WO2022255275A1 - スクリュー圧縮機 - Google Patents
スクリュー圧縮機 Download PDFInfo
- Publication number
- WO2022255275A1 WO2022255275A1 PCT/JP2022/021846 JP2022021846W WO2022255275A1 WO 2022255275 A1 WO2022255275 A1 WO 2022255275A1 JP 2022021846 W JP2022021846 W JP 2022021846W WO 2022255275 A1 WO2022255275 A1 WO 2022255275A1
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- WIPO (PCT)
- Prior art keywords
- bearing
- space
- casing
- supply port
- liquid supply
- Prior art date
Links
- 239000007788 liquid Substances 0.000 claims abstract description 140
- 230000001050 lubricating effect Effects 0.000 claims abstract description 69
- 238000007789 sealing Methods 0.000 claims abstract description 44
- 238000005192 partition Methods 0.000 claims abstract description 21
- 239000012530 fluid Substances 0.000 claims description 44
- 238000004891 communication Methods 0.000 claims description 17
- 239000000314 lubricant Substances 0.000 claims description 4
- 238000013019 agitation Methods 0.000 description 14
- 238000005096 rolling process Methods 0.000 description 14
- 239000010687 lubricating oil Substances 0.000 description 6
- 239000003921 oil Substances 0.000 description 5
- 238000011084 recovery Methods 0.000 description 5
- 238000005461 lubrication Methods 0.000 description 3
- 230000004308 accommodation Effects 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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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
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/52—Bearings for assemblies with supports on both sides
-
- 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
Definitions
- the present invention relates to a screw compressor, and is suitable for application to a screw compressor equipped with a liquid supply mechanism.
- an oil-cooled screw compressor disclosed in Patent Document 1 is known as a screw compressor.
- This screw compressor has an oil supply hole through which lubricating oil is supplied to a space in which the suction bearing and the mechanical seal are stored, and a first recovery hole is formed in the partition between the screw rotor and the suction side bearing. Furthermore, a second recovery hole is formed bypassing the first recovery hole, and these first and second recovery holes also have a structure opening to the compressed air suction passage.
- the suction side bearing agitates the lubricating oil accumulated in the space and also agitates the lubricating oil passing through the suction side bearing.
- the agitation loss generated by the process was large, which was a factor in the deterioration of the performance as a compressor.
- the present invention has been made in consideration of the above points, and intends to propose a highly reliable and highly efficient screw compressor that can effectively prevent deterioration in performance as a compressor.
- the present invention provides a screw compressor for compressing a working medium, which includes first and second screw rotors for sucking, compressing and discharging the working medium, and one end side of a rotating shaft of a power source.
- a first bearing that rotatably supports the one end side of the connected first screw rotor; a casing that houses the first screw rotor and the first bearing; a through hole of the casing through which the shaft portion of the first screw rotor, which is arranged on the opposite side of the toothed portion of the first screw rotor with respect to one bearing and is connected to the output shaft of the power source, is inserted; a partition wall for separating the first bearing and the shaft sealing member inside the casing; and a first bearing provided in the casing for supplying lubricating fluid to the first bearing.
- a first liquid supply port and a liquid supply path having a second liquid supply port for supplying the lubricating liquid to the shaft sealing member are provided.
- FIG. 2 is a horizontal sectional view showing the configuration of the male rotor side in the screw compressor according to the first embodiment
- FIG. 2 is a vertical sectional view showing the configuration of the male rotor side in the screw compressor according to the first embodiment
- FIG. 3 is a vertical cross-sectional view showing the configuration of a male rotor-side fluid supply path in the screw compressor according to the first embodiment
- 2 is a vertical sectional view showing the configuration of the female rotor side in the screw compressor according to the first embodiment
- FIG. FIG. 3 is a conceptual diagram for explaining an external route of lubricating fluid injected into the screw compressor according to the first embodiment
- FIG. 6 is a vertical cross-sectional view showing the configuration of a male rotor side in a screw compressor according to a second embodiment
- FIG. 11 is a vertical cross-sectional view showing the configuration of a male rotor side in a screw compressor according to a third embodiment
- FIG. 11 is a vertical cross-sectional view showing the configuration of a male rotor side in a screw compressor according to a fourth embodiment
- FIGS. 1 and 2 show a screw compressor 1 according to a first embodiment.
- 1 is a CC arrow view (horizontal sectional view) in FIG. 2
- FIG. 2 is an AA arrow view (vertical sectional view) in FIG.
- the screw compressor 1 of the present embodiment includes a male rotor 2 and a female rotor 3, which are a pair of screw rotors, and a casing 4 that houses the male rotor 2 and the female rotor 3. configured with.
- the male rotor 2 includes a toothed portion 2A formed with a plurality of spirally extending teeth (lobes), and one end side of the toothed portion 2A in the axial direction of the rotor (the left side in FIGS. 1 and 2). ), and a discharge-side shaft portion 2C formed on the other end side of the toothed portion 2A in the rotor axial direction (the right side in FIGS. 1 and 2, hereinafter the same).
- the suction side shaft portion 2B of the male rotor 2 is rotatably supported by a suction side bearing (hereinafter referred to as a first suction side bearing) 5, and the discharge side shaft portion 2C of the male rotor 2 is supported by a discharge side bearing (hereinafter referred to as a first suction side bearing). , which is called a first discharge-side bearing) 6, so as to be rotatable.
- a suction side bearing hereinafter referred to as a first suction side bearing
- a discharge side bearing hereinafter referred to as a first suction side bearing
- the female rotor 3 includes a toothed portion 3A formed with a plurality of teeth that mesh with the teeth of the male rotor 2, a suction side shaft portion 3B formed on one end side of the toothed portion 3A in the axial direction of the rotor, and a toothed portion. and a discharge-side shaft portion 3C formed on the other end side in the rotor axial direction of 3A.
- the suction side shaft portion 3B of the female rotor 3 is rotatably supported by a suction side bearing (hereinafter referred to as a second suction side bearing) 7, and the discharge side shaft portion 3C of the female rotor 3 is supported by a discharge side bearing (hereinafter referred to as a second suction side bearing). , which is referred to as a second discharge-side bearing) 8 is rotatably supported.
- the suction side shaft portion 2B of the male rotor 2 penetrates the casing 4 and is connected to the rotating shaft of the motor (not shown).
- the male rotor 2 can be rotationally driven integrally with the rotating shaft of the motor, and the female rotor 3 can also be rotationally driven integrally with the male rotor 2 accordingly.
- the casing 4 includes a main casing 4A, a discharge side casing 4B connected to the other end of the main casing 4A in the rotor axial direction, and a suction side partition 4C connected to one end of the main casing 4A in the rotor axial direction. and a suction side casing 4D.
- the discharge-side casing 4B is provided with a first discharge-side bearing housing space 9A and a second discharge-side bearing housing space 9B which are provided independently of each other.
- the first discharge side bearing 6 is accommodated, and the second discharge side bearing 8 is accommodated in the second discharge side bearing accommodation space 9B.
- the discharge-side casing 4B has a discharge port 10 positioned radially outside (lower in FIG. 2) than the toothed portions 2A and 3A of the male rotor 2 and the female rotor 3, and a discharge port 10 and a bore (to be described later).
- a discharge path 11 connecting between 12 is formed.
- the main casing 4A is formed with a bore 12 for housing the toothed portion 2A of the male rotor 2 and the toothed portion 3A of the female rotor 3.
- the bore 12 is a space having a shape in which two cylindrical holes are partially overlapped to accommodate the toothed portion 2A of the male rotor 2 and the toothed portion 3A of the female rotor 3 in a meshed state.
- a working chamber is formed by the inner wall surface of the bore 12, the tooth spaces of the male rotor 2, and the tooth spaces of the female rotor 3.
- the working chamber is formed such that its volume gradually decreases from one end side to the other end side in the axial direction of the rotor. As a result, the working medium such as air sucked from the suction port 13 is gradually compressed in the working chamber and discharged from the discharge port 10 through the discharge path 11 .
- the suction port 13 is formed outside the toothed portion 2A of the male rotor 2 and the toothed portion 3A of the female rotor 3 in the main casing 4A in the rotor radial direction (upper side in FIG. 2).
- the suction port 13 communicates with the working chamber via the suction space 14 , and the working medium sucked from the suction port 13 is supplied to the working chamber via the suction space 14 .
- a cylindrical first suction-side bearing housing space 15 and a cylindrical second suction-side bearing housing space 16 are formed in the end face of the main casing 4A on one end side in the rotor axial direction.
- the first suction side bearing 5 is fitted in the first suction side bearing housing space
- the second suction side bearing 7 is fitted in the second suction side bearing housing space 16. Contained.
- a first bearing communication space 17 having a slightly smaller diameter than the first suction side bearing housing space 15 and communicating between the first suction side bearing housing space 15 and the suction space 14;
- a second bearing communicating space 18 having a slightly smaller diameter than the second suction side bearing accommodating space 16 and communicating between the second suction side bearing accommodating space 16 and the suction space 14 is formed.
- a suction side partition 4C is fixed to one end face of the main casing 4A in the rotor axial direction
- a suction side casing 4D is fixed to the end of the suction side partition 4C in the rotor axial direction.
- a shaft sealing space 20 communicating with the through hole 19 through which the suction side shaft portion 2B of the male rotor 2 is inserted is formed on the surface facing the suction side partition wall 4C.
- a shaft sealing member 21 for sealing the through hole 19 is arranged inside.
- the casing 4 of the screw compressor 1 is provided with a first working chamber liquid supply port 22 that communicates with the working chamber in the bore 12 , and through this first working chamber liquid supply port 22 is adapted to inject liquid into the working chamber.
- a first suction side liquid supply port 23 is provided on the side of the suction port 13 of the casing 4, and a first discharge side liquid supply port 24 is provided on the side of the discharge port 10 of the casing 4.
- the liquid can be injected into the shaft sealing space 20 and the first suction-side bearing housing space 15 through the suction-side liquid supply port 23, and the liquid can be injected into the first discharge-side liquid supply port 24 through the first discharge-side liquid supply port 24. Liquid can be injected into the discharge side bearing housing space 9A.
- the lubricating liquid injected into the first suction side liquid supply port 23 passes through the inside of the casing 4 and is discharged into the shaft seal space 20 via the first liquid supply port 25, and is discharged into the second liquid supply. It is discharged into the first suction side bearing accommodation space 15 through the port 26 .
- FIG. 3 shows the flow path inside the casing 4 of the lubricating liquid supplied to the first suction side bearing 5 and the shaft sealing member 21 .
- the arrows in the drawing indicate the direction in which the lubricating liquid is supplied.
- a first liquid supply path 27 that communicates the first suction side liquid supply port 23 with the first and second liquid supply ports 25 and 26. It is The first liquid supply path 27 branches into first and second branched paths 27A and 27B on the way, the first branched path 27A communicates with the first liquid supply port 25, and the second branched path 27B is formed to communicate with the second liquid supply port 26 .
- the first liquid supply port 25 opens toward the shaft sealing member 21 arranged in the shaft sealing space 20 , so that the liquid is injected into the casing 4 from the first suction side liquid supply port 23 .
- the lubricating liquid that has flowed into the first branch passage 27A is discharged from the first liquid supply port 25 and supplied to the shaft sealing member 21 .
- the shaft seal space 20 communicates with the suction space 14 via a bypass communication passage 28, whereby the lubricating fluid injected into the shaft seal space 20 is discharged to the suction space 14 via the bypass communication passage 28.
- the second liquid supply port 26 opens toward the first suction side bearing 5 housed in the first suction side bearing housing space 15, thereby forming the first suction side liquid supply port.
- 23 into the casing 4 and flowed into the second branch passage 27B is discharged from the second liquid supply port 26 and supplied to the first suction side bearing 5 from the male rotor 2 side.
- the first suction side bearing 5 since the first suction side bearing 5 is partially exposed to the suction space 14 via the first bearing communication space 17 of the main casing 4A, the first The lubricating fluid supplied to the suction side bearing 5 flows out to the suction space 14 via the first bearing communication space 17 . This lubricating fluid then joins the lubricating fluid that has flowed into the suction space 14 via the bypass communication passage 28, and is conveyed to the working chamber together with the working medium that has flowed into the suction space 14 from the suction port 13.
- the agitation loss of the lubricating liquid in the first suction side bearing 5 is considered.
- the first suction side bearing 5 is a roller bearing, but it is not limited to this. There may be.
- the rolling elements in the rolling bearing roll while pushing the lubricating liquid aside, so they are subject to fluid resistance. Further, in the present embodiment, since the lubricating fluid supplied to the first suction side bearing 5 is constantly replaced, the rolling elements need to accelerate the newly introduced lubricating fluid. There is The sum of these is the agitation loss.
- the location where the first suction-side bearing 5 is arranged is located higher than the lowest end of the suction space 14, so that the lubricating fluid is less likely to accumulate. It has become.
- the screw compressor 1 is installed with the male rotor 2 and the female rotor 3 horizontal as shown in FIG. Since the first bearing communication space 17 is formed so as to be lower than the height position of the lowermost end of the inner diameter of the outer ring, the lubricant in the rolling element raceway of the first suction side bearing 5 is discharged to the suction space 14. It has an easy-to-use structure.
- the second liquid supply port 26 is formed on the side of the suction side partition wall 4C, the lubricating liquid supplied to the first suction side bearing 5 through the second liquid supply port 26 flows into the suction space 14 side. In order to flow out, the lubricating liquid needs to pass through the rolling element raceway of the first suction side bearing 5 which rotates, so the stirring loss increases accordingly.
- the second liquid supply port 26 is formed so as to supply the lubricating liquid to the first suction side bearing 5 from the male rotor 2 side. It is not necessary for all the lubricating fluid supplied to the first suction side bearing 5 to pass through the rolling element raceways of the rotating first suction side bearing 5 . Therefore, it can be said that the present screw compressor 1 has a structure in which the agitation loss of the lubricating liquid in the rolling element raceway portion of the first suction side bearing 5 is small.
- the required amount of lubricating liquid in the first suction side bearing 5 is generally smaller than the required amount in the shaft sealing member 21 such as a mechanical seal.
- the space 20 is separated from the space 20 by the suction side partition wall 4C, and the first liquid supply port 25 for supplying the lubricating liquid to the shaft sealing member 21 and the second liquid supply port 25 for supplying the lubricating liquid to the first suction side bearing 5 are provided. Since the liquid supply port 26 is provided independently, it is possible to supply lubricating liquid in an amount suitable for each of the shaft sealing member 21 and the first suction side bearing 5 .
- the distribution of the amount of lubricating fluid supplied to the shaft sealing member 21 and the first suction side bearing 5 can be determined by the pressure loss of the first fluid supply path 27. can be determined by the length of the branch passages 27A and 27B, the hydraulic diameter, the diameters of the first and second liquid supply ports 25 and 26, and the like. In the present embodiment, as described above, the amount of lubricating liquid required to be supplied to the shaft sealing member 21 is larger than the amount of lubricating liquid to be supplied to the first suction side bearing 5.
- the lengths and hydraulic diameters of the first and second branches 27A, 27B and the diameters of the first and second liquid supply ports 25, 26 are selected.
- FIG. 4 is a BB arrow view (vertical sectional view) in FIG.
- the main casing 4A is provided with a second working chamber liquid supply port 30 communicating with the working chamber in the bore 12, and lubrication is performed from the outside of the screw compressor 1 via the second working chamber liquid supply port 30. It is adapted to supply liquid to the working chamber.
- a second discharge-side liquid supply port 31 is formed in the discharge-side casing 4B. Lubricant can be supplied to the second discharge side bearing 8 provided.
- a second suction-side fluid supply port 32 is formed outside the rotor radial direction of the suction-side casing 4D, and a second suction-side fluid supply port 32 is housed in the second suction-side bearing housing space 16 of the main casing 4A.
- a third liquid supply port 33 is provided toward the suction side bearing 7 , and the third liquid supply port 33 is connected to the second suction side via a second liquid supply path 34 formed inside the casing 4 . It communicates with the liquid supply port 32 . Accordingly, by injecting the lubricating liquid into the screw compressor 1 through the second suction-side liquid feeding port 32, the lubricating liquid is injected into the third liquid feeding port 33 via the second liquid feeding path 34. to the second suction side bearing 7.
- the second suction side fluid supply port 32 is supplied with the fluid.
- the lubricating fluid supplied to the second suction side bearing 7 via the second fluid supply path 34 flows out to the suction space 14 via the second bearing communication space 18, and then from the suction port 13. Together with the working medium that has flowed into the suction space 14, it is conveyed to the working chamber.
- the agitation loss of the lubricating liquid in the second suction side bearing 7 is reduced by the same mechanism as the agitation loss of the lubricating liquid in the first suction side bearing 5. can be suppressed.
- the second working chamber liquid supply port 30, the second suction side liquid supply port 32 and the second discharge side liquid supply port 31 are the same as the first working chamber liquid supply port 22 and the first working chamber liquid supply port 22 described above with reference to FIG. It may be formed separately from the corresponding one of the suction side liquid supply port 23 and the first discharge side liquid supply port 24, or may be provided at the same location, that is, the first and second The working chamber liquid supply ports 22, 30, the first and second suction side liquid supply ports 23, 32, and the first and second discharge side liquid supply ports 24, 31 may be the same.
- FIG. 5 shows the external route of the lubricating liquid injected into the screw compressor 1 of this embodiment.
- the lubricating fluid injected into the screw compressor 1 is discharged from the discharge port 10 (FIGS. 2 and 4) while being mixed with the working medium compressed by the screw compressor 1.
- FIG. The lubricating fluid is separated from the compressed working medium by the oil separator 40, cooled by the cooler 41, and then passed through the oil filter (and check valve) 42 to the first and second working chambers. It is supplied to liquid supply ports 22 and 30 (FIGS. 2 and 4), and injected into the working chamber through these first and second working chamber liquid supply ports 22 and 30, respectively.
- the lubricating fluid After passing through the oil filter 42, the lubricating fluid is branched into the first and second suction side fluid supply ports 23 and 32 (FIGS. 2 and 4), the first and second discharge side fluid supply ports 24, 31 (FIGS. 2 and 4), and through the first suction side liquid supply port 23, the shaft sealing member 21 (FIG. 2) in the shaft sealing space 20 (FIG. 2) and the first suction side First suction side bearing 5 in bearing housing space 15 (Fig. 2), second suction side bearing 7 in second suction side bearing housing space 15, first discharge side bearing housing space 9A (Fig. 1)
- the branching of the lubricating fluid is not limited to the outside of the screw compressor 1 as shown in FIG.
- the first suction-side bearing housing space 15 housing the first suction-side bearing 5 and the shaft seal member 21 are provided.
- the shaft sealing space 20 is separated from the shaft sealing space 20 by the suction side partition wall 4 ⁇ /b>C. Since the liquid supply port 26 is provided independently, it is possible to independently supply suitable amounts of lubricating liquid to the shaft sealing member 21 and the first suction side bearing 5 respectively. Therefore, according to the screw compressor 1, it is possible to suppress the churning loss of the lubricating liquid at the first suction side bearing 5 caused by the excessive supply of the lubricating liquid to the first suction side bearing 5. Therefore, a highly reliable and highly efficient screw compressor can be realized.
- the second liquid supply port 26 is formed so as to supply the lubricating liquid to the first suction side bearing 5 from the male rotor 2 side. It is not necessary for all of the lubricating fluid supplied to the side bearing 5 to pass through the rolling element raceways of the rotating first suction side bearing 5 . Therefore, according to the screw compressor 1, the agitation loss of the lubricating fluid in the first suction side bearing 5 is small, and a higher efficiency screw compressor can be realized.
- FIG. 6 shows a vertical cross section of a screw compressor 50 according to a second embodiment.
- the present screw compressor 50 is configured in a casing 51 (a suction side casing 50D, a suction side partition wall 50C and a main casing 50A) so that a bypass communication passage 52 communicates between the shaft seal space 20 and the bore 12. It differs from the screw compressor 1 of the first embodiment.
- the main casing 50A is provided with the first working chamber fluid supply port 22 (FIG. 2) and a path communicating between the first working chamber fluid supply port 22 and the bore 12.
- the lubricating fluid supplied to the shaft sealing member 21 in the shaft sealing space 20 is discharged into the bore 12 through the bypass communication passage 52 .
- the first and second suction side bearings 5 and 7 and the shaft sealing member 21 are provided in the same manner as the screw compressor 1 of the first embodiment. While supplying necessary and sufficient lubricating liquid to the bearings 5 and 7 on the suction side, agitation loss can be kept low. Therefore, according to this embodiment as well, a highly reliable and highly efficient screw compressor can be provided.
- FIG. 7 shows a vertical cross section of a screw compressor 60 according to a third embodiment.
- This screw compressor 60 is configured in the same manner as the screw compressor 1 of the first embodiment except that the position of the second liquid supply port 62 is different.
- the second liquid supply port 62 is provided in the suction side partition wall 60C so that the lubricating liquid can be supplied to the first suction side bearing 5 from the suction side partition wall 60C side.
- a second branch of the first liquid supply path 63 is formed in the suction side casing 60D and the suction side partition wall 60C so as to communicate between the first liquid supply port 62 and the first suction side liquid supply port 23.
- a path 63B is provided.
- the lubricating liquid supplied from the second liquid supply port 62 to the first suction side bearing 5 passes through the rolling element raceway of the rotating first suction side bearing 5.
- the agitation loss in the first suction side bearing 5 is greater than in the screw compressor 1 according to the first embodiment.
- the first liquid supply port 62 is provided on the suction side partition wall 60C side with respect to the first suction side bearing 5, the first Since it is not necessary to provide a portion for providing a liquid supply port in the main casing 4A, and the opening area of the first bearing communication space 17 can be increased accordingly, the rolling element raceway portion of the first suction side bearing 5 The lubricating liquid is less likely to stay in the first suction side bearing 5, and the agitation loss in the first suction side bearing 5 can be kept low.
- the screw compressor 60 of the present embodiment having the above configuration, as in the screw compressor 1 of the first embodiment, the first suction side bearing 5 and the shaft sealing member 21 are sufficiently Agitation loss in the first suction side bearing 5 can be kept low while supplying a sufficient amount of lubricating fluid. Therefore, according to this embodiment as well, a highly reliable and highly efficient screw compressor can be provided.
- FIG. 8 shows a vertical cross section of a partial configuration of a screw compressor 70 according to a fourth embodiment.
- the screw compressor 70 part of the lubricating fluid supplied from the second fluid supply port 26 to the first suction side bearing 5 is applied to the rolling element raceway of the rotating first suction side bearing 5.
- the lubricating fluid passing through the rolling element raceway of the first suction side bearing 5 quickly flows into the shaft seal space 20 through the through hole 72, the first suction side bearing 5
- the lubricating liquid is less likely to stay in the rolling element raceway, and as a result, the agitation loss in the first suction side bearing 5 can be kept lower than in the screw compressor 1 of the first embodiment.
- the screw of the first embodiment can Compared to the compressor 1, the agitation loss in the first suction side bearing 5 can be kept low. Therefore, according to this embodiment, it is possible to provide a highly reliable and highly efficient screw compressor.
- liquid supply path (first branch path) communicating with the first liquid supply port and the liquid supply path (second branch path) communicating with the second liquid supply port 2) are branched inside the casing, but the present invention is not limited to this, and these fluid supply paths are originally formed separately separately formed).
- the second liquid supply port 62 is provided in the suction side partition wall 60C so that the lubricating liquid can be supplied to the first suction side bearing 5 from the suction side partition wall 60C side.
- the present invention is not limited to this, and the third liquid supply port 26 described above with reference to FIG. may be provided on the suction side partition wall 60C.
- the present invention can be widely applied to various configurations of screw compressors for compressing a working medium.
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Abstract
Description
図1及び図2は、第1の実施の形態によるスクリュー圧縮機1を示す。図1は図2におけるC-C矢視図(水平断面図)であり、図2は図1におけるA-A矢視図(垂直断面図)である。
図2との対応部分に同一符号を付して示す図6は、第2の実施の形態によるスクリュー圧縮機50の垂直断面を示す。本スクリュー圧縮機50は、バイパス連通路52が軸封空間20及びボア12間を連通するようにケーシング51(吸込側ケーシング50D、吸込側隔壁50C及びメインケーシング50A)内に構成されている点が第1の実施の形態のスクリュー圧縮機1と相違する。
図2との対応部分に同一符号を付して示す図7は、第3の実施の形態によるスクリュー圧縮機60の垂直断面を示す。本スクリュー圧縮機60は、第2の給液口62の位置が異なる点を除いて第1の実施の形態のスクリュー圧縮機1と同様に構成されている。
図3との対応部分に同一符号を付して示す図8は、第4の実施の形態によるスクリュー圧縮機70の一部構成の垂直断面を示す。本スクリュー圧縮機70は、第1の実施の形態のスクリュー圧縮機1に比べて吸込側隔壁71に形成された雄ロータ2の吸込側軸部2Bを挿通させるための貫通孔72が大きく形成されている点を除いて第1の実施の形態のスクリュー圧縮機1と同様に構成されている。
なお上述の第1~第4の実施の形態においては、雄ロータ2の吸込側軸部のみが動力源としてのモータの回転軸と接続されている場合について述べたが、本発明はこれに限らず、雄ロータ2に代えて又は加えて雌ロータ3の吸込側軸受が動力源の回転軸と接続された形態のスクリュー圧縮機についても本発明を適用することができる。
Claims (6)
- 作動媒体を圧縮するスクリュー圧縮機において、
前記作動媒体を吸い込み、圧縮して吐出する第1及び第2のスクリューロータと、
動力源の回転軸に一端側が連結された前記第1のスクリューロータの当該一端側を回転自在に支持する第1の軸受と、
前記第1のスクリューロータ及び前記第1の軸受が収納されたケーシングと、
前記ケーシング内部における前記第1の軸受に対して前記第1のスクリューロータの歯形部の反対側に配置され、前記動力源の前記出力軸と連結された前記第1のスクリューロータの軸部が挿通する前記ケーシングの貫通孔をシールする軸封部材と、
前記ケーシング内部において前記第1の軸受及び前記軸封部材間を隔離する隔壁と、
前記ケーシングに設けられ、前記第1の軸受に潤滑液を給液するための第1の給液口、及び、前記軸封部材に前記潤滑液を供給するための第2の給液口を有する給液経路と
を備えることを特徴とするスクリュー圧縮機。 - 前記軸封部材は、前記ケーシングに設けられた第1の空間内に配設され、
前記第1の軸受は、前記ケーシングに設けられた第2の空間内に配設され、
前記動力源の前記回転軸に一端側が連結された前記スクリューロータにおける歯が形成された歯形部は、前記ケーシングに設けられた第3の空間内に収納され、
前記第1及び第2の空間は、前記隔壁により隔離され、
前記第1の空間がバイパス連通路を介して前記第3の空間と連通され、
前記第1の空間に供給された前記潤滑液が前記バイパス通路を介して前記第3の空間に排出される
ことを特徴とする請求項1に記載のスクリュー圧縮機。 - 前記第1の給液口は、
前記スクリューロータ側から前記第1の軸受に前記潤滑液を給液するよう前記ケーシングに形成された
ことを特徴とする請求項1に記載のスクリュー圧縮機。 - 前記第2の空間及び前記第3の空間を連通する連通空間を備え、
前記第1の軸受に給液された前記潤滑液が前記連通空間を介して前記第3の空間に排出される
ことを特徴とする請求項2に記載のスクリュー圧縮機。 - 前記第1及び第2のスクリューロータが水平となるように設置したときに、前記連通空間の最下端部が前記第1の軸受の外輪内径の下端位置よりも低くなるように前記連通空間が形成された
ことを特徴とする請求項4に記載のスクリュー圧縮機。 - 前記第1のスクリューロータにおける前記動力源の前記回転軸が連結された前記一端側と同じ前記第2のスクリューロータの一端側を回転自在に支持する第2の軸受と、
前記ケーシングに設けられ、前記第2の軸受に前記潤滑液を給液するための第3の給液口とを備え、
前記第3の給液口は、
前記スクリューロータ側から前記第1の軸受に前記潤滑液を給液するよう前記ケーシングに形成された
ことを特徴とする請求項1に記載のスクリュー圧縮機。
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JP2002021758A (ja) | 2000-07-11 | 2002-01-23 | Hitachi Ltd | 油冷式スクリュー圧縮機 |
WO2007000815A1 (ja) * | 2005-06-29 | 2007-01-04 | Mayekawa Mfg. Co., Ltd | 二段スクリュー圧縮機の給油方法、装置及び冷凍装置の運転方法 |
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JP2002021758A (ja) | 2000-07-11 | 2002-01-23 | Hitachi Ltd | 油冷式スクリュー圧縮機 |
WO2007000815A1 (ja) * | 2005-06-29 | 2007-01-04 | Mayekawa Mfg. Co., Ltd | 二段スクリュー圧縮機の給油方法、装置及び冷凍装置の運転方法 |
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