CN109113990A - Screw compressor - Google Patents
Screw compressor Download PDFInfo
- Publication number
- CN109113990A CN109113990A CN201810654524.0A CN201810654524A CN109113990A CN 109113990 A CN109113990 A CN 109113990A CN 201810654524 A CN201810654524 A CN 201810654524A CN 109113990 A CN109113990 A CN 109113990A
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- China
- Prior art keywords
- mentioned
- oil feed
- supplementary bearing
- feed pump
- pump
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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
- F04C18/02—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
- 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
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The present invention provides a kind of screw compressor, inhibits the abrasion of the internal rotor for constituting oil feed pump and pump cover, realizes that the reliability of screw compressor improves.Screw compressor have set on supplementary bearing shell and be freely and rotatably supported rotary shaft countershaft portion supplementary bearing.In addition, having: oil feed pump is installed on supplementary bearing shell, and has pump case and be located at the intracorporal internal rotor of the pump case and outer rotor；Multiple carrying bolts install the pump case of oil feed pump relative to supplementary bearing shell in the state of maintaining the gap in axial gap and radial direction；And elastic support member, it is set between above-mentioned supplementary bearing shell and above-mentioned pump case in the mode surrounded around multiple above-mentioned carrying bolts.
Description
Technical field
The present invention relates to the screw compressors for having oil feed pump, more particularly to processing HFC class refrigerant, air, titanium dioxide
The screw compressor of the natural kinds such as carbon refrigerant, other compressibility gases inhibits to constitute the internal rotor of above-mentioned oil feed pump, pump cover etc.
Abrasion.
Background technique
Screw compressor is widely used in various fields as the compressor of freezing air conditioner equipment.In addition, passing through
For preventing the energy conservation limitation of global warming, the high efficiency of compressor is hastily improved.On the other hand, even if very harsh
Under conditions of operate screw compressor, it is also necessary to fatal damage will not be generated in sliding part.In addition, in recent years, in order to low
Cost, the small-sized of screw compressor, high speed, base bearing, supplementary bearing sliding bearing exploitation it is also very urgent.
As recorded in Japanese Unexamined Patent Publication 2015-203337 bulletin (patent document 1), in screw compressor, rolling is utilized
Bearing constitutes the structure of base bearing, supplementary bearing in order to these bearing fuel feeding and equipped with oil feed pump.The oil being discharged from the oil feed pump
(lubricating oil) is supplied a part to above-mentioned supplementary bearing by being formed in the oily access of rotary shaft.Remaining most oil passes through
Above-mentioned oil access is conveyed from the crank portion upper end of rotary shaft into the rotation boss portion of rotating vortex, is being had lubricated from there
After the swivel bearing for stating rotating vortex, to the above-mentioned base bearing supply being made of rolling bearing.In this way, in above patent document 1
Structure in using series connection fuel system.
But in screw compressor, in the case where being made of above-mentioned base bearing, above-mentioned supplementary bearing rolling bearing, such as
Fruit cannot then have the reliability for being unable to ensure these bearing portions reliably to the lubricating oil of each bearing portion supply full amount
Big project.In order to solve the project, it is necessary to for point from the oily access at the center for being set to rotary shaft to each bearing portion DFF Direct Fuel Feed
With fuel system.
In addition, using above-mentioned distribution fuel system, compared with using the case where connecting fuel system, it is necessary to
Increase the fuel delivery from above-mentioned oil feed pump, if the volume of oil feed pump (maximum discharge volume) is not set as twice or more,
Then necessary fuel delivery is supplied without each bearing portion of normal direction.If in order to realize that fuel delivery increases and realizes that the volume of oil feed pump increases,
The suction side pressure of the oil feed pump and the pressure difference of discharge lateral pressure increase.
Above-mentioned oil feed pump is made of internal rotor, outer rotor, pump cover and the pump case for storing these etc., which utilizes
The engaging members such as bolt are fixed on the shell being fixed on lower frame (sub-frame).In addition, due to the component for constituting compressor
Manufacturing tolerance, the inclination of assembling tolerance when assembled and the rotary shaft generated in the running, vibration, above-mentioned internal rotor and outer
Dimensional tolerance of each component etc. is considered between rotor and said pump cover and gap is set.
Existing technical literature
Patent document 1: Japanese Unexamined Patent Publication 2015-203337 bulletin
In above patent document 1, the leakage of oil becomes more if increasing above-mentioned gap, and fuel feeding efficiency is caused to decline.In addition,
If reducing above-mentioned gap to improve fuel feeding efficiency, in order to which above-mentioned gap is arranged, above-mentioned internal rotor and outer rotor are being operated
When inclination and strongly contacted with said pump cover, exist and generate abrasion and lead to the project of reliability decrease.
It is moved freely in addition, also being described in above patent document 1 with the axial direction that said pump can be made to cover on rotary shaft
Mode using cover pressing piece pass through the elastomeric support pump cover.
If constituting in this way, the axial gap between internal rotor and outer rotor and pump cover can be eliminated, therefore can improve
Fuel feeding efficiency (volume efficiency).If but in this way constitute, it is independent of rotation speed total to pump cover, internal rotor and outer rotor
It is to be contacted with said pump cover.Therefore, if the volume enlargement of adjoint oil feed pump, suction side pressure and the discharge lateral pressure of oil feed pump
Pressure difference increases, then said pump cover, above-mentioned internal rotor and above-mentioned outer rotor cause abnormal wear, or presence to lead to reliability
The project of decline.In order to utilize above-mentioned elastomeric support said pump cover, above-mentioned cover pressing piece is needed, is deposited in terms of cost
In the project for becoming high price.
Summary of the invention
The purpose of the present invention is to provide abrasion and the realizations of a kind of internal rotor and pump cover that can inhibit to constitute oil feed pump
The screw compressor that reliability improves.
To achieve the goals above, the present invention is a kind of screw compressor, is had: closed container；It is installed on the closed appearance
The main frame and sub-frame of device；Fixed scroll, the overlapping portion with end plate He the vortex shape for standing up the end plate, and
It is installed on above-mentioned main frame；Rotating vortex, the overlapping portion with end plate He the vortex shape for standing up the end plate are and above-mentioned
Fixed scroll engages and forms discharge chambe；Rotary shaft with the cam pin portion that the rotating vortex is rotated；It is set to
The back side of the above-mentioned end plate of above-mentioned rotating vortex has the rotation boss portion of the swivel bearing for the insertion of above-mentioned cam pin portion；
Set on above-mentioned main frame and be freely and rotatably supported above-mentioned rotary shaft main shaft part base bearing；And set on being installed on above-mentioned pair
The supplementary bearing shell of frame and be freely and rotatably supported above-mentioned rotary shaft countershaft portion supplementary bearing, which is characterized in that have: peace
Loaded on above-mentioned supplementary bearing shell and with pump case and the oil feed pump for being located at the intracorporal internal rotor of the pump case and outer rotor；Relatively
The pump case of above-mentioned oil feed pump is installed in the state of maintaining the gap in axial gap and radial direction in above-mentioned supplementary bearing shell
Multiple carrying bolts of body；Above-mentioned supplementary bearing shell and said pump are set in the mode surrounded around multiple above-mentioned carrying bolts
Elastic support member between shell.
It is another feature that a kind of screw compressor, has: closed container；It is installed on the closed container
Main frame and sub-frame；Fixed scroll, the overlapping portion with end plate He the vortex shape for standing up the end plate, and pacify
Loaded on above-mentioned main frame；Rotating vortex, the overlapping portion with end plate He the vortex shape for standing up the end plate are and above-mentioned solid
Determine vortex engages and forms discharge chambe；Rotary shaft with the cam pin portion that the rotating vortex is rotated；Set on upper
The back side of the above-mentioned end plate of rotating vortex is stated, there is the rotating wheel hub of the swivel bearing for the insertion of above-mentioned cam pin portion；If
In above-mentioned main frame and be freely and rotatably supported above-mentioned rotary shaft main shaft part base bearing；And set on being installed on above-mentioned secondary frame
The shell of the supplementary bearing of frame and be freely and rotatably supported above-mentioned rotary shaft countershaft portion supplementary bearing, which is characterized in that have: peace
Loaded on above-mentioned supplementary bearing shell and with pump case and the oil feed pump for being located at the intracorporal internal rotor of the pump case and outer rotor；Relatively
The pump case of above-mentioned oil feed pump is installed in the state of maintaining the gap in axial gap and radial direction in above-mentioned supplementary bearing shell
Multiple carrying bolts of body；And in a circumferential direction set on the above-mentioned supplementary bearing shell of the inner circumferential side of multiple above-mentioned carrying bolts
With the elastic support member between above-mentioned pump case.
Effect of the invention is as follows.
According to the present invention, have to be inhibited and constitute the abrasion of the internal rotor and pump cover of oil feed pump and realize reliability
The effect of the screw compressor of raising.
Detailed description of the invention
Fig. 1 is the longitudinal section view for indicating the embodiment one of screw compressor of the invention.
Fig. 2 is the major part enlarged cross-sectional view near oil feed pump shown in FIG. 1.
Fig. 3 is the major part enlarged cross-sectional view near carrying bolt shown in Fig. 2.
Fig. 4 is the figure for illustrating the embodiment two of screw compressor of the invention, is and the comparable figure of Fig. 3.
Fig. 5 is the figure for illustrating the embodiment three of screw compressor of the invention, is and the comparable figure of Fig. 3.
Fig. 6 is the figure for illustrating the example IV of screw compressor of the invention, is and the comparable figure of Fig. 2.
Fig. 7 is the top view of oil feed pump shown in fig. 6.
Fig. 8 is the figure for illustrating the embodiment five of screw compressor of the invention, is and the comparable figure of Fig. 2.
Fig. 9 is the figure for illustrating the embodiment six of screw compressor of the invention, is and the comparable figure of Fig. 2.
Figure 10 is the longitudinal section view for indicating existing screw compressor.
Figure 11 is the figure for illustrating the operating principle of oil feed pump.
Figure 12 is the chart for indicating the relationship of speed and discharge pressure ratio of oil feed pump.
In figure: 1-screw compressor, 2-compression mechanical parts, 3-driving portions, 21,22-bolts, 100-closed containers,
101-rotary shafts, 101a-main shaft part, 101b-countershaft portion, 101c-cam pin portion, 101d-sliding bearing, 102-oil are logical
Road (fuel supply path), 102a, 102b-branch oil access, 103-swivel bearings, 104-base bearings, 105-supplementary bearings,
106-oil feed pumps, 106a-internal rotor, 106aa-hole, 106b-outer rotor, 106c-suction inlet, 106d-outlet,
106e-pump case, 106f-pump cover, 106g-through hole, 106h-oil discharge slot (oily discharge path), 107-motor,
107a-rotor, 107b-stator, 110-fixed scrolls, 110a-vortex shape overlapping portion, 110b-end plate, 110c-discharge
Mouth, 120-rotating vortex, 120a-vortex shape overlapping portion, 120b-end plate, 120c-rotation boss portion, 120d-rotation are convex
Platform end surface, 130-discharge chambes, 131-oily reservoirs, 133-supplementary bearing shells, 133a, 133b, 133c, 133d-groove,
134-cruciform joints, 136-discharge spaces, 137-sub-frames (lower frame), 138-carrying bolts, 138a-large-diameter portion,
140-suction lines, 150-discharge pipes, 160-frames (main frame), 161-endless grooves, 170-slots, 172-seal members,
180-back pressure chambers, 181-hyperbaric chambers, 184-oil exit pipes, 190-elastic support members, 191,191a-resin ring, 192,
192a, 192b-wave plate gasket, 193,193a-O ring, 194-compression helical springs, 204-sliding bearings.
Specific embodiment
In the following, being described with reference to the specific embodiment of screw compressor of the invention.In the various figures, it is labelled with identical
The part of symbol indicates same or equivalent part.
[embodiment one]
Illustrate the embodiment one of screw compressor of the invention using FIG. 1 to FIG. 3.Fig. 1 is the whirlpool for indicating the present embodiment one
The longitudinal section view of compressor is revolved, Fig. 2 is the major part enlarged cross-sectional view near oil feed pump shown in FIG. 1, and Fig. 3 is shown in Fig. 2
Carrying bolt near major part enlarged cross-sectional view.
Firstly, illustrating the overall structure of the screw compressor of the present embodiment one using Fig. 1.
Screw compressor 1 is configured to for compression mechanical part 2 and driving portion 3 etc. being accommodated in closed container 100.
Compression mechanism section 2 is made of fixed scroll 110, rotating vortex 120 and frame (main frame) 160 etc..
Above-mentioned fixed scroll 110 has end plate 110b and vertically stands up the vortex shape overlapping portion of end plate 110b
110a is formed with outlet 110c in the overlapping portion central portion side of above-mentioned end plate 110b.In addition, the peripheral part benefit of end plate 110b
Said frame 160 is fixed on multiple bolts 21.
Above-mentioned rotating vortex 120 has end plate 120b and vertically stands up the vortex shape overlapping portion of end plate 120b
120a is formed with rotation boss portion 120c in the back side of above-mentioned end plate 120b, sets in the inner peripheral surface of rotation boss portion 120c
It is equipped with swivel bearing 103.In addition, 120d is the end face (rotation boss end surface) of above-mentioned rotation boss portion 120c.
Engage above-mentioned fixed scroll 110 and above-mentioned rotating vortex 120 to form discharge chambe 130, which passes through
Above-mentioned rotating vortex 120 is rotated, and volume reduces, and carries out compressed action.In the compressed action, with above-mentioned rotation
Turn the rotary motion of vortex 120, the movement fluid such as refrigerant gas is sucked by suction line 140 to above-mentioned discharge chambe 130, should
The movement fluid being inhaled into is by compression travel from the above-mentioned outlet 110c of above-mentioned fixed scroll 110 is formed in closed container
Discharge space 136 in 100 is discharged.
Later, compressed refrigerant gas is by being formed in the outer peripheral surface of above-mentioned fixed scroll 120 and said frame 160
Above-mentioned driving portion 3 side flowing of the access (not shown) into above-mentioned closed container 100, from there by discharge pipe 150 to close
Close the discharge such as refrigerating cycle outside container 100.Therefore, the space in above-mentioned closed container 100 is remained into discharge pressure.
The above-mentioned driving portion 3 that above-mentioned rotating vortex 120 is rotated includes by rotor 107a and stator 107b structure
At motor 107 and rotary shaft 101 etc..In addition, above-mentioned rotating vortex 120 is using as the main component of the anti-locking mechanism of rotation
Cruciform joint 134 prevent from being rotated from transferring.
Above-mentioned cruciform joint 134 is set to the back pressure chamber 180 by being formed between above-mentioned rotating vortex 120 and said frame 160.
In addition, being formed with the two group keys orthogonal with above-mentioned cruciform joint 134, one group of key is slided in the keyway for being formed in said frame 160,
Remaining one group in the keyway sliding for being configured to the back side of above-mentioned rotating vortex 120.
Above-mentioned rotary shaft 101 has main shaft part 101a, countershaft portion 101b and cam pin portion 101c, above-mentioned main shaft part 101a
It is freely and rotatably supported using the base bearing 104 for being set to said frame 160, above-mentioned countershaft portion 101b, which is utilized, is set to supplementary bearing shell
133 supplementary bearing 105 is freely and rotatably supported.
In addition, above-mentioned supplementary bearing shell 133 is installed on sub-frame (lower frame) 137, the sub-frame using multiple bolts 22
The lower part of above-mentioned closed container 100 is fixedly welded on using crease.In addition, the bottom in above-mentioned closed container 100 is formed with
Oily reservoir 131, above-mentioned base bearing 104 are configured at 2 side of compression mechanical part of above-mentioned motor 107, and above-mentioned supplementary bearing 105 configures
In 131 side of above-mentioned oily reservoir.
The above-mentioned cam pin portion 101c insertion of above-mentioned rotary shaft 101 is located at the rotation boss portion of above-mentioned rotating vortex 120
Above-mentioned swivel bearing 103 in 120c.Therefore, the above-mentioned cam pin portion 101c of rotary shaft 101 is relative to above-mentioned swivel bearing 103
It can move in rotary axis direction and rotatably freely engage.
In the present embodiment, make respectively on above-mentioned base bearing 104, above-mentioned supplementary bearing 105 and above-mentioned swivel bearing 103
Use sliding bearing.In addition, to these swivel bearings 103, base bearing 104 and supplementary bearing 105 fuel feeding by being formed in above-mentioned rotation
The oil feed pump 106 of oily access (fuel supply path) 102 and the lower end side for being located at above-mentioned rotary shaft 101 in shaft 101 carries out.
The above-mentioned oil measure for the lower space for being stored in closed container 100 is attracted to deposit using above-mentioned oil feed pump 106 that is, being formed with
The oil (lubricating oil) in portion 131 and by above-mentioned oily access to above-mentioned swivel bearing 103 for the path of oil supply, by from oily access
The branch oil access 102a of 102 branches is to above-mentioned supplementary bearing 105 for the path of oil supply and by from above-mentioned oily 102 branch of access
Branch oil access 102b to above-mentioned base bearing 104 for the path of oil supply.
The above-mentioned back pressure chamber 180 for being formed in the back side of above-mentioned rotating vortex 120 is by above-mentioned fixed scroll 110, above-mentioned
Rotating vortex 120 and said frame 160 are surrounded and the space of formation.In addition, in above-mentioned rotation boss portion 120c substantially for guidance
The hyperbaric chamber 181 of the oil of discharge pressure.Above-mentioned back pressure chamber 180 is divided with above-mentioned hyperbaric chamber 181 by sealing mechanism pressure
From.
Above-mentioned sealing mechanism is by being configured to and being located at the above-mentioned rotation boss portion 120c at the back side of above-mentioned rotating vortex 120
The endless groove 161 of the end face portion of end face 120d opposed said frame 160,172 structure of seal member for being disposed in the endless groove 161
At.Above-mentioned rotation boss end surface 120d is the sealing surface contacted with above-mentioned seal member 172.In addition, being configured to lubricate
The sliding part that above-mentioned cruciform joint 134 in above-mentioned back pressure chamber 180 waits, above-mentioned sealing mechanism are also equipped with slit-shaped, hole shape
Deng slot 170, which is formed in above-mentioned rotation boss end surface 120d, and makes above-mentioned across above-mentioned seal member 172
Hyperbaric chamber 181 and above-mentioned back pressure chamber 180 be continuous or accompanying rotation is vortexed 120 rotary motion and make above-mentioned hyperbaric chamber 181 and upper
Back pressure chamber 180 is stated intermittently to be connected to.
Therefore, the oil for the high pressure being discharged from above-mentioned swivel bearing 103, above-mentioned base bearing 104 is close by above-mentioned seal member 172
Envelope, in order to inhibit the outflow to above-mentioned 180 side of back pressure chamber, above-mentioned hyperbaric chamber 181 is the pressure space of substantially discharge pressure or so.
That is, the oil due to the substantially discharge pressure in closed container 100 is boosted by the pumping action of oil feed pump 106, passing through rotation
By depressurization when shaft holds the clearance portions such as 103, base bearing 104, but the substantially discharge pressure of above-mentioned hyperbaric chamber 181.
In addition, 204 are provided at the sliding bearing of the flange part 101d of said frame 160 and the above-mentioned rotary shaft 101 of support,
184 be for the oil being discharged from above-mentioned swivel bearing 103 and above-mentioned base bearing 104 to be deposited the row that portion 131 guides to above-mentioned oil measure
Oil pipe, 138 be the carrying bolt for above-mentioned oil feed pump 106 to be supported in above-mentioned supplementary bearing shell 133.
Here, illustrating the structure of existing screw compressor using Figure 10.Figure 10 indicates existing screw compressor
Longitudinal section view illustrates to omit, with difference about the screw compressor same section with the embodiment of the present invention one shown in FIG. 1
Part centered on be illustrated.In addition, marking the same symbol to Fig. 1 same or equivalent part.
In existing screw compressor shown in Fig. 10, base bearing 104, supplementary bearing 105 use rolling bearing.In addition,
The oil being discharged from oil feed pump 106 is fed into swivel bearing 103 by the oily access 102 of rotary shaft 101.In addition, being from above-mentioned
The a part for the oil that swivel bearing 103 is discharged passes through the part of seal member 172, is supplied to back pressure chamber 180, remaining more than half oil
The series connection fuel system supplied to the above-mentioned base bearing 104 being made of rolling bearing.
In addition, being fed through branch oil access 102a to the above-mentioned supplementary bearing 105 being made of rolling bearing flows through above-mentioned oil
A part of the oil of access 102.
In contrast, in the present embodiment shown in Fig. 1, not only swivel bearing 103, base bearing 104 and supplementary bearing 105
Using sliding bearing, therefore, if not securely feeding the oil of full amount to each bearing portion 103~105, it is unable to ensure axis
Hold reliability.Therefore, as above-mentioned in the present embodiment, to distribute to come in parallel from oily access 102 to each bearing portion 103~105
From the distribution fuel system of the oil of above-mentioned oily access 102.In the case where the distribution fuel system, need than above-mentioned series connection fuel feeding
Mode increases supply amount, therefore, if being not existing twice shown in Fig. 10 or more by the volume settings of oil feed pump 106,
It is unable to ensure the necessary fuel delivery to each bearing 103~105.
In this way, being illustrated using Figure 11 and Figure 12 for the cost effective and small-sized of screw compressor, high speed, with each axis
The sliding bearing that holds and need to realize that the volume of oil feed pump 106 increases, as it does so, the discharge pressure of oil feed pump 106 and sucking are pressed
The case where pressure difference of power increases.Figure 11 is the figure for illustrating the operating principle of oil feed pump, and Figure 12 is the rotary frequency for illustrating oil feed pump
The chart of the relationship of rate and discharge pressure ratio.
As shown in figure 11, as above-mentioned oil feed pump 106, the gear for the annulus shape for being commonly referred to as remaining pendulum-type pump is used
Pump.As shown in figure 11, tooth form is internal rotor 106a by being formed by remaining pendulum curve and is engaged with and is driven remaining pendulum-type pump
The structure for the annulus shape that dynamic outer rotor 106b is constituted.Above-mentioned internal rotor 106a is formed with hole 106aa in its center, at this
Lower end and the engaging of rotary shaft 101 (referring to Fig.1) are inserted into the 106aa of hole, if above-mentioned rotary shaft 101 rotates, internal rotor
106a is also driven in rotation.With the rotation of internal rotor 106a, outer rotor 106b also rotates.
The number of teeth of above-mentioned internal rotor 106a is Z (being in this example embodiment 8), and the number of teeth of above-mentioned outer rotor 106b is Z+1 (at this
For 9) in example.In the relationship of the number of teeth, is engaged, be formed between these with outer rotor 106b by above-mentioned internal rotor 106a
The volume in space be gradually expanded together with the rotation of above-mentioned internal rotor 106a, be gradually reduced later.In the process of volume enlargement
In, oil is sucked from suction inlet 106c, during a reduced volume of, oil is discharged from outlet 106d, and be supplied to rotary shaft 101
Oily access 102.
The a part for being supplied to the oil of oily access 102 is supplied to supplementary bearing 105 from branch oil access 102a, later, outflow
Inner space between supplementary bearing shell 133 and rotary shaft 101, then by be formed in above-mentioned supplementary bearing shell 133 with it is above-mentioned
Axial gap between oil feed pump 106 is discharged to oily reservoir 131.
Figure 12 indicates the oil feed pump A of the volume as benchmark, relative to oil feed pump A volume for 2.5 times of oil feed pump B's
The relationship of the discharge pressure ratio of the speed and pump of pump.That is, in the case where making the speed 100Hz of oil feed pump A
Discharge pressure ratio is 1, and the discharge pressure ratio of each speed of oil feed pump A is indicated with curve A.In addition, curve B is indicated
The discharge pressure ratio of each speed of the oil feed pump B of 2.5 times of volume of the volume with oil feed pump A.
As shown in Fig. 12, with the speed of oil feed pump is declined, discharge pressure ratio declines.In addition, by volume
The discharge pressure ratio of 2.5 times of oil feed pump B is increased in the case where speed is 100Hz, discharge pressure ratio is
2.5, with speed is declined, discharge pressure ratio also declines, but it is possible to find out, if the row relative to oil feed pump A
Pressure ratio is identical speed out, then the discharge pressure ratio increase of oil feed pump B is about 2.5 times or so.
Above-mentioned oil feed pump A is for base bearing and supplementary bearing using rolling bearing, for the existing whirlpool for fuel system of connecting
The oil feed pump of compressor is revolved, above-mentioned oil feed pump B is for base bearing and supplementary bearing using sliding bearing, for distribution fuel system
The oil feed pump of the screw compressor of above-mentioned the present embodiment one.In the oil feed pump of the present embodiment one, base bearing and supplementary bearing are used
Sliding bearing needs to make the volume of oil feed pump to supply an adequate amount of oil to each sliding bearing as distribution fuel system
Existing 2.5 times or so.
Therefore, in the oil feed pump of the present embodiment, compared with the oil feed pump of existing screw compressor, the discharge of oil feed pump
Pressure gets higher 2.5 times or so, and the suction side pressure of oil feed pump and the pressure difference of discharge lateral pressure increase.
If it is the stress level of existing oil feed pump, then the abrasion loss for pumping cover, internal rotor and outer rotor is few, but if making
The volume of oil feed pump is the stress level of existing 2.5 times or so the present embodiment one, then the suction side pressure of oil feed pump and row
The pressure difference of lateral pressure increases out, as it does so, the vibration of oil feed pump increases, especially generates the phenomenon that pumping cover, internal rotor abnormal wear.
Then, the sheet of the abnormal wear of pump cover, internal rotor for can be avoided oil feed pump etc. is illustrated using Fig. 1, Fig. 2 and Fig. 3
The structure of the fuel feeding pumping section of embodiment one.
As shown in Figure 1, the inner peripheral surface in supplementary bearing shell 133 is inserted into 105 ground of the supplementary bearing setting being made of sliding bearing.
In addition, being equipped with oil feed pump 106 by carrying bolt 138 in the lower end of above-mentioned supplementary bearing shell 133.
Explain the structure of above-mentioned oil feed pump 106 in detail using Fig. 2 and Fig. 3.
The above-mentioned oil feed pump 106 of above-mentioned supplementary bearing shell 133 is installed on used referred to as remaining pendulum-type using as described in Figure 11
The gear pump of the annulus shape of pump.The remaining pendulum-type is pumped by internal rotor 106a and is engaged with and driven outer rotor 106b structure
At, above-mentioned internal rotor 106a as shown in Fig. 2, being formed with hole 106aa in its center, rotary shaft 101 is inserted into the 106aa of the hole
Lower end simultaneously engages.If above-mentioned rotary shaft 101 rotates, internal rotor 106a is driven in rotation, with the rotation of internal rotor 106a
Turn, outer rotor 106b also rotates.
The number of teeth of above-mentioned internal rotor 106a is (for example, 8) Z, and the number of teeth of above-mentioned outer rotor 106b is Z+1 (such as 9).Shape
Expand together with the rotation of above-mentioned internal rotor 106a at the volume in the space in above-mentioned internal rotor 106a between outer rotor 106b
After reduce, the oil of oily reservoir 131 (referring to Fig.1) is sucked from suction inlet 106c, oil is discharged from outlet 106d and is supplied to rotation
The oily access 102 of shaft 101.
Above-mentioned internal rotor 106a and outer rotor 106b are accommodated in pump case 106e.It is rotated certainly by pump case 106e
Such as support.The upper end surface side of these rotors 106a, 106b are across lesser gap by being fixed on the pump cover of above-mentioned pump case
106f covering.The pump cover 106f has the airtight function for keeping suction chamber (suction inlet 106c) and room (outlet 106d) being discharged
Energy.
Above-mentioned pump case 106e is maintaining the gap of axial gap s1 and radial direction relative to above-mentioned supplementary bearing shell 133
It is installed in the state of s2 by multiple carrying bolts 138, above-mentioned pump case 106e can be in above-mentioned axial gap s1 and above-mentioned radial direction
Gap s2 in the range of relative to above-mentioned supplementary bearing shell 133 be displaced.Therefore, even if due to the vibration of rotary shaft 101, effect
In the pressure imbalance etc. of internal rotor itself, internal rotor 106a inclination passes through the above-mentioned axial gap s1 and gap s2 of radial direction, pump
Shell 106e can also follow the inclination of above-mentioned internal rotor 106a and tilt.
That is, as shown in figure 3, making the through hole for being formed in the above-mentioned pump case 106e inserted with above-mentioned carrying bolt 138
The diameter of 106g is bigger than the outer diameter of large-diameter portion (root) 138a of above-mentioned carrying bolt 138, it is ensured that above-mentioned radial gap s2.Separately
Outside, by making the axial length a of the large-diameter portion 138a of above-mentioned carrying bolt 138 be formed than set on above-mentioned pump case 106e's
The axial length b long of above-mentioned through hole 106g, it is ensured that above-mentioned axial gap s1.
In addition, in the present embodiment one, to surround above-mentioned support spiral shell relative to each of multiple above-mentioned carrying bolts 138
Elastic support member 190 is arranged in mode around bolt 138 between above-mentioned supplementary bearing shell 133 and above-mentioned pump case 106e.
The elastic support member 190 is in the present embodiment as shown in figure 3, in the mode surrounded around above-mentioned carrying bolt 138 by ring
The resin ring 191 of shape and cricoid wave plate gasket 192 are constituted.
Above-mentioned resin ring 191 and wave plate gasket 192 are set to the ring-type for being formed in the lower end surface of above-mentioned supplementary bearing shell 133
Groove 133a, above-mentioned pump case 106e pressed downwards using above-mentioned wave plate gasket 192 by above-mentioned resin ring 191,
Above-mentioned oil feed pump 106 is flexibly supported by above-mentioned elastic support member 190 as a result,.
The a part for being supplied to the oil of oily access 102 from above-mentioned oil feed pump 106 is supplied to countershaft from branch oil access 102a
105 are held, later, flows out to the inner space between supplementary bearing shell 133 and rotary shaft 101, then by being formed in above-mentioned countershaft
The axial gap s1 held between shell 133 and above-mentioned oil feed pump 106 is discharged to oily reservoir 131.
As previously discussed, in the present embodiment, relative to above-mentioned supplementary bearing shell 133 maintain axial gap s1 and
The pump case 106e of above-mentioned oil feed pump 106 is installed, and in above-mentioned supplementary bearing shell 133 and confession in the state of radial gap s2
The elastic support member 190 being made of resin ring 191 and wave plate gasket 192 is set between the pump case 106e of oil pump 106.
Therefore, even if increasing with the volume of oil feed pump 106, high speed, the pressure of suction side pressure and discharge lateral pressure
Power difference increase, as rotor circumference direction pressure imbalance generate caused by internal rotor 106a inclination, by rotary shaft 101
The inclination of internal rotor 106a caused by vibrating increases, and can also be tilted by above-mentioned pump case 106e, absorb above-mentioned internal rotor 106a
Inclination.In addition, the vibration of the oil feed pump 106 as caused by the increase of the pressure difference of the volume increase with above-mentioned oil feed pump 106,
Vibrating as caused by the high speed rotation of rotary shaft can also be absorbed by above-mentioned elastic support member 190.
The pump cover 106f, internal rotor 106a, the outer rotor 106b that constitute oil feed pump 106 can be inhibited strongly to contact as a result, energy
The abrasion for reducing said pump cover 106f, internal rotor 106a etc., can improve the reliability of screw compressor.
In addition, also not needing the cover pressing piece of existing screw compressor documented by patent document 1, therefore can obtain low
The screw compressor of cost.
In addition, the material as above-mentioned resin ring 191, can be used polytetrafluoroethylene (PTFE) (PTFE), polyphenylene sulfide (PPS)
Or the superengineering plastics that the heat resistances such as polyether-ether-ketone (PEEK) are 150 DEG C or more.
In addition, in the present embodiment one, cricoid above-mentioned groove 133a is located at 133 side of supplementary bearing shell, but can also be with
It replaces, forms the above-mentioned groove for storing above-mentioned resin ring 191, wave plate gasket 192 in the upper surface of pump case 106e
133a。
[embodiment two]
Illustrate the embodiment two of screw compressor of the invention using Fig. 4.Fig. 4 is the figure for illustrating embodiment two, is and Fig. 3
Comparable figure is the major part enlarged cross-sectional view near carrying bolt 138.In the explanation of the present embodiment two, about with it is upper
One same section of embodiment stated illustrates to omit, and is illustrated centered on different parts.
In above-described embodiment one, elastic support member 190 is constituted by resin ring 191 and wave plate gasket 192, by fuel feeding
106 resilient support of pump is made of in supplementary bearing shell 133, but in the present embodiment two the circular O ring 193 of nitrile rubber
The O ring 193 is disposed between the pump case 106a of oil feed pump 106 and supplementary bearing shell 133 by above-mentioned elastic support member 190,
Flexibly support above-mentioned oil feed pump 106.
If describing in detail, also more to surround respectively in the lower end surface of supplementary bearing shell 133 even if then in the present embodiment two
Mode around a carrying bolt 138 is formed with cricoid groove 133a, is equipped with annulus in the cricoid groove 133a
The above-mentioned O ring 193 of shape.Above-mentioned pump case 106e is pressed downwards using above-mentioned O ring 193 as a result, utilizes above-mentioned 193 bullet of O ring
Property the above-mentioned oil feed pump 106 of support.
In addition, even if in the present embodiment, relative to above-mentioned supplementary bearing shell 133, the pump case of above-mentioned oil feed pump 106
106e is also installed in the state of maintaining the gap s2 of axial gap s1 and radial direction.Other structures and one phase of above-described embodiment
Together.
Even if also identical as above-described embodiment one in the present embodiment two, even if due to the pressure generated in oil feed pump 106
The inclination of uneven, rotary shaft 101 vibration, internal rotor 106a increases, and can tilt, can absorb above-mentioned also by pump case 106e
The inclination of internal rotor 106a.In addition, the oil feed pump as caused by the increase of the pressure difference of the volume increase with above-mentioned oil feed pump 106
106 vibration is vibrated as caused by the high speed rotation of rotary shaft and can also be absorbed by above-mentioned O ring 193.
The pump cover 106f, internal rotor 106a, the outer rotor 106b that constitute oil feed pump 106 can be inhibited strongly to contact as a result, subtracted
The abrasion of small said pump cover 106f, internal rotor 106a etc., can improve the reliability etc. of screw compressor, can obtain and embodiment one
Identical effect.
In addition, since only elastic support member 190 can be constituted by O ring 193, also there is knot according to the present embodiment two
Structure is simple and the effect that can manufacture cheaply than above-described embodiment one.
In addition, illustrating the example that cricoid above-mentioned groove 133a is set to 133 side of supplementary bearing shell, but replace,
Even if in the present embodiment two the above-mentioned groove of the above-mentioned O ring 193 of storage can also be formed in the upper surface of pump case 106e
133a。
[embodiment three]
Illustrate the embodiment three of screw compressor of the invention using Fig. 5.Fig. 5 is the figure for illustrating the present embodiment three, be with
The comparable figure of Fig. 3 is the major part enlarged cross-sectional view near carrying bolt 138.Even if being closed in the explanation of the present embodiment three
It also omits in the explanation with one same section of the above embodiments, is illustrated centered on different parts.
In the present embodiment three, above-mentioned elastic support member 190 is made of compression helical spring 194, by the compression spiral
Spring 194 is disposed between the pump case 106e of oil feed pump 106 and supplementary bearing shell 133, flexibly supports above-mentioned oil feed pump 106.
If describing in detail, then in the present embodiment three, in the lower end surface of supplementary bearing shell 133 to surround multiple supports respectively
Mode around bolt 138 forms slightly deep cricoid groove 133b, in addition, in the pump case 106e of oil feed pump 106
The part opposed with above-mentioned groove 133b also forms cricoid groove 133c.In addition, with across above-mentioned groove 133b's and 133c
Above-mentioned compression helical spring 194 is arranged in mode.Therefore, above-mentioned carrying bolt 138 is to be configured at above-mentioned compression helical spring 194
The state of inside.
Above-mentioned pump case 106e is pressed downwards using above-mentioned compression helical spring 194 as a result, utilizes above-mentioned compression spiral
Spring 194 flexibly supports above-mentioned oil feed pump 106.
In addition, even if in the present embodiment, the pump case 106e of above-mentioned oil feed pump 106 is also relative to above-mentioned supplementary bearing shell
133 install in the state of maintaining the gap s2 of axial gap s1 and radial direction.Other structures and above-described embodiment one, two-phase
Together.
Even if also identical as above-described embodiment one in the present embodiment three, even if due to the pressure generated in oil feed pump 106
The inclination of uneven, rotary shaft 101 vibration, internal rotor 106a increases, and can tilt, can absorb above-mentioned also by pump case 106e
The inclination of internal rotor 106a.In addition, the oil feed pump as caused by the increase of the pressure difference of the volume increase with above-mentioned oil feed pump 106
106 vibration is vibrated as caused by the high speed rotation of rotary shaft and can also be absorbed by above-mentioned compression helical spring 194.
The pump cover 106f, internal rotor 106a, the outer rotor 106b that constitute oil feed pump 106 can be inhibited strongly to contact as a result, energy
The abrasion for reducing said pump cover 106f, internal rotor 106a etc., can improve the reliability etc. of screw compressor, can obtain and embodiment
One identical effect.
In addition, even if in the present embodiment three, also due to elastic support member only can be constituted by compression helical spring 194
190, therefore also have the effect of that structure is simple and can manufacture cheaply than above-described embodiment one.
In addition, also forming above-mentioned cricoid groove 133c in the upper surface of pump case 106e, but only in the present embodiment three
So that the lower end of above-mentioned compression helical spring 194 is configured to flat face, then above-mentioned groove 133c is also not necessarily required.
[example IV]
Illustrate the example IV of screw compressor of the invention using Fig. 6 and Fig. 7.Fig. 6 is the figure for illustrating the present embodiment four,
Be with the comparable figure of Fig. 2, Fig. 7 is the top view of oil feed pump shown in fig. 6.Even if in the explanation of the present embodiment four, about with
The explanation of one same section of above-described embodiment is also omitted, and is illustrated centered on different parts.
In above-described embodiment one to three, illustrate to surround above-mentioned support spiral shell relative to each of multiple carrying bolts 138
Mode around bolt 138 is provided with the example of elastic support member 190 between supplementary bearing shell 133 and pump case 106e.
In contrast, above-mentioned supplementary bearing shell 133 and above-mentioned pump case of the present embodiment four in the inner circumferential side of multiple above-mentioned carrying bolts 138
Between body 106e, elastic support member 190 is set in a circumferential direction.
That is, even if in the present embodiment four, also in above-mentioned elastic support member 190 by cricoid resin ring, cricoid
On this point wave plate gasket is constituted is identical as above-described embodiment one.But in the present embodiment, not to surround carrying bolt 138
Around mode elastic support member is set, but in a manner of the inner circumferential side to connect multiple above-mentioned carrying bolts 138, i.e. wrap
Mode around spinning shaft 101 is set in a circumferential direction between above-mentioned supplementary bearing shell 133 and above-mentioned pump case 106e
Set biggish cricoid elastic support member 190, i.e., cricoid resin ring 191a and wave plate gasket 192a.
In addition, above-mentioned resin ring 101a and wave plate gasket 192a is to connect the side of the inner circumferential side of multiple above-mentioned carrying bolts
Formula is configured at the cricoid groove 133d in the formation of the lower end surface of above-mentioned supplementary bearing shell 133, and above-mentioned pump case 106e utilizes upper
It states wave plate gasket 192a to be pressed downwards by means of above-mentioned resin ring 191a, utilizes above-mentioned 190 bullet of elastic support member as a result,
Property the above-mentioned oil feed pump 106 of support.
In addition, even if in the present embodiment, the pump case 106e of above-mentioned oil feed pump 106 is also relative to above-mentioned supplementary bearing shell
133 install in the state of maintaining the gap s2 of axial gap s1 and radial direction.
In addition, in the present embodiment four, due to the above-mentioned supplementary bearing shell 133 in the inner circumferential side of above-mentioned carrying bolt 138
Above-mentioned elastic support member 190, i.e., cricoid resin ring 191a and wave plate are annularly set between above-mentioned pump case 106e
Therefore gasket 192a seals the space (inner space of supplementary bearing shell) and outside of the inside of above-mentioned elastic support member 190
Space (exterior space of supplementary bearing shell).Therefore, blocking lubricates supplementary bearing 105 (referring to Fig.1) and is discharged to outside supplementary bearing
The discharge path of oil in shell 133, no normal direction oil measure deposit the discharge of (referring to Fig.1) side of portion 131.
Therefore, in the present embodiment four, as shown in Figure 6, Figure 7, the inside of multiple above-mentioned supplementary bearing shells 133 of connection is set
Oil discharge slot (oily discharge path) 106h in space and exterior space, it is ensured that oily discharge path.Other structures and above-described embodiment
One is identical.
Even if also identical as above-described embodiment one in the present embodiment four, even if due to the pressure generated in oil feed pump 106
The inclination of uneven, rotary shaft 101 vibration, internal rotor 106a increases, and can tilt, can absorb also by pump case 106e
State the inclination of internal rotor 106a.In addition, the fuel feeding as caused by the increase of the pressure difference of the volume increase with above-mentioned oil feed pump 106
The vibration of pump 106, vibrate as caused by the high speed rotation of rotary shaft also can be by above-mentioned elastic support member 190, i.e. resin ring
191a and wave plate gasket 192a absorbs.
The pump cover 106f, internal rotor 106a, the outer rotor 106b that constitute oil feed pump 106 can be inhibited strongly to contact as a result, subtracted
The abrasion of small said pump cover 106f, internal rotor 106a etc., can improve the reliability etc. of screw compressor, can obtain and embodiment one
Identical effect.
In addition, according to the present embodiment four, due to for outside the above-mentioned supplementary bearing of the inner circumferential side of multiple above-mentioned carrying bolts 138
Therefore the structure that circular elastic support member 190 is arranged between shell 133 and above-mentioned pump case 106e can make to flexibly support
Component 190 is one, relative to embodiment one to three, also has the effect of reducing number of components and cost of implementation reduces.
In addition, illustrating that the example of cricoid above-mentioned groove 133d is arranged in 133 side of supplementary bearing shell, but can take and generation
It, forms the above-mentioned groove for storing above-mentioned resin ring 191a, above-mentioned wave plate gasket 192a in the upper surface of pump case 106e
133d。
In addition, the material as above-mentioned resin ring 191a, it can be identical as above-described embodiment one, use polytetrafluoroethylene (PTFE)
(PTFE), the superengineering plastics that the heat resistances such as polyphenylene sulfide (PPS) or polyether-ether-ketone (PEEK) are 150 DEG C or more.
In addition, in the explanation of above-described embodiment four, so that the inner circumferential side of multiple above-mentioned carrying bolts 138 is annularly continuous
Mode form above-mentioned groove 133d, cricoid elastic support member 190 is arranged in groove 133d, but be not limited to the party
Formula.For example, even if being to be intermittently formed groove in a circumferential direction in the inner circumferential side of multiple above-mentioned carrying bolts 138, it is recessed at this
The elasticity branch such as elastic support member that slot setting is made of arc-shaped, linear resin panel, wave plate gasket, helical spring
The structure for supportting pump case, can also obtain roughly the same effect.
[embodiment five]
Illustrate the embodiment five of screw compressor of the invention using Fig. 8.Fig. 8 is the figure for illustrating the present embodiment five, be with
The comparable figure of Fig. 2 or Fig. 6.In addition, even if in the explanation of the present embodiment five, about part identical with above-described embodiment one
Illustrate also to omit, be illustrated centered on different parts.
The present embodiment five is also identical as above-described embodiment four, the above-mentioned pair in the inner circumferential side of multiple above-mentioned carrying bolts 138
Between bearing case 133 and above-mentioned pump case 106e, it is provided with elastic support member 190 in a circumferential direction.
That is, even if in the present embodiment five, nor resilient support is arranged in the mode surrounded around carrying bolt 138
Component, but in a manner of the inner circumferential side to connect multiple above-mentioned carrying bolts 138, i.e. surround rotary shaft 101 around mode,
Between above-mentioned supplementary bearing shell 133 and above-mentioned pump case 106e, biggish cricoid resilient support is set in a circumferential direction
Component 190.
In addition, constituting elastic support member by resin ring 191a and wave plate gasket 192a in above-described embodiment four
190, oil feed pump 106 is flexibly supported in supplementary bearing shell 133, but in the present embodiment five, by the circular O of nitrile rubber
Ring 193a constitutes above-mentioned elastic support member 190, and O ring 193a is disposed in the pump case 106e and supplementary bearing of oil feed pump 106
Between shell 133, above-mentioned oil feed pump 106 is flexibly supported.
If describing in detail, then in the present embodiment five, in the lower end surface of supplementary bearing shell 133, also to connect multiple supports
The mode of the inner circumferential side of bolt 138, the mode i.e. around encirclement rotary shaft 101, in above-mentioned supplementary bearing shell 133 and said pump
Cricoid elastic support member 190 big in a circumferential direction, i.e. circular O ring 193a are set between shell 106e.
In addition, above-mentioned O ring 193a is disposed in a manner of connecting the inner circumferential side of multiple above-mentioned carrying bolts 138 in above-mentioned pair
The circular groove 133d that the lower end surface of bearing case 133 is formed, presses downwards above-mentioned pump case using above-mentioned O ring 193a
106e flexibly supports above-mentioned oil feed pump 106 using above-mentioned elastic support member 190 as a result,.
In addition, in the present embodiment, the pump case 106e of above-mentioned oil feed pump 106 is also relative to above-mentioned supplementary bearing shell 133
It is installed in the state of maintaining the gap s2 of axial gap s1 and radial direction.Other structures are identical as above-described embodiment one, four.
Even if also identical as above-described embodiment one, four in the present embodiment five, even if due to being generated in oil feed pump 106
The inclination of the vibration of pressure imbalance, rotary shaft 101, internal rotor 106a increases, and can tilt, can absorb also by pump case 106e
The inclination of above-mentioned internal rotor 106a.In addition, as with above-mentioned oil feed pump 106 volume increase pressure difference increase caused by supply
The vibration of oil pump 106 is vibrated as caused by the high speed rotation of rotary shaft and can also be absorbed by above-mentioned O ring 193a.
The pump cover 106f, internal rotor 106a, the outer rotor 106b that constitute oil feed pump 106 can be inhibited strongly to contact as a result, subtracted
The abrasion of small said pump cover 106f, internal rotor 106a etc., can improve the reliability etc. of screw compressor as a result, can obtain and real
Apply example one, four identical effects.
In addition, according to the present embodiment five, since only elastic support member 190 can be constituted by O ring 193a, also have
Structure is simple and the effect that can manufacture cheaply than above-described embodiment four.
In addition, illustrate the example that circular above-mentioned groove 133d is set to 133 side of supplementary bearing shell, but can take and
Instead of, even if in the present embodiment five, it can also be formed in the upper surface of pump case 106e and store the above-mentioned recessed of above-mentioned O ring 193a
Slot 133d.
[embodiment six]
Illustrate the embodiment six of screw compressor of the invention using Fig. 9.Fig. 9 is the figure for illustrating the present embodiment six, be with
The comparable figure of Fig. 2 or Fig. 6.In addition, even if in the explanation of the present embodiment six, said about with one same section of above-described embodiment
It is bright also to omit, it is illustrated centered on different parts.
The present embodiment six is also identical as above-described embodiment four, five, in the above-mentioned of the inner circumferential side of multiple above-mentioned carrying bolts 138
Between supplementary bearing shell 133 and above-mentioned pump case 106e, elastic support member 190 is set in a circumferential direction.
That is, even if in the present embodiment six, nor resilient support is arranged in the mode surrounded around carrying bolt 138
Component, but in above-mentioned supplementary bearing shell 133 and above-mentioned pump case in a manner of the inner circumferential side to connect multiple above-mentioned carrying bolts 138
Between body 106e, biggish cricoid elastic support member is set in a circumferential direction.
In addition, constituting elastic support member by resin ring 191a and wave plate gasket 192a in above-described embodiment four
190, oil feed pump 106 is flexibly supported in supplementary bearing shell 133, but in the present embodiment six, only by circular wave plate gasket
192b constitutes above-mentioned elastic support member 190, and wave plate gasket 192b is disposed in the pump case 106e and countershaft of oil feed pump 106
It holds between shell 133, flexibly supports above-mentioned oil feed pump 106.
In addition, above-mentioned wave plate gasket 192b is disposed in a manner of connecting the inner circumferential side of multiple above-mentioned carrying bolts 138
The circular groove 133d that the lower end surface of above-mentioned supplementary bearing shell 133 is formed, is pressed downwards using above-mentioned wave plate gasket 192b
Above-mentioned pump case 106e is pressed, flexibly supports above-mentioned confession using as the wave plate gasket 192b of above-mentioned elastic support member 190 as a result,
Oil pump 106.
In the present embodiment six, due to only constituting above-mentioned elastic support member 190 by circular wave plate gasket 192b, because
, there is a possibility that wearing away with the part of the wave plate gasket 192b pump case 106e contacted in this.It, can be in order to inhibit the abrasion
The side end of the pump case 106e of above-mentioned wave plate gasket 192b is set to be configured to flat surface.
In addition, even if in the present embodiment, the pump case 106e of above-mentioned oil feed pump 106 is also relative to above-mentioned supplementary bearing shell
133 install in the state of maintaining the gap s2 of axial gap s1 and radial direction.Other structures and above-described embodiment one, four phases
Together.
Even if also identical as above-described embodiment one, four in the present embodiment six, even if due to being generated in oil feed pump 106
The inclination of the vibration of pressure imbalance, rotary shaft 101, internal rotor 106a increases, and can tilt, can absorb also by pump case 106e
The inclination of above-mentioned internal rotor 106a.In addition, as with above-mentioned oil feed pump 106 volume increase pressure difference increase caused by supply
The vibration of oil pump 106 is vibrated as caused by the high speed rotation of rotary shaft and can also be absorbed by above-mentioned wave plate gasket 192b.
The pump cover 106f, internal rotor 106a, the outer rotor 106b that constitute oil feed pump 106 can be inhibited strongly to contact as a result, energy
The abrasion for reducing said pump cover 106f, internal rotor 106a etc., can improve the reliability etc. of screw compressor as a result, can obtain with
Embodiment one, four identical effects.
In addition, according to the present embodiment six, it, can ratio due to being only made of elastic support member 190 wave plate gasket 192b
Above-described embodiment four is cheaper to manufacture.
Furthermore it is possible to instead of circular above-mentioned groove 133d is set to 133 side of supplementary bearing shell, pump case 106a's
Upper surface forms the above-mentioned groove 133d for storing above-mentioned wave plate gasket 192b.
In addition, the present invention is not limited to above-described embodiment, including various deformation example.In addition, can be by the knot of certain embodiment
A part of structure is replaced into the structure of other embodiments, can also increase the structure of other embodiments in the structure of certain embodiment.
In addition, above-described embodiment is explained in detail to be illustrated the present invention with being readily apparent that, do not limit
In the whole structures for having explanation.
Claims (10)
1. a kind of screw compressor, has: closed container；It is installed on the main frame and sub-frame of the closed container；Fixed whirlpool
Rotation, the overlapping portion with end plate He the vortex shape for standing up the end plate, and it is installed on above-mentioned main frame；Rotating vortex,
Its overlapping portion with end plate He the vortex shape for standing up the end plate, engages with above-mentioned fixed scroll and forms discharge chambe；
Rotary shaft is rotated the rotating vortex and has cam pin portion；Boss portion is rotated, above-mentioned rotating vortex is set to
Above-mentioned end plate back side, have for above-mentioned cam pin portion insertion swivel bearing；Base bearing is set to above-mentioned main frame,
And it is freely and rotatably supported the main shaft part of above-mentioned rotary shaft；And supplementary bearing, it is set to the countershaft for being installed on above-mentioned sub-frame
Shell is held, and is freely and rotatably supported the countershaft portion of above-mentioned rotary shaft, which is characterized in that,
Have:
Oil feed pump, is installed on above-mentioned supplementary bearing shell, and there is pump case and be located at the intracorporal internal rotor of the pump case and
Outer rotor；
Multiple carrying bolts, the shape relative to above-mentioned supplementary bearing shell, in the gap for maintaining axial gap and radial direction
The pump case of above-mentioned oil feed pump is installed under state；And
Elastic support member, with the mode surrounded around multiple above-mentioned carrying bolts be set to above-mentioned supplementary bearing shell with it is above-mentioned
Between pump case.
2. a kind of screw compressor, has: closed container；It is installed on the main frame and sub-frame of the closed container；It is fixed
It is vortexed, the overlapping portion with end plate He the vortex shape for standing up the end plate, and it is installed on above-mentioned main frame；Rotate whirlpool
Rotation, the overlapping portion with end plate He the vortex shape for standing up the end plate engages with above-mentioned fixed scroll and forms compression
Room；Rotary shaft is rotated the rotating vortex and has cam pin portion；Boss portion is rotated, above-mentioned rotation is set to
The back side for the above-mentioned end plate being vortexed has the swivel bearing for the insertion of above-mentioned cam pin portion；Base bearing is set to above-mentioned main frame
Frame, and it is freely and rotatably supported the main shaft part of above-mentioned rotary shaft；And supplementary bearing, it is set to the pair for being installed on above-mentioned sub-frame
Bearing case, and it is freely and rotatably supported the countershaft portion of above-mentioned rotary shaft, which is characterized in that,
Have:
Oil feed pump, is installed on above-mentioned supplementary bearing shell, and there is pump case and be located at the intracorporal internal rotor of the pump case and
Outer rotor；
Multiple carrying bolts, the shape relative to above-mentioned supplementary bearing shell, in the gap for maintaining axial gap and radial direction
The pump case of above-mentioned oil feed pump is installed under state；And
Elastic support member, be set in a circumferential direction the above-mentioned supplementary bearing shell of the inner circumferential side of multiple above-mentioned carrying bolts with
Between above-mentioned pump case.
3. screw compressor according to claim 1 or 2, which is characterized in that
Above-mentioned elastic support member is made of resin ring and wave plate gasket, and flexibly supports above-mentioned oil feed pump.
4. screw compressor according to claim 3, which is characterized in that
Above-mentioned resin ring is by polytetrafluoroethylene (PTFE), that is, PTFE, polyphenylene sulfide, that is, PPS and polyether-ether-ketone, that is, PEEK any one structure
At.
5. screw compressor according to claim 1 or 2, which is characterized in that
Above-mentioned elastic support member is made of the circular O ring of nitrile rubber, and flexibly supports above-mentioned oil feed pump.
6. screw compressor according to claim 1, which is characterized in that
Above-mentioned elastic support member is made of compression helical spring, configures above-mentioned support spiral shell in the inside of the compression helical spring
Bolt flexibly supports above-mentioned oil feed pump using the compression helical spring.
7. screw compressor according to claim 6, which is characterized in that
Above-mentioned compression helical spring crosses over the slot for being formed in the end face of above-mentioned supplementary bearing shell and is formed in the position opposed with the slot
The slot of the end face for the above-mentioned pump case set and be inserted into configuration.
8. screw compressor according to claim 2, which is characterized in that
Above-mentioned elastic support member is made of circular wave plate gasket, and the wave plate gasket insertion of the annular shape is configured at above-mentioned
The circular slot that the end face of supplementary bearing shell or the end face of above-mentioned pump case are formed, and flexibly support above-mentioned oil feed pump.
9. screw compressor according to claim 2, which is characterized in that
It is provided with and is connected to the inner space of above-mentioned supplementary bearing shell and the oily discharge path of exterior space.
10. screw compressor according to claim 9, which is characterized in that
Above-mentioned oil discharge path is provided at the oil discharge slot of the end face of the above-mentioned supplementary bearing shell side in above-mentioned pump case.
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| JP2017-122088 | 2017-06-22 | ||
| JP2017122088A JP6862294B2 (en) | 2017-06-22 | 2017-06-22 | Scroll compressor |
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| CN109113990B CN109113990B (en) | 2020-03-06 |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111749883A (en) * | 2019-03-26 | 2020-10-09 | 丰田合成株式会社 | Oil pump |
| WO2022011824A1 (en) * | 2020-07-14 | 2022-01-20 | 艾默生环境优化技术(苏州)有限公司 | Bearing assembly and compressor |
| CN116816669A (en) * | 2023-08-30 | 2023-09-29 | 沈阳海龟医疗科技有限公司 | Floating oil-free vacuum scroll compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| WO2020183605A1 (en) * | 2019-03-12 | 2020-09-17 | 日立ジョンソンコントロールズ空調株式会社 | Compressor and refrigeration cycle device |
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| JP2014025427A (en) * | 2012-07-27 | 2014-02-06 | Daikin Ind Ltd | Compressor |
| CN204175655U (en) * | 2014-10-16 | 2015-02-25 | 宁波龙泰电讯电机有限公司 | The centrifugal fan housing that a kind of elasticity connects |
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| CN111749883A (en) * | 2019-03-26 | 2020-10-09 | 丰田合成株式会社 | Oil pump |
| CN111749883B (en) * | 2019-03-26 | 2022-03-18 | 丰田合成株式会社 | Oil pump |
| WO2022011824A1 (en) * | 2020-07-14 | 2022-01-20 | 艾默生环境优化技术(苏州)有限公司 | Bearing assembly and compressor |
| CN116816669A (en) * | 2023-08-30 | 2023-09-29 | 沈阳海龟医疗科技有限公司 | Floating oil-free vacuum scroll compressor |
| CN116816669B (en) * | 2023-08-30 | 2023-11-21 | 沈阳海龟医疗科技有限公司 | Floating oil-free vacuum scroll compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2019007382A (en) | 2019-01-17 |
| CN109113990B (en) | 2020-03-06 |
| JP6862294B2 (en) | 2021-04-21 |
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