EP3091231B1 - Open type compressor - Google Patents
Open type compressor Download PDFInfo
- Publication number
- EP3091231B1 EP3091231B1 EP16155460.5A EP16155460A EP3091231B1 EP 3091231 B1 EP3091231 B1 EP 3091231B1 EP 16155460 A EP16155460 A EP 16155460A EP 3091231 B1 EP3091231 B1 EP 3091231B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- space
- oil supply
- housing
- open type
- type compressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 239000012530 fluid Substances 0.000 claims description 53
- 230000006835 compression Effects 0.000 claims description 34
- 238000007906 compression Methods 0.000 claims description 34
- 239000000314 lubricant Substances 0.000 claims description 22
- 230000002093 peripheral effect Effects 0.000 claims description 22
- 238000005096 rolling process Methods 0.000 claims description 9
- 239000003921 oil Substances 0.000 description 87
- 238000007789 sealing Methods 0.000 description 11
- 238000005299 abrasion Methods 0.000 description 7
- 239000003507 refrigerant Substances 0.000 description 5
- 239000004519 grease Substances 0.000 description 3
- 238000005266 casting Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000008014 freezing Effects 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/005—Axial sealings for working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
- F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C27/009—Shaft sealings specially adapted for pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/30—Casings or housings
Definitions
- the present invention relates to an open type compressor applicable to a compressor, a pump, an expander, and the like.
- a crankshaft for driving a turning scroll is rotatably supported by a main bearing and a sub bearing.
- a mechanical seal for preventing leakage of fluid along the crankshaft is disposed.
- the open type compressor of JP 2000-352377A is a compressor provided with a lubricant oil supply passage for supplying high-pressure lubricant oil to a seal chamber in which the mechanical seal is provided.
- EP 1059450A2 discloses an open type compressor which has a seal part in the form of a non-contact type labyrinth seal seal located between the two bearings supporting the drive shaft. Oil gathered in an external separator for separating oil from the compressed fluid is supplied under pressure to a sealing chamber through an external oil return pipe communicating with a supply passage formed in a front casing corresponding to the second housing.
- the non-contact type labyrinth seal has a ring-shaped seal main body and a ring-shaped tip which is movably engaged with an inner circumferential surface of the seal main body such that, in operation, the tip is elastically deformed by the highly compressed lubricating oil which is supplied to the sealing chamber to leak part of it to a space located on the side of the labyrinth seal with respect to the one of the bearings located closer to a compression mechanism.
- the present invention has been made in view of the above circumstances, and an object of the invention is to provide an open type compressor capable of suppressing abrasion of a seal part to sufficiently ensure sealing performance, in a configuration in which a bearing part is disposed on a side closer to a compression mechanism than the seal part for preventing leakage of fluid.
- an open type compressor of the present invention has the features of claim 1.
- An open type compressor of the present invention includes: a compression mechanism that is driven by a drive shaft for rotating around an axis, and compresses fluid flowing into from a suction port to discharge the compressed fluid from a discharge port; a seal part that is in contact with an outer peripheral surface of the drive shaft, and prevents leakage of fluid along the drive shaft; a bearing part that is disposed on a side closer to the compression mechanism than the seal part, and supports the drive shaft; a cylindrical first housing that houses the compression mechanism, and has an outer peripheral surface formed with the suction port and the discharge port therein; and a second housing that is mounted so as to block an opening part of the first housing, and holds the bearing part and the seal part on the axis, characterized in that the second housing is formed with an oil supply groove for communicating a first space with a second space, the first space being communicated with the suction port and located on a side of the compression mechanism with respect to the bearing part, the second space being located on a side of the seal part with respect to the bearing part.
- the bearing part for supporting the drive shaft is disposed on the side closer to the compression mechanism than the seal part for preventing the leakage of the fluid along the drive shaft, and the first space communicated with the suction port for fluid is formed on the side of the compression mechanism with respect to the bearing part.
- This first space, and the second space located on the side of the seal part with respect to the bearing part are in a state communicated by the oil supply groove.
- mist-like lubricant oil contained in the fluid flowing into from the suction port is guided from the first space to the second space by the oil supply groove, and is supplied to the seal part.
- the open type compressor of the first aspect of the present invention in a configuration in which the bearing part is disposed on the side closer to the compression mechanism than the seal part for preventing the leakage of the fluid, it is possible to suppress abrasion of the seal part to sufficiently ensure sealing performance.
- a third space for circulating the fluid may be formed between an outer peripheral surface of the bearing part and an inner peripheral surface of the oil supply groove, and the second housing may be formed with a first oil supply hole for communicating the first space with the third space.
- the second housing may be formed with a straight pipe-like second oil supply hole for communicating the suction port with the first space, and the first oil supply hole having a straight pipe-like shape may be disposed on an extension line of the second oil supply hole.
- the bearing part may have an inner ring pressed into the drive shaft, an outer ring pressed into the second housing, and a plurality of rolling bodies disposed between the inner ring and the outer ring, and the outer ring is formed with a communication hole for guiding fluid flowing into the oil supply groove, to the plurality of rolling bodies.
- mist-like lubricant oil is reliably supplied to the plurality of rollers disposed between the inner ring and the outer ring of the bearing part, and the lubricity of the bearing part can be enhanced.
- the rolling bodies each may be a shaft-like member extending along the axis.
- the bearing part is configured by a needle bearing using shaft-like members as rolling bodies, and a dynamic rated load for the bearing part can be increased.
- an open type compressor capable of suppressing abrasion of a seal part to sufficiently ensure sealing performance, in a configuration in which a bearing part is disposed on a side closer to a compression mechanism than the seal part for preventing leakage of fluid.
- An open type scroll compressor (open type compressor) 1 of this embodiment includes a cylindrical housing 2 (first housing) that extends in a circumferential direction around an axis X, and a front housing 3 (second housing) mounted so as to block an opening part 2a provided on a front end side of the housing 2, as illustrated in Fig. 1 .
- the housing 2 is formed in a shape in which a rear end side is blocked, and the front housing 3 is fixed to the opening part 2a on the front end side by a bolt (not illustrated).
- a sealed space is formed inside the housing 2 in a state where the front housing 3 is fixed to the housing 2, and a scroll compression mechanism 5 and a drive shaft 6 are housed in the sealed space.
- a suction port 25 for allowing fluid (refrigerant gas) to flow into the sealed space, and a discharge port 24 for discharging fluid compressed by the scroll compression mechanism 5 from the sealed space to the outside are formed.
- the drive shaft 6 is rotatably supported by the front housing 3 through a main bearing 7 and a sub bearing 8 (bearing part). Additionally, a pulley 11 rotatably installed on an outer peripheral part of the front housing 3 through a bearing 10 is coupled to a front end of the drive shaft 6 protruding from the front housing 3 to the outside through a lip seal 9, through an electromagnetic clutch 12.
- an electromagnetic clutch 12 external power for driving the pulley 11 through the electromagnetic clutch 12 is transmitted to the drive shaft 6, so that the drive shaft 6 rotates around the axis X illustrated in Fig. 1 .
- a crank pin 13 eccentric by a predetermined dimension is integrally provided at a rear end of the drive shaft 6, a crank pin 13 eccentric by a predetermined dimension is integrally provided at a rear end of the drive shaft 6, a crank pin 13 eccentric by a predetermined dimension is integrally provided at a rear end of the drive shaft 6 . Additionally, the rear end of the drive shaft 6 is coupled to a turning scroll 16 of the scroll compression mechanism 5 described later through a publicly known driven crank mechanism 14 including a drive bush which varies the turning radius.
- the scroll compression mechanism 5 is driven by the drive shaft 6, and compresses fluid (refrigerant gas) that flows into from the suction port 25 formed on the outer peripheral surface of the housing 2, to discharge the compressed fluid from the discharge port 24 formed in the housing 2.
- a pair of fixed scroll 15 and a turning scroll 16 are meshed with each other while shifting in phase by 180 degrees, so that a pair of compression chambers 17 is formed between both the scrolls 15 and 16, and the compression chambers 17 are moved while the capacity is gradually reduced from an outer peripheral position to the center position, thereby compressing the fluid (refrigerant gas).
- the pair of fixed scroll 15 includes a discharge port 18 for discharging fluid compressed at a center part, and is fixed to a bottom wall surface of the housing 2 through a bolt 19.
- the turning scroll 16 is coupled to the crank pin 13 of the drive shaft 6 through the driven crank mechanism 14, and is supported on a thrust bearing surface of the front housing 3 through a publicly known rotation block mechanism (not illustrated) in such a manner as to freely revolve, turn, and drive.
- an O-ring 21 is provided at an outer periphery of an end plate 15A of the pair of fixed scroll 15.
- the O-ring 21 is brought into close contact with an inner peripheral surface of the housing 2, so that an internal space of the housing 2 is partitioned into a discharge chamber 22 and a suction chamber 23.
- the discharge chamber 22 is communicated with the discharge port 18, and fluid (compressed refrigerant gas) from the compression chambers 17 is discharged.
- the fluid discharged to the discharge port 18 is discharged from the discharge port 24 formed in the housing 2 to a freezing cycle side.
- the suction chamber 23 is communicated with the suction port 25 formed in the housing 2, the low-pressure fluid that circulates in the freezing cycle is sucked from the suction port 25, and the fluid is sucked in the compression chambers 17 via the suction chamber 23.
- the pair of fixed scroll 15 and the turning scroll 16 are configured such that scroll laps 15B and 16B are erected on the end plate 15A and 16A, respectively. Between both the scrolls 15 and 16, the pair of compression chambers 17 partitioned by the end plates 15A and 16A and the scroll laps 15B and 16B is formed symmetrically with respect to a scroll center. Additionally, the turning scroll 16 smoothly revolves, turns, and drives around the fixed scroll 15.
- the axial height on the outer peripheral side of the scroll laps 15B and 16B is made to be higher than the height on an inner peripheral side of the scroll laps 15B and 16B. Consequently, the three-dimensional compressible scroll compression mechanism 5 that compresses in both the circumferential direction of the scroll laps 15B and 16B, and the lap height direction, when the compression chambers 17 moves while reducing the capacity from the outer peripheral side to the center side, and compresses the fluid, is configured.
- the main bearing 7 is a member for supporting the drive shaft 6 on the axis X, an inner ring is pressed into the drive shaft 6, and an outer ring is pressed into an end on a side of the scroll compression mechanism 5 with respect to the front housing 3.
- the main bearing 7 is held on the axis X by the front housing 3.
- the main bearing 7 is disposed on a side closer to the scroll compression mechanism 5 than the sub bearing 8, and is a ball bearing having an outer diameter larger than the sub bearing 8.
- the sub bearing 8 supports the drive shaft 6 on the axis X along with the main bearing 7, an inner ring 8a is pressed into the drive shaft 6, and an outer ring 8b is pressed into the front housing 3.
- the sub bearing 8 is held by the front housing 3 on the axis X.
- the sub bearing 8 is disposed on a side closer to the scroll compression mechanism 5 than the lip seal 9, and is a needle bearing having an outer diameter smaller than the main bearing 7.
- the sub bearing 8 has the outer ring 8b, a plurality of rollers 8c (rolling bodies) disposed between the inner ring 8a and the outer ring 8b, and a holder 8d holding the plurality of rollers 8c.
- the plurality of rollers 8c each are a shaft-like member extending along the axis X.
- the lip seal 9 (seal part) is a member that is in contact with an outer peripheral surface of the drive shaft 6, and prevents leakage of fluid along the drive shaft 6.
- the lip seal 9 is mounted on an inner peripheral surface of the front housing 3, and is held on the axis X.
- oil supply grooves 3a, oil supply holes 3b (first oil supply holes), oil supply holes 3c (second oil supply holes) are formed in the front housing 3. Mist-like lubricant oil contained in fluid sucked from the suction port 25 is guided to a first space S1 located on a side of the scroll compression mechanism 5 with respect to the sub bearing 8, by the oil supply holes 3c for communicating the suction port 25 with the first space S1.
- mist-like lubricant oil contained in the fluid guided to the first space S1 is supplied to the main bearing 7, and the lubricity of the main bearing 7 is enhanced. Similarly, the mist-like lubricant oil is supplied to the sub bearing 8, and the lubricity of the sub bearing 8 is enhanced.
- oil supply holes 3c provided at two upper and lower places of the front housing 3 are illustrated in the longitudinal sectional view of Fig. 1 , the oil supply holes 3c are provided at a plurality of places (e.g., four places) in the circumferential direction around the axis X.
- the mist-like lubricant oil guided to the first space S1 is guided to a second space S2 located on a side of the lip seal 9 with respect to the sub bearing 8, by the oil supply grooves 3a for communicating the first space S1 with the second space S2.
- the oil supply grooves 3a each are a groove extending along the axis X and having a substantially semicircular cross-section.
- the oil supply grooves 3a are provided at four places at 90 degree intervals in the circumferential direction of the axis X.
- the places to be provided are not limited to the four places, and the oil supply grooves 3a may be provided at arbitrary places (e.g., eight places at 45 degree intervals).
- the oil supply grooves 3a may be previously provided when the front housing 3 is manufactured by casting. Additionally, after the oil supply grooves 3a may be formed by processing after the front housing 3 is manufactured by casting.
- a third space S3 for circulating fluid from the first space S1 to the second space S2 is formed between the outer peripheral surface of the outer ring 8b of the sub bearing 8 and the inner peripheral surfaces of the oil supply grooves 3a.
- the oil supply holes 3b formed in the front housing 3 are formed so as to communicate the first space S1 with the third space S3. As illustrated in Fig. 3 , the oil supply holes 3b are formed so as to discharge the mist-like lubricant oil to an intermediate position in the axis X direction of the third space S3.
- the oil supply holes 3b guide fluid flowing into from the first space S1, to the respective corresponding oil supply grooves 3a.
- the oil supply holes 3b and the oil supply holes 3c are each formed in a straight pipe-like shape, and the oil supply holes 3b are disposed on extension lines of the respective oil supply holes 3c. Therefore, fluid guided from the suction port 25 to each oil supply hole 3c is easily guided to each oil supply hole 3b through the first space S1. Consequently, a fixed amount of the fluid guided from each oil supply hole 3c to the first space S1 can be reliably guided to each oil supply hole 3b.
- each oil supply hole 3b is smaller than the diameter (passage cross-section area) of each oil supply hole 3c. Therefore, the total amount of fluid guided from the oil supply holes 3c to the first space S1 can be prevented from being guided to the oil supply holes 3b, and the fixed amount of the fluid guided from the oil supply holes 3c to the first space S1 can be reliably guided to the main bearing 7.
- communication holes 8e for guiding fluid flowing into the oil supply grooves 3a to the plurality of rollers 8c are formed in the outer ring 8b of the sub bearing 8. Mist-like lubricant oil contained in the fluid flowing into the oil supply grooves 3a through the communication holes 8e are supplied to the plurality of rollers 8c. Therefore, the lubricity of the sub bearing 8 is improved, and the flaking phenomenon (flaking phenomenon) of the sub bearing 8 is suppressed.
- positions in the axis X direction of the communication holes 8e formed in the outer ring 8b of the sub bearing 8 coincide with positions in the axis X direction where the oil supply holes 3b are connected to the oil supply grooves 3a.
- the fluid flowing from each oil supply hole 3b to the corresponding supply groove 3a has a velocity component in a direction flowing to the corresponding communication hole 8e, and therefore easily flows to the corresponding communication hole 8e.
- the communication holes 8e are formed at four places of the outer ring 8b of the sub bearing 8 so as to correspond to the respective four oil supply grooves 3a.
- the sub bearing 8 for supporting the drive shaft 6 is disposed on the side closer to the scroll compression mechanism 5 than the lip seal 9 for preventing the leakage of fluid along the drive shaft 6, and the first space S1 communicated with the suction port 25 for fluid is formed on the side of the scroll compression mechanism 5 with respect to the sub bearing 8.
- This first space S1, and the second space S2 located on the side of the lip seal 9 with respect to the sub bearing 8 are in a state communicated by the oil supply grooves 3a.
- mist-like lubricant oil contained in fluid flowing into from the suction port 25 is guided from the first space S1 to the second space S2 by the oil supply grooves 3a, and is supplied to the lip seal 9.
- the open type compressor 1 of this embodiment in a configuration in which the sub bearing 8 is disposed on the side closer to the scroll compression mechanism 5 than the lip seal 9 for preventing the leakage of fluid, it is possible to suppress abrasion of the lip seal 9 to sufficiently ensure sealing performance.
- a third space S3 for circulating fluid is formed between the outer peripheral surface of the sub bearing 8 and the inner peripheral surfaces of the oil supply grooves 3a, and the oil supply holes 3b for communicating the first space S1 with the third space S3 is formed in the front housing 3.
- lubricant oil that exists in the first space S1 is guided to the third space S3 via both the oil supply holes 3b and the oil supply grooves 3a. Therefore, mist-like lubricant oil is reliably guided from the first space S1 to the second space S2, so that it is possible to suppress the abrasion of the lip seal 9 to improve sealing performance.
- the straight pipe-like oil supply holes 3c for communicating the suction port 25 with the first space S1 are formed in the front housing 3, and the straight pipe-like oil supply holes 3b are disposed on the extension lines of the respective oil supply holes 3c.
- the sub bearing 8 has the inner ring 8a that is pressed into the drive shaft 6, the outer ring 8b that is pressed into the front housing 3, and the plurality of rollers 8c that are disposed between the inner ring 8a and the outer ring 8b. Additionally, the communication holes 8e for guiding fluid flowing into the oil supply grooves 3a to the plurality of rollers 8c are formed in the outer ring 8b.
- mist-like lubricant oil is reliably supplied to the plurality of rollers 8c disposed between the inner ring 8a and the outer ring 8b of the sub bearing 8, and the lubricity of the sub bearing 8 can be enhanced.
- the sub bearing 8 is a needle bearing using shaft-like members as rolling bodies. Therefore, a dynamic rated load for supporting the drive shaft can be increased compared to a case where a ball bearing is used as the sub bearing 8.
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- Engineering & Computer Science (AREA)
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- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
- Compressor (AREA)
Description
- The present invention relates to an open type compressor applicable to a compressor, a pump, an expander, and the like.
- Conventionally, there is known an open type compressor driven by protruding, to the outside of a housing, an end of a drive shaft rotatably supported in a housing through a bearing, and obtaining power from the outside (e.g., refer to PTL 1).
- In an open type compressor of
JP 2000-352377A - The open type compressor of
JP 2000-352377A -
EP 1059450A2 discloses an open type compressor which has a seal part in the form of a non-contact type labyrinth seal seal located between the two bearings supporting the drive shaft. Oil gathered in an external separator for separating oil from the compressed fluid is supplied under pressure to a sealing chamber through an external oil return pipe communicating with a supply passage formed in a front casing corresponding to the second housing. The non-contact type labyrinth seal has a ring-shaped seal main body and a ring-shaped tip which is movably engaged with an inner circumferential surface of the seal main body such that, in operation, the tip is elastically deformed by the highly compressed lubricating oil which is supplied to the sealing chamber to leak part of it to a space located on the side of the labyrinth seal with respect to the one of the bearings located closer to a compression mechanism. - In a case where the mechanical seal is disposed inside the sub bearing like the open type compressor of
JP 2000-352377A - In order to increase a dynamic rated load of the sub bearing, increase in a diameter of the sub bearing or the like is required. However, in the grease sealing type bearing, lubricity cannot be sufficiently enhanced with this increase. In this case, in order to enhance the lubricity of the sub bearing, it is desirable that the sub bearing is disposed inside the mechanical seal, and the lubricity is enhanced by mist-like lubricant oil contained in compressed fluid (refrigerant gas).
- However, when the sub bearing is disposed inside the mechanical seal, supply of lubricant oil to the mechanical seal is disturbed by the sub bearing. When the supply of the mist-like lubricant oil to the mechanical seal becomes insufficient, abrasion of the mechanical seal becomes significant, and sealing performance cannot be sufficiently ensured.
- The present invention has been made in view of the above circumstances, and an object of the invention is to provide an open type compressor capable of suppressing abrasion of a seal part to sufficiently ensure sealing performance, in a configuration in which a bearing part is disposed on a side closer to a compression mechanism than the seal part for preventing leakage of fluid.
- In order to solve the above problem, an open type compressor of the present invention has the features of
claim 1. - An open type compressor of the present invention includes: a compression mechanism that is driven by a drive shaft for rotating around an axis, and compresses fluid flowing into from a suction port to discharge the compressed fluid from a discharge port; a seal part that is in contact with an outer peripheral surface of the drive shaft, and prevents leakage of fluid along the drive shaft; a bearing part that is disposed on a side closer to the compression mechanism than the seal part, and supports the drive shaft; a cylindrical first housing that houses the compression mechanism, and has an outer peripheral surface formed with the suction port and the discharge port therein; and a second housing that is mounted so as to block an opening part of the first housing, and holds the bearing part and the seal part on the axis, characterized in that the second housing is formed with an oil supply groove for communicating a first space with a second space, the first space being communicated with the suction port and located on a side of the compression mechanism with respect to the bearing part, the second space being located on a side of the seal part with respect to the bearing part.
- According to the open type compressor of the first aspect of the present invention, the bearing part for supporting the drive shaft is disposed on the side closer to the compression mechanism than the seal part for preventing the leakage of the fluid along the drive shaft, and the first space communicated with the suction port for fluid is formed on the side of the compression mechanism with respect to the bearing part. This first space, and the second space located on the side of the seal part with respect to the bearing part are in a state communicated by the oil supply groove.
- Therefore, mist-like lubricant oil contained in the fluid flowing into from the suction port is guided from the first space to the second space by the oil supply groove, and is supplied to the seal part.
- Thus, according to the open type compressor of the first aspect of the present invention, in a configuration in which the bearing part is disposed on the side closer to the compression mechanism than the seal part for preventing the leakage of the fluid, it is possible to suppress abrasion of the seal part to sufficiently ensure sealing performance.
- In the open type compressor of the first aspect of the present invention, a third space for circulating the fluid may be formed between an outer peripheral surface of the bearing part and an inner peripheral surface of the oil supply groove, and the second housing may be formed with a first oil supply hole for communicating the first space with the third space.
- Consequently, lubricant oil that exists in the first space is guided to the third space via both the first oil supply hole and the oil supply groove. Therefore, mist-like lubricant oil is reliably guided from the first space to the second space, so that it is possible to suppress the abrasion of the seal part to improve sealing performance.
- In the open type compressor having the above configuration, the second housing may be formed with a straight pipe-like second oil supply hole for communicating the suction port with the first space, and the first oil supply hole having a straight pipe-like shape may be disposed on an extension line of the second oil supply hole.
- Consequently, the fixed amount of fluid guided from the second oil supply hole to the first space can be reliably guided to the first oil supply hole.
- In the open type compressor of the first aspect of the present invention, the bearing part may have an inner ring pressed into the drive shaft, an outer ring pressed into the second housing, and a plurality of rolling bodies disposed between the inner ring and the outer ring, and the outer ring is formed with a communication hole for guiding fluid flowing into the oil supply groove, to the plurality of rolling bodies.
- Consequently, mist-like lubricant oil is reliably supplied to the plurality of rollers disposed between the inner ring and the outer ring of the bearing part, and the lubricity of the bearing part can be enhanced.
- In the open type compressor having the above configuration, the rolling bodies each may be a shaft-like member extending along the axis.
- Consequently, the bearing part is configured by a needle bearing using shaft-like members as rolling bodies, and a dynamic rated load for the bearing part can be increased.
- According to the present invention, it is possible to provide an open type compressor capable of suppressing abrasion of a seal part to sufficiently ensure sealing performance, in a configuration in which a bearing part is disposed on a side closer to a compression mechanism than the seal part for preventing leakage of fluid.
-
- {
Fig. 1} Fig. 1 is a longitudinal sectional view illustrating an open type compressor of an embodiment of the present invention. - {
Fig. 2} Fig. 2 is a perspective view illustrating a sub bearing illustrated inFig. 1 , which is partially cut out. - {
Fig. 3} Fig. 3 is a partially enlarged view of the open type compressor illustrated inFig. 1 . - {
Fig. 4} Fig. 4 is a sectional view taken along the A-A arrow of the open type compressor illustrated inFig. 3 . - {
Fig. 5} Fig. 5 is a sectional view taken along the B-B arrow of the open type compressor illustrated inFig. 3 . - Hereinafter, an open type compressor of an embodiment of the present invention will be described with reference to
Fig. 1 to Fig. 5 . - An open type scroll compressor (open type compressor) 1 of this embodiment includes a cylindrical housing 2 (first housing) that extends in a circumferential direction around an axis X, and a front housing 3 (second housing) mounted so as to block an
opening part 2a provided on a front end side of thehousing 2, as illustrated inFig. 1 . - The
housing 2 is formed in a shape in which a rear end side is blocked, and thefront housing 3 is fixed to theopening part 2a on the front end side by a bolt (not illustrated). A sealed space is formed inside thehousing 2 in a state where thefront housing 3 is fixed to thehousing 2, and ascroll compression mechanism 5 and adrive shaft 6 are housed in the sealed space. - In an outer peripheral surface of the
housing 2, asuction port 25 for allowing fluid (refrigerant gas) to flow into the sealed space, and adischarge port 24 for discharging fluid compressed by thescroll compression mechanism 5 from the sealed space to the outside are formed. - The
drive shaft 6 is rotatably supported by thefront housing 3 through a main bearing 7 and a sub bearing 8 (bearing part). Additionally, apulley 11 rotatably installed on an outer peripheral part of thefront housing 3 through abearing 10 is coupled to a front end of thedrive shaft 6 protruding from thefront housing 3 to the outside through alip seal 9, through anelectromagnetic clutch 12. Thus, external power for driving thepulley 11 through theelectromagnetic clutch 12 is transmitted to thedrive shaft 6, so that thedrive shaft 6 rotates around the axis X illustrated inFig. 1 . - At a rear end of the
drive shaft 6, acrank pin 13 eccentric by a predetermined dimension is integrally provided. Additionally, the rear end of thedrive shaft 6 is coupled to a turningscroll 16 of thescroll compression mechanism 5 described later through a publicly known drivencrank mechanism 14 including a drive bush which varies the turning radius. - The
scroll compression mechanism 5 is driven by thedrive shaft 6, and compresses fluid (refrigerant gas) that flows into from thesuction port 25 formed on the outer peripheral surface of thehousing 2, to discharge the compressed fluid from thedischarge port 24 formed in thehousing 2. - In the
scroll compression mechanism 5, a pair offixed scroll 15 and aturning scroll 16 are meshed with each other while shifting in phase by 180 degrees, so that a pair ofcompression chambers 17 is formed between both thescrolls compression chambers 17 are moved while the capacity is gradually reduced from an outer peripheral position to the center position, thereby compressing the fluid (refrigerant gas). - The pair of
fixed scroll 15 includes adischarge port 18 for discharging fluid compressed at a center part, and is fixed to a bottom wall surface of thehousing 2 through abolt 19. The turningscroll 16 is coupled to thecrank pin 13 of thedrive shaft 6 through the drivencrank mechanism 14, and is supported on a thrust bearing surface of thefront housing 3 through a publicly known rotation block mechanism (not illustrated) in such a manner as to freely revolve, turn, and drive. - At an outer periphery of an
end plate 15A of the pair offixed scroll 15, an O-ring 21 is provided. The O-ring 21 is brought into close contact with an inner peripheral surface of thehousing 2, so that an internal space of thehousing 2 is partitioned into adischarge chamber 22 and asuction chamber 23. - The
discharge chamber 22 is communicated with thedischarge port 18, and fluid (compressed refrigerant gas) from thecompression chambers 17 is discharged. The fluid discharged to thedischarge port 18 is discharged from thedischarge port 24 formed in thehousing 2 to a freezing cycle side. - The
suction chamber 23 is communicated with thesuction port 25 formed in thehousing 2, the low-pressure fluid that circulates in the freezing cycle is sucked from thesuction port 25, and the fluid is sucked in thecompression chambers 17 via thesuction chamber 23. - The pair of
fixed scroll 15 and the turningscroll 16 are configured such thatscroll laps end plate scrolls compression chambers 17 partitioned by theend plates scroll laps scroll 16 smoothly revolves, turns, and drives around the fixedscroll 15. - As illustrated in
Fig. 1 , in thecompression chambers 17, the axial height on the outer peripheral side of thescroll laps scroll laps scroll compression mechanism 5 that compresses in both the circumferential direction of thescroll laps compression chambers 17 moves while reducing the capacity from the outer peripheral side to the center side, and compresses the fluid, is configured. - The
main bearing 7 is a member for supporting thedrive shaft 6 on the axis X, an inner ring is pressed into thedrive shaft 6, and an outer ring is pressed into an end on a side of thescroll compression mechanism 5 with respect to thefront housing 3. Themain bearing 7 is held on the axis X by thefront housing 3. Themain bearing 7 is disposed on a side closer to thescroll compression mechanism 5 than thesub bearing 8, and is a ball bearing having an outer diameter larger than thesub bearing 8. - The
sub bearing 8 supports thedrive shaft 6 on the axis X along with themain bearing 7, aninner ring 8a is pressed into thedrive shaft 6, and anouter ring 8b is pressed into thefront housing 3. Thesub bearing 8 is held by thefront housing 3 on the axis X. Thesub bearing 8 is disposed on a side closer to thescroll compression mechanism 5 than thelip seal 9, and is a needle bearing having an outer diameter smaller than themain bearing 7. - As illustrated in the perspective view of
Fig. 2 , thesub bearing 8 has theouter ring 8b, a plurality ofrollers 8c (rolling bodies) disposed between theinner ring 8a and theouter ring 8b, and aholder 8d holding the plurality ofrollers 8c. The plurality ofrollers 8c each are a shaft-like member extending along the axis X. - In
Fig. 2 , illustration of theinner ring 8a is omitted. - The lip seal 9 (seal part) is a member that is in contact with an outer peripheral surface of the
drive shaft 6, and prevents leakage of fluid along thedrive shaft 6. Thelip seal 9 is mounted on an inner peripheral surface of thefront housing 3, and is held on the axis X. - Now, a mechanism for supplying mist-like lubricant oil contained in fluid sucked from the
suction port 25, to thesub bearing 8 and thelip seal 9 will be described. - As illustrated in
Fig. 1 , in thefront housing 3,oil supply grooves 3a,oil supply holes 3b (first oil supply holes), oil supply holes 3c (second oil supply holes) are formed. Mist-like lubricant oil contained in fluid sucked from thesuction port 25 is guided to a first space S1 located on a side of thescroll compression mechanism 5 with respect to thesub bearing 8, by the oil supply holes 3c for communicating thesuction port 25 with the first space S1. - The mist-like lubricant oil contained in the fluid guided to the first space S1 is supplied to the
main bearing 7, and the lubricity of themain bearing 7 is enhanced. Similarly, the mist-like lubricant oil is supplied to thesub bearing 8, and the lubricity of thesub bearing 8 is enhanced. - Although the oil supply holes 3c provided at two upper and lower places of the
front housing 3 are illustrated in the longitudinal sectional view ofFig. 1 , the oil supply holes 3c are provided at a plurality of places (e.g., four places) in the circumferential direction around the axis X. - As illustrated in the enlarged view of a main part of
Fig. 3 , the mist-like lubricant oil guided to the first space S1 is guided to a second space S2 located on a side of thelip seal 9 with respect to thesub bearing 8, by theoil supply grooves 3a for communicating the first space S1 with the second space S2. - As illustrated in
Fig. 3 andFig. 4 (sectional view taken along the A-A arrow ofFig. 3 ), theoil supply grooves 3a each are a groove extending along the axis X and having a substantially semicircular cross-section. - As illustrated in
Fig. 4 , theoil supply grooves 3a are provided at four places at 90 degree intervals in the circumferential direction of the axis X. The places to be provided are not limited to the four places, and theoil supply grooves 3a may be provided at arbitrary places (e.g., eight places at 45 degree intervals). - The
oil supply grooves 3a may be previously provided when thefront housing 3 is manufactured by casting. Additionally, after theoil supply grooves 3a may be formed by processing after thefront housing 3 is manufactured by casting. - As illustrated in
Fig. 3 , a third space S3 for circulating fluid from the first space S1 to the second space S2 is formed between the outer peripheral surface of theouter ring 8b of thesub bearing 8 and the inner peripheral surfaces of theoil supply grooves 3a. - As illustrated in
Fig. 3 , theoil supply holes 3b formed in thefront housing 3 are formed so as to communicate the first space S1 with the third space S3. As illustrated inFig. 3 , theoil supply holes 3b are formed so as to discharge the mist-like lubricant oil to an intermediate position in the axis X direction of the third space S3. - As illustrated by the arrows in
Fig. 4 , theoil supply holes 3b guide fluid flowing into from the first space S1, to the respective correspondingoil supply grooves 3a. - As illustrated in
Fig. 1 , theoil supply holes 3b and the oil supply holes 3c are each formed in a straight pipe-like shape, and theoil supply holes 3b are disposed on extension lines of the respective oil supply holes 3c. Therefore, fluid guided from thesuction port 25 to eachoil supply hole 3c is easily guided to eachoil supply hole 3b through the first space S1. Consequently, a fixed amount of the fluid guided from eachoil supply hole 3c to the first space S1 can be reliably guided to eachoil supply hole 3b. - As illustrated in
Fig. 1 , the diameter (passage cross-section area) of eachoil supply hole 3b is smaller than the diameter (passage cross-section area) of eachoil supply hole 3c. Therefore, the total amount of fluid guided from the oil supply holes 3c to the first space S1 can be prevented from being guided to theoil supply holes 3b, and the fixed amount of the fluid guided from the oil supply holes 3c to the first space S1 can be reliably guided to themain bearing 7. - As illustrated in
Fig. 3 ,communication holes 8e for guiding fluid flowing into theoil supply grooves 3a to the plurality ofrollers 8c are formed in theouter ring 8b of thesub bearing 8. Mist-like lubricant oil contained in the fluid flowing into theoil supply grooves 3a through thecommunication holes 8e are supplied to the plurality ofrollers 8c. Therefore, the lubricity of thesub bearing 8 is improved, and the flaking phenomenon (flaking phenomenon) of thesub bearing 8 is suppressed. - As illustrated in
Fig. 3 , positions in the axis X direction of thecommunication holes 8e formed in theouter ring 8b of thesub bearing 8 coincide with positions in the axis X direction where theoil supply holes 3b are connected to theoil supply grooves 3a. The fluid flowing from eachoil supply hole 3b to thecorresponding supply groove 3a has a velocity component in a direction flowing to thecorresponding communication hole 8e, and therefore easily flows to thecorresponding communication hole 8e. - As illustrated in
Fig. 5 , thecommunication holes 8e are formed at four places of theouter ring 8b of thesub bearing 8 so as to correspond to the respective fouroil supply grooves 3a. - Action and effects produced by the
open type compressor 1 of this embodiment, described above, will be described. - According to the
open type compressor 1 of this embodiment, thesub bearing 8 for supporting thedrive shaft 6 is disposed on the side closer to thescroll compression mechanism 5 than thelip seal 9 for preventing the leakage of fluid along thedrive shaft 6, and the first space S1 communicated with thesuction port 25 for fluid is formed on the side of thescroll compression mechanism 5 with respect to thesub bearing 8. This first space S1, and the second space S2 located on the side of thelip seal 9 with respect to thesub bearing 8 are in a state communicated by theoil supply grooves 3a. - Therefore, mist-like lubricant oil contained in fluid flowing into from the
suction port 25 is guided from the first space S1 to the second space S2 by theoil supply grooves 3a, and is supplied to thelip seal 9. - Thus, according to the
open type compressor 1 of this embodiment, in a configuration in which thesub bearing 8 is disposed on the side closer to thescroll compression mechanism 5 than thelip seal 9 for preventing the leakage of fluid, it is possible to suppress abrasion of thelip seal 9 to sufficiently ensure sealing performance. - In the
open type compressor 1 of this embodiment, a third space S3 for circulating fluid is formed between the outer peripheral surface of thesub bearing 8 and the inner peripheral surfaces of theoil supply grooves 3a, and theoil supply holes 3b for communicating the first space S1 with the third space S3 is formed in thefront housing 3. - Consequently, lubricant oil that exists in the first space S1 is guided to the third space S3 via both the
oil supply holes 3b and theoil supply grooves 3a. Therefore, mist-like lubricant oil is reliably guided from the first space S1 to the second space S2, so that it is possible to suppress the abrasion of thelip seal 9 to improve sealing performance. - In the
open type compressor 1 of this embodiment, the straight pipe-like oil supply holes 3c for communicating thesuction port 25 with the first space S1 are formed in thefront housing 3, and the straight pipe-likeoil supply holes 3b are disposed on the extension lines of the respective oil supply holes 3c. - Consequently, the fixed amount of fluid guided from the oil supply holes 3c to the first space S1 can be reliably guided to the
oil supply holes 3b. - In the
open type compressor 1 of this embodiment, thesub bearing 8 has theinner ring 8a that is pressed into thedrive shaft 6, theouter ring 8b that is pressed into thefront housing 3, and the plurality ofrollers 8c that are disposed between theinner ring 8a and theouter ring 8b. Additionally, thecommunication holes 8e for guiding fluid flowing into theoil supply grooves 3a to the plurality ofrollers 8c are formed in theouter ring 8b. - Consequently, mist-like lubricant oil is reliably supplied to the plurality of
rollers 8c disposed between theinner ring 8a and theouter ring 8b of thesub bearing 8, and the lubricity of thesub bearing 8 can be enhanced. - In the
open type compressor 1 of this embodiment, thesub bearing 8 is a needle bearing using shaft-like members as rolling bodies. Therefore, a dynamic rated load for supporting the drive shaft can be increased compared to a case where a ball bearing is used as thesub bearing 8. - The present invention is not limited to the invention according to the above embodiment, and can be appropriately changed and modified without departing from the scope of the present invention.
Claims (5)
- An open type compressor (1) comprising:a compression mechanism (5) that is arranged to be driven by a drive shaft (6) for rotating around an axis (X), and to compress fluid flowing into from a suction port (25) to discharge the compressed fluid from a discharge port (24);a seal part (9) that is in contact with an outer peripheral surface of the drive shaft (6), and is arranged to prevent leakage of fluid along the drive shaft (6);a bearing part (8) that is disposed on a side closer to the compression mechanism (5) than the seal part (9), and supports the drive shaft (6);a cylindrical first housing (2) that houses the compression mechanism (5) and has an outer peripheral surface formed with the suction port (25) and the discharge port (24) therein;a second housing (3) that is mounted so as to block an opening part (2a) of the first housing (2) and holds the bearing part (8) and the seal part (9) on the axis (X),a first space (S1) that is communicated with the suction port (25) and is located on a side of the compression mechanism (5) with respect to the bearing part (8), anda second space (S2) that is located on a side of the seal part (9) with respect to the bearing part (8), characterised in thatthe second housing (3) is formed with an oil supply groove (3a) communicating the first space (S1) with the second space (S2) such that, in operation, mist-like lubricant oil guided to the first space (S1) is guided to the second space (S2) by the oil supply groove (3a).
- The open type compressor (1) according to claim 1, wherein
a third space (S3) for circulating the fluid is formed between an outer peripheral surface of the bearing part (8) and an inner peripheral surface of the oil supply groove (3a), and
the second housing (3) is formed with a first oil supply hole (3b) for communicating the first space (S1) with the third space (S3). - The open type compressor (1) according to claim 2, wherein
the second housing (3) is formed with a straight pipe-like second oil supply hole (3c) for communicating the suction port (25) with the first space (S1), and
the first oil supply hole (3b) having a straight pipe-like shape is disposed on an extension line of the second oil supply hole (3c). - The open type compressor (1) according to any one of claims 1 to 3, wherein
the bearing part (8) has an inner ring (8a) pressed into the drive shaft (6), an outer ring (8b) pressed into the second housing (3), and a plurality of rolling bodies (8c) disposed between the inner ring (8a) and the outer ring (8b), and
the outer ring (8b) is formed with a communication hole (8e) for guiding fluid flowing into the oil supply groove (3a), to the plurality of rolling bodies (8c). - The open type compressor (1) according to claim 4, wherein
the rolling bodies (8c) each are a shaft-like member extending along the axis (X).
Applications Claiming Priority (1)
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JP2015034091A JP6664879B2 (en) | 2015-02-24 | 2015-02-24 | Open type compressor |
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JP2018071459A (en) | 2016-10-31 | 2018-05-10 | 三菱重工サーマルシステムズ株式会社 | Open type compressor |
JP6917845B2 (en) * | 2017-09-21 | 2021-08-11 | サンデン・オートモーティブコンポーネント株式会社 | Scroll type fluid machine |
JP6963452B2 (en) * | 2017-09-28 | 2021-11-10 | 三菱重工サーマルシステムズ株式会社 | Open compressor |
JP6961438B2 (en) | 2017-09-28 | 2021-11-05 | 三菱重工サーマルシステムズ株式会社 | Open compressor |
CN108950636A (en) * | 2018-08-27 | 2018-12-07 | 深圳立比立精密科技有限公司 | A kind of Novel anode oxidizing polishing slot |
JP7263071B2 (en) * | 2019-03-18 | 2023-04-24 | 三菱重工サーマルシステムズ株式会社 | open compressor |
EP4112937A1 (en) | 2021-07-01 | 2023-01-04 | Kaeser Kompressoren SE | Transmission arrangement with a slip ring seal and method for mounting a transmission arrangement with a slip ring seal |
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JPS513413A (en) * | 1974-06-28 | 1976-01-12 | Hitachi Ltd | ROOTARIISHIKIATSUSHUKUKINO JUNKATSUHOHO OYOBI JUNKATSUKIKO |
US4538975A (en) * | 1983-08-16 | 1985-09-03 | Sanden Corporation | Scroll type compressor with lubricating system |
JPH08159058A (en) * | 1994-11-30 | 1996-06-18 | Sanden Corp | Scroll compressor |
JP2000352377A (en) * | 1999-06-08 | 2000-12-19 | Mitsubishi Heavy Ind Ltd | Open type compressor |
JP4747775B2 (en) * | 2005-01-11 | 2011-08-17 | 株式会社豊田自動織機 | Scroll compressor |
JP2007205297A (en) * | 2006-02-03 | 2007-08-16 | Matsushita Electric Ind Co Ltd | Scroll compressor |
CN203230590U (en) * | 2013-05-14 | 2013-10-09 | 力达(中国)机电有限公司 | Lubricating cooling system of vortex-type air compressor |
-
2015
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2016
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