CN108350869A - Fluid machinery - Google Patents
Fluid machinery Download PDFInfo
- Publication number
- CN108350869A CN108350869A CN201780003768.6A CN201780003768A CN108350869A CN 108350869 A CN108350869 A CN 108350869A CN 201780003768 A CN201780003768 A CN 201780003768A CN 108350869 A CN108350869 A CN 108350869A
- Authority
- CN
- China
- Prior art keywords
- groove portion
- bent axle
- lubricating oil
- sliding area
- thrust plate
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0238—Hermetic compressors with oil distribution channels
- F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0261—Hermetic compressors with an auxiliary oil pump
-
- 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
- F04C2240/80—Other components
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
- Compressor (AREA)
Abstract
The present invention provides a kind of fluid machinery.In the present invention, hermetic type screw compressor has：Circular thrust plate (40) has the through hole (41) to circulate for lubricating oil；And bent axle (11), it is placed in the upper surface of thrust plate (40), and inside is formed with the circulation flow path (17) of the lubricating oil circulation for use by the through hole (41) of thrust plate (40), in the sliding area of bent axle (11) and thrust plate (40), the concave groove portion (42) that lubricating oil is supplied from through hole (41) is at least formed in any one in bent axle (11) and thrust plate (40), the outboard end (42a) of the radial direction of groove portion (42) is located at more in the inner part than the outermost circumference in sliding area.
Description
Technical field
The present invention relates to a kind of fluid machineries.
Background technology
Vertical type hermetic type compressor accommodates compression mechanism in shell and drives the motor (motor) of compression mechanism, and
Compression mechanism is combined with motor rotor on same bent axle.Bent axle is arranged in a manner of axially becoming plummet direction, and bent
The lower end of axis is applied with thrust load.Here, thrust load by bent axle and motor rotor own wt and action when produce
The power of the axial direction of raw magnetic force.
When supporting above-mentioned thrust load, the lower end of bent axle generates friction loss.Therefore, such as following patent documents 1 and 2
In it is recorded, be equipped with the thrust bearing contacted with bent axle lower end.
Conventional art document
Patent document
Patent document 1：Japanese Unexamined Patent Publication 62-78389 bulletins
Patent document 2：Japanese Unexamined Patent Publication 2014-152747 bulletins
Invention content
The invention technical task to be solved
It in patent document 1 and 2, records and supplies lubricating oil relative to thrust bearing, thus improve in thrust bearing
The content of lubricity.Also, in the sliding area of bent axle lower end and thrust bearing, for axial thrust bearing supply lubricating oil
Oil supply tank spreads entire radial direction, that is, is through to outer peripheral portion from inner peripheral portion and is formed.
Oil circuit inside compressor is formed in the center of bent axle, and branches into the bearing of journals or the compression of bearing radial load
Mechanism.Lubricating oil is supplied from the pump being set to around bent axle lower end to the oil circuit at the center for being set to bent axle, via
Oil circuit is supplied to the bearing of journals or compression mechanism.
Therefore, when the lubricating oil to boost in pump is also supplied to thrust bearing, if in bent axle lower end and thrust axis
The oil supply tank formed in sliding area held is formed throughout entire radial direction, then lubricating oil can pass through the oil supply tank.Its
As a result, the lubricating oil to boost in pump is caused largely to be flowed out from oil supply tank, there is supply to the bearing of journals or compression mechanism etc.
The problem of amount of lubricating oil is reduced.
The present invention is to complete in light of this situation, and its purpose is to provide one kind can reduce in the production of bent axle lower end
Raw friction loss, and other sliding parts can also be securely fed with the fluid machinery of lubricating oil.
Means for solving technical task
In order to solve the above problems, fluid machinery of the invention uses following methods.
That is, the fluid machinery involved by the mode of the present invention has：Circular plate portion, with what is circulated for lubricating oil
Through hole；And bent axle, it is placed in the upper surface of the plate portion, and the internal through hole being formed with for use by the plate portion
The circulation flow path of the lubricating oil circulation, in the sliding area of the bent axle and the plate portion, in the bent axle and the plate portion
In be at least formed with the concave groove portion that the lubricating oil is supplied from the through hole, the radius side of the groove portion in any one
To outboard end be located at more in the inner part than the outermost circumference in the sliding area.
According to the structure, plate portion is formed through hole, and circulation is formed in the inside for the bent axle for being placed in plate portion upper surface
Flow path, lubricating oil circulate plate portion through hole after, flow through the circulation flow path of bent axle.In the sliding area of bent axle and plate portion,
At least forming a groove in any one in bent axle and plate portion, and lubricating oil is supplied from through hole to groove portion.As a result, lubricating oil is filled out
It fills the sliding area in bent axle and plate portion and forms oil film, so as to reduce friction loss.Also, the radial direction of groove portion
Outboard end is located at more in the inner part than the outermost circumference in above-mentioned sliding area, therefore the lubricating oil of supply to groove portion is difficult from cunning
The inner circumferential side in dynamic region leaks to outer peripheral side.
For example, the outboard end of the radial direction of groove portion is located at the 10% of the radius of the outermost circumference in above-mentioned sliding area
The position of left and right inside.
In aforesaid way, the outboard end of the radial direction of the groove portion can also be located at than in the sliding area most
Centre position between inner peripheral portion and the outermost circumference is more outward.
According to the structure, can by groove portion by lubricating oil supply to than in sliding area most inner peripheral portion with it is described outermost
Centre position between circumference is more outward.
In aforesaid way, the area in the region of the groove portion is formed in the sliding area relative to the sliding area
The gross area in domain than the outboard end of the radial direction of the groove portion more in the inner part can be 50% or more and 80% or less.
It is easy to form oil film in the sliding area of bent axle and plate portion by supplying to the lubricating oil of groove portion according to the structure.
In aforesaid way, in the inboard portion of the radial direction of the groove portion or in the bent axle or the plate portion
The part opposite with the inboard portion of the radial direction of the groove portion could be formed with the conical surface.
According to the structure, the inboard portion of the radial direction of groove portion or the part opposite with it are the conical surface, therefore groove portion
The inside of radial direction broadens along short transverse, and lubricating oil is easy supply to the inside of groove portion.
In aforesaid way, the groove portion can have ladder-like, taper or recess.
Invention effect
In accordance with the invention it is possible to reduce the friction loss generated in bent axle lower end, and also can to other sliding parts
Lubricating oil is supplied by ground.
Description of the drawings
Fig. 1 is the longitudinal section view for indicating the Scrawl compressor involved by one embodiment of the present invention.
Fig. 2 is the partial enlargement vertical profile for the thrust plate for indicating the Scrawl compressor involved by one embodiment of the present invention
View.
Fig. 3 is the vertical view for the thrust plate for indicating the Scrawl compressor involved by one embodiment of the present invention.
Fig. 4 is the groove portion indicated formed in the thrust plate of the Scrawl compressor involved by one embodiment of the present invention
An example longitudinal section view.
Fig. 5 is the groove portion indicated formed in the thrust plate of the Scrawl compressor involved by one embodiment of the present invention
An example longitudinal section view.
Fig. 6 is the groove portion indicated formed in the thrust plate of the Scrawl compressor involved by one embodiment of the present invention
An example longitudinal section view.
Fig. 7 is the lower end for the bent axle for indicating the Scrawl compressor involved by one embodiment of the present invention, thrust plate
And the longitudinal section view of intake line.
Fig. 8 is the curve graph of the efficiency for the air-conditioning device for indicating each operation mode or performance evaluation.
Fig. 9 is the longitudinal section view for indicating the rotary compressor involved by one embodiment of the present invention.
Specific implementation mode
Hereinafter, refer to the attached drawing illustrates the hermetic type screw compressor involved by one embodiment of the present invention.
As shown in Figure 1, the hermetic type screw compressor 1 as scroll fluid machine have bottom by lower cover seal along upper
The closed shell 2 of the lower longer cylindrical shape in direction.The top of the closed shell 2 is discharged lid 3 and upper cover 4 seals, and in the row
Go out between lid 3 and upper cover 4 the discharge chamber 5 for being formed with and compressed high pressure gas being discharged.
In closed shell 2, it is fixedly installed upper bearing member (frame parts) 6 at upside position, passes through upper axis
Bearing portion part 6 is assembled with scroll compression body 7, and position is equipped with the electro-motor being made of stator 8 and rotor 9 on the downside of it
10.The electro-motor 10 is fixedly installed on closed shell 2 by stator 8 by is assembled, and bent axle 11 is fixed in rotor 9.
It is equipped with the crank-pin 12 of axle center bias predetermined size in the upper end of bent axle 11, by the way that its crank-pin 12 is attached at whirlpool
Compression mechanism 7 is revolved, scroll compression body 7 can be driven by electro-motor 10.The top of bent axle 11 is rotatably freely supported on
The journal bearing portion 6A of portion's parts of bearings 6, and lower end is rotatably freely supported on and is arranged at the downside position of closed shell 2
The lower part bearing of journals 13.
It is configured to as follows, that is, displacement type oil feed pump 14 is equipped between the lower part bearing of journals 13 and the lower end of bent axle 11,
And the lubricating oil 15 for the bottom for being filled in closed shell 2 is sucked via intake line 16, and to being arranged in an axial direction in bent axle 11
Circulation flow path 17 be discharged.The lubricating oil 15 can be via circulation flow path 17 supply to upper bearing member 6, scroll compression body
The position of the needs lubrication such as 7 and the lower part bearing of journals 13.
Scroll compression body 7 has：Fixed scroll 18, one kind by upper bearing member 6 as component parts, and it is fixed
It is arranged on portion's parts of bearings 6；Revolution vortex 19, is sliding freely supported on the thrust bearing division of upper bearing member 6
6B, and form discharge chambe 20 by being engaged with fixed scroll 18；The rotations such as euclidean Ring dampening mechanism 21, is clipped in upper axis bearing portion
Part 6 and revolution are vortexed between 19, prevent the rotation of revolution vortex 19 and allow the rotary motion that revolves round the sun；And driver bushing 22 and
Floating bearing (needle bearing) 23, is set between the crank-pin 12 of bent axle 11 and bearing hub 19C, is transmitted to revolution vortex 19 bent
The rotary force of axis 11, bearing hub 19C are set to the back side of revolution vortex 19, in scroll compression body 7, fixed scroll 18
End plate central portion is set to the state being connect with discharge cap 3 in upper bearing member 6.
Fixed scroll 18 has end plate 18A and stands up the vortex shape vortex ring 18B on its end plate 18A, and is end plate
The central part of 18A is equipped with discharge 24, and the vortex ring face of tooth of vortex shape vortex ring 18B is equipped with the structure of sheet packing 25.And
And revolution vortex 19 has end plate 19A and stands up the vortex shape vortex ring 19B on its end plate 19A, is end plate 19A's
The back side is equipped with bearing hub 19C, and the vortex ring face of tooth of vortex shape vortex ring 19B is equipped with the structure of sheet packing 26.
Scroll compression body 7 will be piped via the sucking in the position opening opposite with the stator winding 8A of electro-motor 10
27 suckings are sucked into from the sucking 28 in 2 inner opening of closed shell in discharge chambe 20 in the refrigerant gas in closed shell 2, and
Compress it into high temperature and high pressure gas.The compressed gas via the central part for being set to fixed scroll 18 discharge 24 and be set to
The dump valve 29 of discharge cap 3 is discharged into discharge chamber 5, is further piped 30 to pressure via the discharge being connect with discharge chamber 5
The external output of contracting machine.
Hereinafter, being said to the thrust plate 40 being set on the compressor involved by present embodiment referring to figs. 2 to Fig. 7
It is bright.
Thrust plate 40 is the plate-shaped member being arranged in a manner of being contacted with the lower face of bent axle 11.The thickness example of thrust plate 40
Such as it is about 1mm.Thrust plate 40 is set between the lower surface of the lower part bearing of journals 13 and the upper surface of intake line 16.
The through hole 41 to circulate for lubricating oil 15 is formed in thrust plate 40.By through hole 41, it is formed in intake line
16 circulation flow path 51 is connected with the circulation flow path 17 for being formed in bent axle 11.As a result, as shown in fig. 7, passing through intake line
The through hole 41 of the 16 circulation thrust plate 40 of lubricating oil 15, and after the through hole 41 of the circulation thrust plate 40 of lubricating oil 15, flow through
The circulation flow path 17 of bent axle 11.
In thrust plate 40, the sliding area between bent axle 11 and thrust plate 40 is formed with groove portion 42.In addition, bent axle 11
Sliding area between thrust plate 40 is the region of the upper surface of lower face and the thrust plate 40 of bent axle 11 toward each other.With
Under, the case where being only formed in thrust plate 40 to groove portion 42, illustrates, but the present invention is not limited to the examples.For example, of the invention
Involved groove portion can be between bent axle 11 and thrust plate 40 sliding area be only formed in bent axle 11, song can also be formed in
Both axis 11 and thrust plate 40.
About groove portion 42, be formed as concavity in thrust plate 40, and lubricating oil 15 is fed with from through hole 41.That is, groove portion
42 in 41 side of through hole of thrust plate 40, and is formed in the circulation flow path 51 of intake line 16 or is formed in the circulation stream of bent axle 11
Road 17 is connected.
By forming small recess in thrust plate 40, dynamic pressure is generated in sliding area, and generate based on oil film pressure
It suspends.As a result, it is possible to reduce the generated friction loss between the lower face of bent axle 11 and the upper surface of thrust plate 40.
The depth of groove portion 42 is, for example, 5 μm or more and 10 μm or less.The depth of groove portion 42 is according in the lower face of bent axle 11
The ratio between comprehensive roughness of generated oil film thickness and sliding surface (Λ values) determines between the upper surface of thrust plate 40.
Knowing has when Λ values (comprehensive roughness of=oil film thickness/sliding surface) are the value more than 3, determines and generates the suspension based on oil film,
Bent axle 11 can be made to suspend relative to thrust plate 40 by oil film.If also, no matter the height of the rotating speed of bent axle 11, groove portion 42
Depth is excessively shallow or too deep, then Λ values become lower value.That is, no matter the height of the rotating speed of bent axle 11, there are Λ values to become very big
The depth of the best groove portion 42 of value.
In addition, the rotating speed in bent axle 11 is lower, if the depth of groove portion 42 is set as relatively deep, Λ values are easy into
For 3 hereinafter, on the other hand, the rotating speed in bent axle 11 is higher, even if the depth of groove portion 42 is set as relatively deep Λ values
It is able to maintain that the value more than 3.That is, the rotating speed in bent axle 11 is lower, the depth of the groove portion 42 of the value more than 3 can be set as
It is narrower to spend range situation more higher than the rotating speed of bent axle 11.
Inventor etc. has obtained following opinion, that is, within the compressor, by the diameter of bent axle 11 be set as 10mm or more and
40mm is hereinafter, the rotating speed of bent axle 11 is set as 10rps or more and 140rps hereinafter, lubricating oil viscosity is set as 2mPas or more
And 30mPas is calculated hereinafter, when total its own gravity of bent axle 11 and rotor 9 is set as 10N or more and 100N or less
The analysis of Λ values as a result, the depth of the groove portion 42 of thrust plate 40 ranges preferably from 5 μm or more and 10 μm of ranges below.
Also, inventor etc. has obtained following opinion according to demonstration experiment, that is, when the rotating speed of bent axle 11 is relatively low, such as
When less than 40rps, the depth of groove portion 42 is preferably 5 μm, when the rotating speed of bent axle 11 is higher, when for example, 90rps or more, and groove portion
42 depth is preferably 10 μm.This display trend same as the above-mentioned analysis of Λ values is calculated.
For example, among refrigeration when operating, by the overall efficiency of the compressor in the case of thrust plate of the setting without groove portion 42
Curve when being set as 1 is illustrated in Fig. 8.As a result, when being operated among the lower refrigeration of rotating speed of bent axle 11, compared to by groove portion
The case where 42 depth is set as 10 μm, it is more efficient when the depth of groove portion 42 is set as 5 μm.On the other hand, turn in bent axle 11
When the fast specified operating of higher heating, the case where compared to the depth of groove portion 42 is set as 5 μm, the depth of groove portion 42 is set as 10
μm when it is more efficient.
That is, when being operated by centre than specified operating when the higher APF of weighted value (Annual Performance
Factor：Annual performance factor) in the case of energy-efficient performance to evaluate air-conditioning device, set compared to by the depth of groove portion 42
It is 10 μm, is preferably set to 5 μm.
The outboard end 42a of the radial direction of groove portion 42 be located at than bent axle 11 with it is outermost in the sliding area of thrust plate 40
Circumference is more in the inner part.That is, groove portion 42 is not connected to from the inside of radial direction throughout outermost circumference in sliding area.Cause
This, is easy to rest in groove portion 42 from the lubricating oil 15 of through hole 41 supply to groove portion 42, and is difficult more outside than sliding area
Side leaks.
Different from present embodiment, groove portion 42 is in the entire radial direction throughout sliding area, that is, runs through from inner peripheral portion
Outer peripheral portion and in the case of being formed, cause lubricating oil 15 to be flowed out from the system for the distribution of commodities, supply to the bearing of journals or compression mechanism etc.
The amount of lubricating oil 15 can reduce.In contrast, for present embodiment, groove portion 42 in sliding area not from
The inside of radial direction is connected to throughout outermost circumference, can be to the bearing of journals or pressure there is no need to reduce the amount of lubricating oil 15
The sufficient lubricating oil of the supplies such as contracting mechanism 15.
The outboard end 42a of the radial direction of groove portion 42 is located at the 10% of the radius of the outermost circumference in above-mentioned sliding area
The position of left and right inside.Thereby, it is possible to be reliably prevented supply to the lubricating oil 15 of groove portion 42 from the inner circumferential side of sliding area to
Peripheral side leaks.
The outboard end 42a of the radial direction of groove portion 42 is located at than the most inner peripheral portion in sliding area and between outermost circumference
Centre position it is more outward.Thereby, it is possible to be supplied lubricating oil 15 to than the most inner peripheral portion in sliding area by groove portion 42
Centre position between outermost circumference is more outward.
If indicating relation above by formula, become as follows.
rave(=(rout-rin)/2) 0.9 × r of ＜ r ＜out
Wherein, r is the outboard end 42a of groove portion 42, that is, forms the radius of the boundary part of ladder, routFor sliding area
In outermost circumference radius, rinFor the radius of the most inner peripheral portion in sliding area.
Also, be formed in sliding area the area in the region of groove portion 42 relative in sliding area than the half of groove portion 42
The gross areas of the outboard end 42a in diameter direction more in the inner part, preferably 50% or more and 80% or less.
If the area in the region for being formed with groove portion 42 in sliding area is set as Astep, groove portion will be compared in sliding area
The outboard end 42a of 42 radial direction more in the inner part and be not that the area in region (mesa region) of groove portion 42 is set as Aland,
It can then be indicated by following formula.
0.5≤Astep/(Astep+Aland)≤0.8
By meeting the condition, dynamic pressure is generated in sliding area, and easy to produce the suspension based on oil film pressure.In Fig. 3
Shown in example, it is 60 ° of sector that groove portion 42, which has central angle, and circumferentially every 90 ° be equipped at 4, therefore Astep/ (Astep+
Aland it is) 0.67.
Also, as shown in Fig. 2, the part opposite in the inboard portion of the radial direction with the groove portion 42 in bent axle 11 is formed
There is the conical surface 43.In this way, the conical surface 43 is formed in the side for importing lubricating oil 15 in groove portion 42, the thus radial direction of groove portion 42
Inside broadens along short transverse, and lubricating oil 15 is easy supply to the inside of groove portion 42.In addition, in the present invention, about the conical surface, and
The case where being not limitedly formed the part opposite with groove portion can also be set to the inner peripheral portion of groove portion.In this case, lubricating oil
15 are also easy supply to the inside of groove portion.
Circumferentially cutting cross sectional shape along groove portion 42 is for example with ladder-like (Fig. 4), taper (Fig. 5) or recess (figure
6).That is, also can the general shape used in thrust bearing etc. be suitable for present embodiment.
In addition, as shown in Fig. 2 or Fig. 7, in the pump rotor 45 equipped with displacement type oil feed pump 14 more more outward than sliding area.
Also, the lower surface of bent axle 11 and the lower surface of pump rotor 45 are in the same face, therefore even if from bent axle 11 and thrust plate 40
Sliding area leaks micro lubricating oil 15, and lower surface and the thrust plate of pump rotor 45 can be also lubricated by its lubricating oil 15
Between upper surface.In this case, the efficiency of displacement type oil feed pump 14 can be improved.
More than, according to the present embodiment, it is formed through hole 41 in thrust plate 40, is placed in the upper surface of thrust plate 40
The inside of bent axle 11 be formed with circulation flow path 17, lubricating oil 15 circulate thrust plate 40 through hole 41 after, flow through bent axle 11
Circulate flow path 17.In the sliding area of bent axle 11 and thrust plate 40, groove portion 42 is formed in thrust plate 40, lubricating oil 15 from through
Hole 41 is supplied to groove portion 42.As a result, lubricating oil 15 is filled in the sliding area of bent axle 11 and thrust plate 40 and forms oil film, from
And friction loss can be reduced.Also, the outboard end 42a of the radial direction of groove portion 42 be located at than in above-mentioned sliding area most
Peripheral part more in the inner part, therefore is supplied to the lubricating oil 15 of groove portion 42 it is difficult to be leaked to outer peripheral side from the inner circumferential side of sliding area.
Therefore, can not only reduce friction loss, and without reduce lubricating oil 15 amount can to the bearing of journals or
The sufficient lubricating oil of the supplies such as compression mechanism 15.As a result, it is possible to realize the raising of the high efficiency of compressor and reliability.
In addition, in the above-described embodiment, the case where Scrawl compressor, is illustrated, but the present invention does not limit
In the example.For example, rotary compressor, reciprocating compressor can also be suitable for.Moreover, fluid machinery according to the present invention
It is not limited to compressor, additionally it is possible to be suitable for expander.
Hereinafter, to be applicable in relative to rotary compressor involved by present embodiment thrust plate 40 the case where say
It is bright.
As an example of rotary compressor, Fig. 9 is the longitudinal section view for the configuration example for indicating hermetic type single cylinder.In addition, hereinafter,
For convenience's sake, to being illustrated suitable for the embodiment of single cylinder rotary compressor, but not only duplex-cylinder rotary compressor, also
It can be equally applicable to the rotation/compression mechanism of the compressor for the multiple compression mechanisms for having different, this is natural.
Closed rotary compressor 61 has the shell 62 of closed structure.The shell 62 is by cylindric central shell 62A, close
The lower case 62C of the lower part of the upper body 62B and the central shell 62A of sealing on the top of the central shell 62A of envelope is constituted.In
The upside in shell 62A is entreated, the electro-motor 64 being made of stator 65 and rotor 66 is fixedly installed as driving source.
Also, rotor 66 is joined integrally bent axle (rotary shaft) 67.
It is equipped with single cylinder rotation/compression mechanism 63 in the lower part of electro-motor 64.63 structure of rotation/compression mechanism is as follows, that is,
Have：Cylinder main body 69 is formed with cylinder chamber 68；Upper bearing 70 and lower bearing 71, upper bearing 70 are fixedly installed on gas
The top of cylinder main body 69 and lower bearing 71 are fixedly installed on the lower part of cylinder main body 69, and 70 blanket gas cylinder chamber 68 of upper bearing
Top and 71 blanket gas cylinder chamber 68 of lower bearing lower part；Rotor 72, it is chimeric with the eccentric part 67A of bent axle 67, and in cylinder
The inner peripheral surface of room 68 rotates；And the blade and blade of illustration omitted be by pressing spring etc., will be divided into cylinder chamber 68 suction side and
Discharge side.
The rotation/compression mechanism 63 is fixedly installed on cylinder main body by many places plug welding circumferentially or fixed riveting
The inner peripheral surface of any of 69 or upper bearing 70 center shell 62A, other components are assembled with the component for being secured to setting
The mode being integrated is constituted.
Rotation/compression mechanism 63 is via suction line 73 from the air storage chamber 74 being wholely set with rotary compressor 61 to cylinder chamber
The low pressure refrigerant gas of sucking compression fluids in 68, and after compressing the refrigerant gas by the rotation of rotor 72, Xiang Li
Discharge in the top muffler room 75 and lower silencer room 76 formed with upper bearing 70 and lower bearing 71.So compression
Higher pressure refrigerant gas to converge in top muffler room 75 after, the mode being discharged into central shell 62A is constituted.Separately
Outside, it is poor to become substantially no pressure for the inside of top muffler room 75 and lower silencer room 76 and the inside of central shell 62A
State.
The gas passage orifices on the periphery that higher pressure refrigerant gas circulation is set to electro-motor 64 are (not shown.) and drawn
It is directed at the upper space of electro-motor 64, further, with to the outside of rotary compressor 61, i.e. refrigeration is followed via discharge piping 77
The mode of ring side output is constituted.
In above-mentioned rotation/compression mechanism 63, cylinder main body 69, be disposed in cylinder main body 69 top upper bearing 70
And it is disposed in the lower bearing 71 of lower part and forms the lower silencer of lower silencer room 76 in the lower section of lower bearing 71
7A is screwed togather by the fastening of the bolt 78 axially penetrated through along bent axle 67 and is integrated.
Top muffler room 75 and lower silencer room 76 are the part of no external and internal pressure difference.However, in the knot of diagram
In structure example, the leakproofness relative to lubricating oil 15 can be found out, therefore lower silencer 76A is only fastened by bolt 78, but for
Top muffler 75A and lower silencer 76A only fasten any one by the structure of both fastenings of bolt 78 or by bolt 78
Structure etc., be not particularly limited.
Here, thrust plate 40 is the plate-shaped member being arranged in a manner of being contacted with the lower face of bent axle 67.Thrust plate 40
Thickness is, for example, about 1mm.Thrust plate 40 be set to the lower surface of the lower part bearing of journals 13 and lower silencer 76A upper surface it
Between.
It is configured to as follows, that is, it is (not shown to be equipped with centrifugal oil feed pump in the lower end of bent axle 67.), and by centrifugal
Oil feed pump sucks the lubricating oil 15 for being filled in 62 bottom of shell, and (does not scheme to the circulation flow path being arranged in an axial direction in bent axle 67
Show.) discharge.The lubricating oil 15 can supply the portion lubricated to needs such as upper bearing 70 and lower bearings 71 via circulation flow path
Position.
In thrust plate 40, the sliding area between bent axle 67 and thrust plate 40 is formed with groove portion 42.Groove portion 42 is only
Be formed as concavity in push plate 40, lubricating oil 15 is supplied from through hole 41.That is, groove portion 42 and centrifugal oil feed pump or being formed in bent axle
67 circulation flow path is connected.For rotary compressor 61, it also is provided with having and is said in screw compressor 1
The mutually isostructural thrust plate of bright situation 40.Also, lubricating oil 15 is filled in the sliding area of bent axle 67 and thrust plate 40 and shape
At oil film, so as to reduce friction loss.Also, the outboard end 42a of the radial direction of groove portion 42 is located at than above-mentioned sliding
Outermost circumference in region more in the inner part, therefore is supplied to the lubricating oil 15 of groove portion 42 it is difficult to outside from the inner circumferential side of sliding area
Side leaks.
Therefore, can not only reduce friction loss, and without reduce lubricating oil 15 amount can to the bearing of journals or
The sufficient lubricating oil of the supplies such as compression mechanism 15.As a result, it is possible to realize the raising of the high efficiency of compressor and reliability.For
Detailed structurally and functionally effect is repeated with the content illustrated in screw compressor 1, therefore is omitted.
Symbol description
Chamber, 6- upper axis bearing portion is discharged in 1- hermetic type screw compressors, 2- closed shells, 3- discharge caps, 4- upper covers, 5-
Part, 6A- journal bearing portions, 6B- thrust bearing divisions, 7- scroll compression bodies, 7A- lower silencers, 8- stators, 8A- stators around
Group, 9- rotors, 10- electro-motors, 11- bent axles, 12- crank-pins, the lower parts the 13- bearing of journals, 14- displacement type oil feed pumps, 15- profits
Lubricating oil, 16- intake lines, 17- circulation flow paths, 18- fixed scrolls, 18A- end plates, 18B- vortex shape vortex rings, 19- revolutions are vortexed,
19A- end plates, 19B- vortex shape vortex rings, 19C- bearing hubs, 20- discharge chambes, 21- rotation dampening mechanisms, 22- driver bushings,
24- outlets, 25- sheet packings, 26- sheet packings, 27- sucking pipings, 28- suction inlets, 29- dump valves, 30- discharges
Piping, 40- thrust plates, 41- through holes, 42- groove portions, 42a- outboard ends, 45- pump rotors, 51- circulation flow paths, 61- rotation pressures
Contracting machine, 62- shells, the centers 62A- shell, 62B- upper bodies, 62C- lower cases, 63- rotation/compression mechanisms, the electronic horses of 64-
It reaches, 65- stators, 66- rotors, 67- bent axles, 67A- eccentric parts, 68- cylinder chamber, 69- cylinder main bodies, 70- upper bearings, under 71-
Portion's bearing, 72- rotors, 73- suction lines, 74- air storage chambers, the tops 75- muffler room, the tops 75A- muffler, the noise reduction of the lower parts 76-
Device room, 76A- lower silencers, 77- discharge pipings, 78- bolts.
Claims (5)
1. a kind of fluid machinery, has：
Circular plate portion has the through hole to circulate for lubricating oil；And
Bent axle is placed in the upper surface of the plate portion, and the internal institute for being formed with the through hole for use by the plate portion
The circulation flow path of lubricating oil circulation is stated,
In the sliding area of the bent axle and the plate portion, being at least formed in any one in the bent axle and the plate portion
The concave groove portion of the lubricating oil is supplied from the through hole,
The outboard end of the radial direction of the groove portion is located at more in the inner part than the outermost circumference in the sliding area.
2. fluid machinery according to claim 1, wherein
The outboard end of the radial direction of the groove portion is located at than most inner peripheral portion and the outermost circumference in the sliding area
Between centre position it is more outward.
3. fluid machinery according to claim 1 or 2, wherein
Be formed in the sliding area area in the region of the groove portion relative in the sliding area than the groove portion
The outboard end gross area more in the inner part of radial direction be 50% or more and 80% or less.
4. fluid machinery according to any one of claim 1 to 3, wherein
In the inboard portion of the radial direction of the groove portion or half with the groove portion in the bent axle or the plate portion
The part that the inboard portion in diameter direction is opposite is formed with the conical surface.
5. fluid machinery according to any one of claim 1 to 4, wherein
The groove portion has ladder-like, taper or recess.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-042113 | 2016-03-04 | ||
| JP2016042113A JP6758867B2 (en) | 2016-03-04 | 2016-03-04 | Fluid machine |
| PCT/JP2017/008086 WO2017150603A1 (en) | 2016-03-04 | 2017-03-01 | Fluid machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108350869A true CN108350869A (en) | 2018-07-31 |
| CN108350869B CN108350869B (en) | 2020-03-24 |
Family
ID=59742967
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201780003768.6A Active CN108350869B (en) | 2016-03-04 | 2017-03-01 | Fluid machinery |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3369931B1 (en) |
| JP (1) | JP6758867B2 (en) |
| CN (1) | CN108350869B (en) |
| WO (1) | WO2017150603A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113330215A (en) * | 2019-01-31 | 2021-08-31 | 三菱电机株式会社 | Sliding bearing structure and scroll compressor |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2020165314A (en) * | 2019-03-28 | 2020-10-08 | 三菱重工サーマルシステムズ株式会社 | Compressor |
| JP2022026427A (en) * | 2020-07-31 | 2022-02-10 | 株式会社小松製作所 | Guide device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3182901A (en) * | 1963-11-12 | 1965-05-11 | Westinghouse Electric Corp | Compressor |
| JPS5118486Y2 (en) * | 1971-05-24 | 1976-05-17 | ||
| US4131396A (en) * | 1977-04-07 | 1978-12-26 | Sundstrand Corporation | Hermetic compressor lubrication system with two-stage oil pump |
| US4325679A (en) * | 1980-07-22 | 1982-04-20 | White Consolidated Industries, Inc. | Oil pump for hermetic compressor |
| CN103827499A (en) * | 2011-09-28 | 2014-05-28 | 大金工业株式会社 | Compressor |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3830341A (en) * | 1972-11-24 | 1974-08-20 | Carrier Corp | Lubrication system for a motor compressor unit |
| US3926281A (en) * | 1974-03-21 | 1975-12-16 | Tecumseh Products Co | Compressor oil pump with filter |
| JPS5911184U (en) * | 1982-07-13 | 1984-01-24 | ダイキン工業株式会社 | Lubrication mechanism of hermetic compressor |
-
2016
- 2016-03-04 JP JP2016042113A patent/JP6758867B2/en active Active
-
2017
- 2017-03-01 EP EP17760067.3A patent/EP3369931B1/en active Active
- 2017-03-01 WO PCT/JP2017/008086 patent/WO2017150603A1/en active Application Filing
- 2017-03-01 CN CN201780003768.6A patent/CN108350869B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3182901A (en) * | 1963-11-12 | 1965-05-11 | Westinghouse Electric Corp | Compressor |
| JPS5118486Y2 (en) * | 1971-05-24 | 1976-05-17 | ||
| US4131396A (en) * | 1977-04-07 | 1978-12-26 | Sundstrand Corporation | Hermetic compressor lubrication system with two-stage oil pump |
| US4325679A (en) * | 1980-07-22 | 1982-04-20 | White Consolidated Industries, Inc. | Oil pump for hermetic compressor |
| CN103827499A (en) * | 2011-09-28 | 2014-05-28 | 大金工业株式会社 | Compressor |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113330215A (en) * | 2019-01-31 | 2021-08-31 | 三菱电机株式会社 | Sliding bearing structure and scroll compressor |
| CN113330215B (en) * | 2019-01-31 | 2023-02-17 | 三菱电机株式会社 | Sliding bearing structure and scroll compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108350869B (en) | 2020-03-24 |
| EP3369931B1 (en) | 2021-03-31 |
| WO2017150603A1 (en) | 2017-09-08 |
| JP2017155718A (en) | 2017-09-07 |
| EP3369931A1 (en) | 2018-09-05 |
| JP6758867B2 (en) | 2020-09-23 |
| EP3369931A4 (en) | 2018-12-12 |
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