface of the body casing portion 11 along the tangential direction of the groove 91 c 1 at the outer edge portion of the slinger 191.

(3) Features (3-1)
In the present embodiment, the lubricating oil dropped from the upper bearing 33 and received by the oil receiving portion 91c is collected in the groove 91c1 and then scattered from the slinger 191. Therefore, the oil droplets of the scattered lubricating oil are mist-like. Larger than the oil droplets. Therefore, in this embodiment, the mist phenomenon can be suppressed.

(3-2)
In this embodiment, since the groove 91c1 is curved in the direction opposite to the rotation direction of the slinger 191, the lubricating oil collected in the groove 91c1 is likely to move radially outward along the groove 91c1. As a result, since the lubricating oil collected in the groove 91c1 is likely to be scattered from the slinger 191, the lubricating oil overflows from the groove 91c1, and becomes a mist-like oil droplet from the upper surface other than the groove 91c1 of the slinger 191. It is possible to suppress scattering inside.

(3-3)
In the present embodiment, the lubricating oil scattered from the slinger 191 is scattered toward a space above the opening 20 a of the discharge pipe 20. As a result, it is possible to prevent the lubricating oil scattered from the slinger 191 from entering the discharge pipe 20 through the opening 20a, being mixed into the compressed refrigerant, and being discharged to the outside of the scroll compressor 201.

  In the present embodiment, the lubricating oil scattered from the slinger 191 is scattered in a space above the second discharge port 58 b of the gas guide 58. Thereby, it can suppress that the lubricating oil splashed from the slinger 191 is caught in the flow of the compression refrigerant | coolant discharged from the 2nd discharge port 58b, and becomes a mist-like oil droplet.

(3-4)
In this embodiment, as shown in FIG. 9, the lubricating oil is scattered toward the inner peripheral surface of the trunk casing portion 11 along the tangential direction of the groove 91 c 1 at the outer edge portion of the slinger 191. At this time, since the lubricating oil is scattered in the direction opposite to the axial rotation direction of the crankshaft 17, the absolute speed of the lubricating oil scattered from the slinger 191 is reduced. And the smaller the absolute velocity of the scattered lubricating oil is, the less the lubricating oil is caught in the refrigerant flow in the high-pressure space S1 and becomes a mist-like oil droplet. Therefore, in this embodiment, it can suppress that lubricating oil becomes a mist-like oil droplet.

(3-5)
In the present embodiment, the lubricating oil scattered from the slinger 191 is scattered in the same direction as the flow direction of the refrigerant discharged from the second discharge port 58b of the gas guide 58, as shown in FIG. Here, considering the case where the lubricating oil scattered from the slinger 191 falls in the high-pressure space S1 to the second discharge port 58b, the relative speed of the lubricating oil to the compressed refrigerant discharged from the second discharge port 58b is: Smaller than the absolute speed of the lubricant. And, as the relative speed of the lubricating oil with respect to the compressed refrigerant is smaller, the lubricating oil is less likely to be mist-like oil droplets by being caught in the refrigerant flow in the high-pressure space S1. Therefore, in this embodiment, it can suppress that lubricating oil becomes a mist-like oil droplet.

(4) Modification (4-1) Modification 2A
In this embodiment, the slinger 191 has the groove 91c1 extending while being curved, but as shown in FIG. 11, the slinger 191 has four grooves 191c1 extending linearly along the radial direction. You may do it.

(4-2) Modification 2B
In the present embodiment, the slinger 191 has four grooves 91c1, but may have other number of grooves 91c1, such as six grooves 91c1, for example. As the number of grooves 91c1 formed in the slinger 191 increases, the lubricating oil is easily collected in the grooves 91c1. Therefore, the lubricating oil is collected more efficiently and scattered from the slinger 191.

  In Modification 2A, the slinger 191 has four grooves 191c1 extending linearly along the radial direction, but has another number of grooves 191c1, such as six grooves 191c1. It may be.

<Third Embodiment>
A compressor according to a third embodiment of the present invention will be described with reference to FIGS. Since the basic configuration, operation, and features of this embodiment are the same as those of the compressor according to the second embodiment, only differences from the second embodiment will be described.

(1) Configuration In this embodiment, the slinger 291 does not have the four grooves 91c1 provided in the slinger 191 of the second embodiment in the oil receiving portion 91c, and has four ridges 91c2. is doing. As shown in FIG. 12, these four ridges 91 c 2 are formed at positions having a 4-fold rotational symmetry with respect to the rotation axis of the crankshaft 17. The ridge 91c2 is a convex portion extending while curving in a direction opposite to the rotation direction of the crankshaft 17 from the radially inner side of the slinger 291 to the radially outer side.

(2) Operation In this embodiment, the lubricating oil dropped from the upper bearing 33 is received by the oil receiving portion 91c of the slinger 291 and then the side surface of the ridge 91c2 by the action of the centrifugal force due to the axial rotation of the crankshaft 17 And move outward in the radial direction of the slinger 291. The lubricating oil that has moved to the outer edge of the slinger 291 that is the radially outer end of the ridge 91c2 is scattered as oil droplets in the high-pressure space S1 toward the inner peripheral surface of the trunk casing 11. Note that the oil droplets of the lubricating oil are scattered toward the inner peripheral surface of the trunk casing portion 11 along the tangential direction of the ridge 91c2 at the outer edge portion of the slinger 291 as in the second embodiment.

(3) Features In the present embodiment, the lubricating oil that has fallen from the upper bearing 33 and received by the oil receiving portion 91c moves along the side surface of the ridge 91c2 while moving radially outward of the slinger 291. Since the oil is collected by the side surfaces, the oil droplets of the lubricating oil scattered from the slinger 291 are larger than the mist-like oil droplets. Therefore, in this embodiment, the mist phenomenon can be suppressed.

(4) Modification (4-1) Modification 3A
In this embodiment, the slinger 291 has a ridge 91c2 that extends while curving, but has a ridge 191c2 that extends linearly along the radial direction, as shown in FIG. Also good.

(4-2) Modification 3B
In the present embodiment, the slinger 291 has four ridges 91c2, but may have another number of ridges 91c2, such as six ridges 91c2. As the number of ridges 91c2 formed on the slinger 291 increases, the lubricating oil is easily collected on the side surface of the ridge 91c2. Therefore, the lubricating oil is collected more efficiently and scattered from the slinger 291.

  In Modification 3A, the slinger 291 has four ridges 191c2 extending linearly along the radial direction, but has other numbers of ridges 191c2, such as six ridges 191c2. It may be.

<Fourth embodiment>
A compressor according to a fourth embodiment of the present invention will be described with reference to FIGS. 14 and 15. Since the basic configuration, operation, and features of this embodiment are the same as those of the compressor according to the second embodiment, only differences from the second embodiment will be described.

(1) Configuration In the present embodiment, the slinger 391 has six protruding portions 91c3 formed outside the oil receiving portion 91c. As shown in FIG. 14, the six protrusions 91 c 3 are formed at positions having a 6-fold rotational symmetry with respect to the rotation axis of the crankshaft 17. The protruding portion 91c3 is a plate-like member that extends from the outer edge portion of the oil receiving portion 91c while curving in the direction opposite to the rotation direction of the slinger 391 from the radially inner side to the radially outer side of the slinger 391. The upper surface of the protrusion 91c3 is smoothly joined to the upper surface of the oil receiver 91c.

(2) Operation In the present embodiment, the lubricating oil that has dropped from the upper bearing 33 is received by the oil receiving portion 91c of the slinger 391, and then the centrifugal force due to the axial rotation of the crankshaft 17 causes the protrusion 91c3 to The upper surface is moved along the curve of the protrusion 91c3 to the radially outer end of the protrusion 91c3. The lubricating oil that has moved to the radially outer end of the protrusion 91c3 is scattered as oil droplets in the high-pressure space S1 by the action of centrifugal force.

(3) Features In the present embodiment, the lubricating oil dropped from the upper bearing 33 and received by the oil receiving portion 91c causes the upper surface of the protruding portion 91c3 to protrude from the protruding portion by the action of centrifugal force due to the axial rotation of the crankshaft 17. Since the oil is collected when moving to the radially outer end of 91c3, the oil droplets of the lubricating oil scattered from the slinger 391 are larger than the mist-like oil droplets. Therefore, in this embodiment, the mist phenomenon can be suppressed.

(4) Modification (4-1) Modification 4A
In the present embodiment, the slinger 391 has six protrusions 91c3, but may have another number of protrusions 91c3 such as eight protrusions 91c3. The greater the number of protrusions 91c3 formed on the slinger 391, the more easily the lubricant moves on the upper surface of the protrusion 91c3 to the radially outer end of the protrusion 91c3. To be collected. Accordingly, the lubricating oil is collected more efficiently and scattered from the slinger 391.

(4-2) Modification 4B
In the present embodiment, the upper surface of the protrusion 91c3 is a flat surface, but as shown in FIG. 15, an outer wall 91d is provided on the outer edge of the protrusion 91c3 excluding the end 91e on the radially outer side of the protrusion 91c3. It may be done. The outer wall 91d is formed vertically upward from the upper surface of the protrusion 91c3.

  In the slinger 391 in the present modified example, the outer wall 91d can prevent the lubricating oil from being scattered from the outer edge portion of the protruding portion 91c3 other than the end portion 91e. Accordingly, the lubricating oil is collected more efficiently and scattered from the slinger 391.

  INDUSTRIAL APPLICABILITY The present invention can be applied to a compressor, in particular, a compressor having a mechanism that suppresses the lubricating oil falling from the bearing from being scattered in a mist form.

DESCRIPTION OF SYMBOLS 10 Casing 15 Compression mechanism 16 Motor 17 Crankshaft 18 Balance weight 20 Discharge pipe 20a Opening part 23 Housing 23a 2nd oil guide part 33 Upper bearing (bearing)
58 Gas guide 58a First discharge port 58b Second discharge port 91 Slinger (annular member)
91b 1st oil guide part 91c Oil receiving part 91c1 Groove 91c2 Ridge 91c3 Projection part 92 Oil discharge hole 101 Scroll compressor (compressor)
S1 High pressure space S3 Oil storage space

JP 2009-235948 A

Claims (12)

A casing (10) for storing lubricating oil therein;
A compression mechanism (15) that is housed in the casing, compresses the refrigerant, and discharges the refrigerant into the high-pressure space (S1) in the casing;
A crankshaft (17) that is housed in the casing and performs a shaft rotational movement;
A motor (16) housed in the casing and driving the compression mechanism via the crankshaft;
A bearing (33) housed in the casing and pivotally supporting the crankshaft;
An annular member (91) disposed in the high-pressure space and fixed in close contact with the outer peripheral surface of the crankshaft below the bearing;
With
The annular member has an oil receiving portion (91c) for receiving the lubricating oil falling downward from the bearing, and the lubricating oil received by the oil receiving portion is misted by centrifugal force to move inside the high pressure space. Suppress the mist phenomenon that scatters,
Compressor (101). A housing (23) fixed in the casing and supporting the bearing;
The annular member forms an oil storage space (S3) that is a part of the high-pressure space and is a space below the bearing and above the annular member, together with the housing and the bearing,
The housing has an oil discharge hole (92) that is a part of the high-pressure space and communicates the space below the annular member and the oil storage space;
The annular member has a first oil guide portion (91b) that guides the lubricating oil received by the oil receiving portion and subjected to centrifugal force to the oil discharge hole.
The compressor according to claim 1. The housing has a second oil guide portion (23a) that guides the lubricating oil received by the oil receiving portion and subjected to centrifugal force to the oil discharge hole.
The compressor according to claim 2. A balance weight (18) housed in the casing, fixed in close contact with the outer peripheral surface of the crankshaft, and integrally formed with the annular member;
The compressor according to claim 2 or 3. The oil receiving portion of the annular member has an oil collecting portion that can collect the received lubricating oil.
The compressor according to claim 1. The oil collecting portion is a groove (91c1) extending from the radially inner side to the radially outer side of the annular member.
The compressor according to claim 5. The groove is curved in a direction opposite to the rotation direction of the annular member,
The compressor according to claim 6. The oil collecting portion is a ridge (91c2) extending from the radially inner side to the radially outer side of the annular member.
The compressor according to claim 5. The ridge is curved in a direction opposite to the rotational direction of the annular member;
The compressor according to claim 8. The oil collecting portion is a protruding portion (91c3) protruding from the radially inner side of the annular member to the radially outer side on the outer peripheral surface of the annular member,
The protrusion is curved in a direction opposite to the rotation direction of the annular member.
The compressor according to claim 5. A gas guide (58) having a discharge port that is housed in the casing and guides the refrigerant compressed by the compression mechanism and discharges the refrigerant to the high-pressure space;
A discharge pipe (20) that penetrates the casing and opens into the high-pressure space through an opening (20a);
Further comprising
The annular member is disposed at a position where lubricating oil is not scattered toward the discharge port and the opening.
The compressor according to any one of claims 5 to 10. The discharge port includes a first discharge port (58a) that discharges the refrigerant in the vertical direction and a second discharge port (58b) that discharges the refrigerant in the circumferential direction of the casing.
The lubricating oil is scattered from the annular member in the same direction as the direction in which the refrigerant discharged from the second discharge port flows.
The compressor according to claim 11.

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