CN106014979A - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
- Publication number
- CN106014979A CN106014979A CN201610539504.XA CN201610539504A CN106014979A CN 106014979 A CN106014979 A CN 106014979A CN 201610539504 A CN201610539504 A CN 201610539504A CN 106014979 A CN106014979 A CN 106014979A
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- CN
- China
- Prior art keywords
- bearing
- mating holes
- orbiter
- clutch shaft
- screw compressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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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
- F04C18/0223—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 with symmetrical double wraps
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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
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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
- F04C2240/00—Components
- F04C2240/50—Bearings
Abstract
The invention provides a scroll compressor. The scroll compressor comprises an enclosure, a static scroll plate, a support, a dynamic scroll plate, a driving part, a matching part, a hinge pin and a first antifriction part, wherein the static scroll plate is arranged in the enclosure; the support is arranged in the enclosure and connected with the static scroll plate; the dynamic scroll plate is clamped between the static scroll plate and the support and matched with the static scroll plate; the driving part penetrates a yielding hole in the support and drives the dynamic scroll plate to conduct eccentric motion; the matching part comprises a first matching hole and a second matching hole, one of the first matching hole and the second matching hole is formed in the dynamic scroll plate, and the other one is formed in the support; the hinge pin is arranged between the support and the dynamic scroll plate and comprises a first shaft segment and a second shaft segment, and the second shaft segment can do circular motion in the second matching hole; and the first antifriction part is arranged between the hole wall of the second matching hole and the second shaft segment, matched with the second shaft segment and used for reducing friction between the hinge pin and the hole wall of the second matching hole. By application of the technical scheme, the problem of high production cost of a scroll compressor in the prior art can be effectively solved.
Description
Technical field
The present invention relates to field of air conditioning, in particular to a kind of screw compressor.
Background technology
Air-conditioner vehicle air-conditioning screw compressor is frequently with fog lubrication, and lubricant effect passes through feed lubrication than conventional vortex compressor
Weak effect.Therefore generally use ball anti-rotation mechanism to prevent orbiter rotation at air-conditioner vehicle screw compressor.As
Shown in Fig. 1, ball anti-rotation mechanism 1 replaces sliding friction with rolling friction, improves friction pair, but ball grooves orifice plate is processed
Required precision is high, and processed complex, assembly difficulty are high, thus adds the production cost of screw compressor.
Summary of the invention
A kind of screw compressor of offer is provided, becomes solving the production of screw compressor of the prior art
This high problem.
To achieve these goals, the invention provides a kind of screw compressor, including: casing；Fixed scroll, is arranged on machine
In shell；Support, in being arranged on casing and is connected with fixed scroll, support has and dodges hole；Orbiter, is folded in quiet whirlpool
Between capstan and support, orbiter cooperates with fixed scroll；Drive division, is located in and dodges in hole, drive division and dynamic whirlpool
Capstan connects to drive orbiter eccentric motion；Auxiliary section, including the first mating holes being oppositely arranged and the second mating holes, the
One in one mating holes and the second mating holes is arranged on orbiter, and another in the first mating holes and the second mating holes sets
Put on support；Bearing pin, is arranged between support and orbiter, and bearing pin includes the first shaft part being arranged in the first mating holes
And the second shaft part being arranged in the second mating holes, the second shaft part can circle in the second mating holes；First antifriction
Part, is arranged between the hole wall of the second mating holes and the second shaft part and coordinates with the second shaft part, coordinates in order to reduce bearing pin and second
Friction between the hole wall in hole.
Further, the first antifriction part includes that clutch shaft bearing, clutch shaft bearing are fixed in the second mating holes, the second shaft part and first
The inwall of bearing coordinates.
Further, screw compressor also includes that the second antifriction part, the second antifriction part are arranged on the hole wall and first of the first mating holes
Between shaft part, to reduce the friction between the hole wall of bearing pin and the first mating holes.
Further, the second antifriction part is the second bearing, and the inwall of the first shaft part and the second bearing coordinates.
Further, clutch shaft bearing and the second bearing are rolling bearing, the inner ring interference fit of the first shaft part and the second bearing.
Further, the internal diameter D of clutch shaft bearing1=2r+d+t, wherein r is the eccentric arm of fixed scroll, and d is the diameter of bearing pin,
T is target offset.
Further, clutch shaft bearing is sliding bearing or wear-resisting steel loop, and the second bearing is rolling bearing, the first shaft part and the second axle
The inner ring interference fit held, clutch shaft bearing is arranged on orbiter, and the second bearing is arranged on support.
Further, the internal diameter D of clutch shaft bearing2=2r+d, wherein r is the eccentric arm of fixed scroll, and d is the diameter of bearing pin.
Further, the first mating holes is arranged on orbiter, and the second mating holes is arranged on support, and the first shaft part is with interference
Being arranged in the first mating holes, clutch shaft bearing is rolling bearing, and the first antifriction part also includes the company that the inner ring with clutch shaft bearing coordinates
Female connector, the second shaft part is coordinated with the inner ring of clutch shaft bearing by adapter sleeve.
Further, adapter sleeve includes the first cylindrical portion and is arranged on the connection post of the first cylindrical portion bottom, connects post towards propping up
Frame extends and coordinates with the inner ring of clutch shaft bearing, and the inwall of the first cylindrical portion forms rotation space, and the second shaft part stretches into rotation space
In and coordinate with the inwall of the first cylindrical portion.
Further, the internal diameter of the first cylindrical portion is equal to D3=2r+d+t, wherein r is the eccentric arm of fixed scroll, and d is bearing pin
Diameter, t is target offset.
Further, drive division includes bent axle and the eccentric rotary portion being connected with bent axle, and bent axle is located in dodges in hole, eccentric
Rotation section is arranged between bent axle and orbiter.
Further, eccentric rotary portion includes eccentric bushing and the 3rd bearing being arranged between orbiter and eccentric bushing, eccentric
Set includes the second cylindrical portion and is arranged on the biasing post of the second cylindrical portion bottom, and biasing post extends and with the 3rd towards orbiter
The inner ring of bearing coordinates, the second cylindrical portion and the one end fits of bent axle.
Further, the inwall of the second cylindrical portion forms installing hole, in one end of bent axle stretches to installing hole and with installing hole gap
Coordinate.
Application technical scheme, screw compressor includes the first mating holes and the second mating holes being oppositely arranged.Bearing pin,
Being arranged between support and orbiter, the first shaft part of bearing pin is arranged in the first mating holes, and the second shaft part of bearing pin is arranged on
In second mating holes.First antifriction part, is arranged between the hole wall of the second mating holes and the second shaft part and coordinates with the second shaft part.
When the orbiter of screw compressor rotates relative to fixed scroll, the second shaft part of bearing pin makees circumference fortune in the first antifriction part
Dynamic.When the orbiter of screw compressor has the trend of rotation, the second shaft part of bearing pin and the first antifriction part interference are to play
The effect of anti-rotation.Said structure has a three below advantage: the first, said structure can reduce bearing pin and the second mating holes
Friction between hole wall, improves local and burns phenomenon, reduce power consumption so that compressor can the operating of high-speed and high-efficiency ground.The second,
Assembling between above-mentioned bearing pin and antifriction part is simple, facilitate installation to improve production efficiency.3rd, the processing of above-mentioned bearing pin is simple,
Scrappage is low, and stock utilization is high, thus reduces production cost, and the production solving screw compressor of the prior art becomes
This high problem.
Accompanying drawing explanation
The Figure of description of the part constituting the application is used for providing a further understanding of the present invention, and the present invention's is schematic real
Execute example and illustrate for explaining the present invention, being not intended that inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 shows the structural representation of ball anti-rotation mechanism of the prior art；
Fig. 2 shows the vertical profile structural representation of the embodiment one of the screw compressor according to the present invention；
Fig. 3 shows the structural representation of the holder part of the anti-rotation mechanism of the screw compressor of Fig. 2；
Fig. 4 shows the perspective view of the fixed scroll part of the anti-rotation mechanism of Fig. 2；
Fig. 5 shows the structure for amplifying schematic diagram at the C of the screw compressor of Fig. 2；
Fig. 6 shows the partial vertical sectional structural representation of the embodiment two of the screw compressor according to the present invention；And
Fig. 7 shows the partial vertical sectional structural representation of the embodiment three of the screw compressor according to the present invention.
Wherein, above-mentioned accompanying drawing includes the following drawings labelling:
10, casing；20, fixed scroll；30, support；40, orbiter；50, drive division；51, bent axle；52, inclined
Heart rotation section；521, eccentric bushing；5211, the second cylindrical portion；5212, biasing post；522, the 3rd bearing；61, first coordinates
Hole；62, the second mating holes；70, bearing pin；81, clutch shaft bearing；82, adapter sleeve；821, the first cylindrical portion；822, even
Connect post；90, the second bearing；100, off-centre operation.
Detailed description of the invention
It should be noted that in the case of not conflicting, the embodiment in the application and the feature in embodiment can be mutually combined.
Describe the present invention below with reference to the accompanying drawings and in conjunction with the embodiments in detail.
As shown in Figures 2 to 5, the screw compressor of embodiment one includes casing 10, fixed scroll 20, support 30, dynamic vortex
Dish 40, drive division 50, auxiliary section, bearing pin 70 and the first antifriction part.Wherein, in fixed scroll 20 is arranged on casing 10.
In support 30 is arranged on casing 10 and it is connected with fixed scroll 20, support 30 has and dodges hole.Orbiter 40 is folded in
Between fixed scroll 20 and support 30, orbiter 40 cooperates with fixed scroll 20.Drive division 50 is located in dodges hole
In, drive division 50 is connected with orbiter 40 to drive orbiter 40 eccentric motion.Auxiliary section includes first be oppositely arranged
Mating holes 61 and the second mating holes 62, one in the first mating holes 61 and the second mating holes 62 is arranged on orbiter 40,
Another in first mating holes 61 and the second mating holes 62 is arranged on support 30.Bearing pin 70 is arranged on support 30 and dynamic whirlpool
Between capstan 40, bearing pin 70 includes the first shaft part being arranged in the first mating holes 61 and is arranged in the second mating holes 62
The second shaft part, the second shaft part can circle in the second mating holes 62.First antifriction part, is arranged on the second mating holes
Coordinate between hole wall and second shaft part of 62 and with the second shaft part, in order to reduce between bearing pin 70 and the hole wall of the second mating holes 62
Friction.
The technical scheme of application the present embodiment, screw compressor includes the first mating holes 61 and the second mating holes 62 being oppositely arranged.
Bearing pin 70, is arranged between support 30 and orbiter 40, and the first shaft part of bearing pin 70 is arranged in the first mating holes 61,
Second shaft part of bearing pin 70 is arranged in the second mating holes 62.First antifriction part, is arranged on the hole wall and of the second mating holes 62
Coordinate between two shaft parts and with the second shaft part.When the orbiter 40 of screw compressor is relative to fixed scroll 20 eccentric motion,
Second shaft part of bearing pin 70 circles in the first antifriction part.When the orbiter 40 of screw compressor has the trend of rotation
Time, the second shaft part of bearing pin 70 and the first antifriction part interference are to play the effect of anti-rotation.It is excellent that said structure has three below
Point: the first, said structure can reduce the friction between bearing pin 70 and the hole wall of the second mating holes 62, improves local and burns existing
As, reduce power consumption so that compressor can the operating of high-speed and high-efficiency ground.The second, the dress between above-mentioned bearing pin 70 and the first antifriction part
Join simple, facilitate installation to improve production efficiency.3rd, the part of above-mentioned bearing pin 70 is simple, processing is easy ensures, scrappage is low,
Stock utilization is high, thus reduces production cost, solves the problem that the production cost of screw compressor of the prior art is high.
As shown in Fig. 2, Fig. 3 and Fig. 5, in embodiment one, the first antifriction part includes clutch shaft bearing 81, and clutch shaft bearing 81 is solid
Being scheduled in the second mating holes 62, the second shaft part coordinates with the inwall of clutch shaft bearing 81.Specifically, when the dynamic whirlpool of screw compressor
When capstan 40 is relative to fixed scroll 20 eccentric motion, the second shaft part of bearing pin 70 coordinates at the inwall of clutch shaft bearing 81, and
Circle in the inwall of clutch shaft bearing 81.When the orbiter 40 of screw compressor has the trend of rotation, bearing pin 70
The inwall interference engagement of the second shaft part and clutch shaft bearing 81 thus play the effect of anti-rotation.Above-mentioned clutch shaft bearing 81 is standard
Part, part generalization degree is high, easily purchases, changes and easy to maintenance.Additionally, use the coordinated scheme of bearing pin and bearing,
Assembly part is reduced, and fitted position is prone to ensure.
As shown in Fig. 2, Fig. 4 and Fig. 5, in embodiment one, screw compressor also includes that the second antifriction part, the second antifriction part set
Put between the hole wall and the first shaft part of the first mating holes 61, to reduce rubbing between bearing pin 70 and the hole wall of the first mating holes 61
Wipe.Said structure can reduce the friction between bearing pin 70 and the hole wall of the first mating holes 61, thus improve local further and burn
Bright phenomenon, reduces power consumption so that compressor can more high-speed and high-efficiency ground operating.
As shown in Fig. 2, Fig. 4 and Fig. 5, in embodiment one, the second antifriction part is the second bearing 90, the first shaft part and second
The inwall of bearing 90 coordinates.Above-mentioned second bearing 90 is standard component, it is easy to buying.Additionally, use coordinating of bearing pin and bearing
Scheme so that Assembly part reduces, fitted position is prone to ensure.
As shown in Figures 2 to 5, in embodiment one, clutch shaft bearing 81 and the second bearing 90 are rolling bearing, the first axle
Section and the inner ring interference fit of the second bearing 90.Specifically, when the orbiter 40 of screw compressor is relative to fixed scroll 20
During eccentric motion, the second shaft part of bearing pin 70 and the contact internal walls of clutch shaft bearing 81, under the effect of contact friction force, bearing pin
70 around the center rotating of the second bearing 90, it is achieved bearing pin 70 rolls in the inwall of clutch shaft bearing 81, thus becomes slip for rolling
Friction.Use the rolling friction can to improve due to bad the brought a large amount of sliding frictions heat of fog lubrication, it is to avoid parts locally
Burn the generation of phenomenon, thus reduce power consumption so that compressor can high-speed and high-efficiency operating.Preferably, clutch shaft bearing 81 He
Second bearing 90 can use the bearing of sealing, self-lubricating.Said structure can improve compressor lubrication unfavorable condition further,
And play anti-miscellaneous effect, thus improve model machine maintainability.
It should be noted that clutch shaft bearing 81 can be arranged on support, the second bearing 90 be arranged on orbiter 40 (as
Shown in Fig. 5).Clutch shaft bearing 81 can also be arranged on orbiter 40, and the second bearing 90 is arranged on support (in figure not
Illustrate).Above two scheme works principle is consistent with the effect played, and does not repeats them here.It addition, again in embodiment one,
Bearing pin 70 is not acted on by axial force, and therefore bearing pin 70 interference can be played in the inwall of the second bearing 90
Axial limiting effect, prevents bearing pin 70 axial float.
Also, it should be noted in embodiment one, clutch shaft bearing the 81, second bearing 90 and bearing pin 70 form anti-rotation mechanism.
In the present embodiment, such anti-rotation mechanism is multiple, is arranged on support 30 with clutch shaft bearing 81, and the second bearing 90 sets
As a example by putting on orbiter 40, clutch shaft bearing 81 is arranged circumferentially on support 30, and the second bearing 90 is arranged circumferentially in dynamic whirlpool
On capstan 40, multiple clutch shaft bearings 81 and multiple second bearing 90 one_to_one corresponding.One group of corresponding clutch shaft bearing 81 and
It is provided with bearing pin 70 between two bearings 90.
It is arranged on support with clutch shaft bearing 81 below, as a example by the second bearing 90 is arranged on orbiter 40, simply introduces one
Lower installation process:
First by the first shaft part force fit of bearing pin 70 to the inwall of the second bearing 90, will be equipped with bearing pin 70 He the most again
The outer wall force fit of the assembly of the second bearing 90 in the hole wall of the first mating holes 61 of orbiter 40 as dynamic disk component.
Then by the hole wall of the second mating holes 62 on the outer wall force fit of clutch shaft bearing 81 to support 30.Now, will be equipped with
The dynamic disk component of bearing pin 70 and the second bearing 90 is assembled on support 30, and the second shaft part of bearing pin 70 is inserted into clutch shaft bearing
In the inwall of 81.
As it is shown on figure 3, in embodiment one, rotate for suppression orbiter 40 self, also need to meet following size relationship.Tool
Body ground, the internal diameter D of clutch shaft bearing 811=2r+d+t, wherein r is the eccentric arm of fixed scroll 20, and d is the diameter of bearing pin 70,
T is target offset.It is to say, move clockwise or counterclockwise when orbiter 40 is eccentric arm r along off-centre operation 100 track
Time, because the internal diameter of clutch shaft bearing 81 meets above-mentioned relation, the bearing pin 70 on orbiter 40 can be by clutch shaft bearing 81 inwall
Constraint and can not rotation.Specifically, meet above-mentioned relation when the internal diameter of clutch shaft bearing 81 and orbiter 40 operates to Fig. 3
In location A time, bearing pin 70 can run to the position of 70A in Fig. 3, and bearing pin 70 is by the radial direction side of clutch shaft bearing 81 inwall
To constraint so that orbiter 40 can not rotation.In like manner, when orbiter 40 operates the B location to Fig. 3, pin
Axle 70 can run to the position of 70B in Fig. 3, and bearing pin 70 is by the retraining of radial direction of clutch shaft bearing 81 inwall so that dynamic
Scroll plate 40 can not rotation.Preferably, target offset scope t is between 0.02mm～0.12mm.
It should be noted that and work as D1> 2r+d, and when orbiter 40 moves, meeting between inwall and the bearing pin 70 of clutch shaft bearing 81
There is gap, do not contact.If above-mentioned gap-ratio target offset scope t is much larger, the inwall of clutch shaft bearing 81 is to pin
Axle 70 does not has effect of contraction, and orbiter 40 self also can occur rotation while off-centre operation 100 revolution, bearing pin 70,
The anti-rotation mechanism that clutch shaft bearing 81 and the second bearing 90 are formed will lose the effect preventing orbiter 40 rotation.And work as
D1< during 2r+d, orbiter 40 is under bias is assembled, and bearing pin 70 can exist Assembly Interference with the inwall of clutch shaft bearing 81, makes
Obtain bearing pin 70 to assemble in the inwall less than clutch shaft bearing 81.
As in figure 2 it is shown, in embodiment one, drive division 50 includes bent axle 51 and the eccentric rotary portion 52 being connected with bent axle 51,
Bent axle 51 is located in dodges in hole, and eccentric rotary portion 52 is arranged between bent axle 51 and orbiter 40.Said structure is simple,
It is easily achieved.
As in figure 2 it is shown, in embodiment one, eccentric rotary portion 52 includes eccentric bushing 521 and is arranged on orbiter 40 He
The 3rd bearing 522 between eccentric bushing 521, eccentric bushing 521 includes the second cylindrical portion 5211 and is arranged on the second cylindrical portion 5211
The biasing post 5212 of bottom, biasing post 5212 extends towards orbiter 40 and coordinates with the inner ring of the 3rd bearing 522, second
Cylindrical portion 5211 and the one end fits of bent axle 51.Specifically, when bent axle 51 rotates, due to the second cylindrical portion 5211 and bent axle
The one end fits of 51, therefore the second cylindrical portion 5211 together can rotate along with bent axle 51.Owing to biasing post 5212 is arranged prejudicially
In the second cylindrical portion 5211 (biasing post 5212 is misaligned with the axis of bent axle 51), therefore biasing post 5212 can eccentric rotary.
Owing to the inner ring of biasing post 5212 with the 3rd bearing 522 coordinates, the 3rd bearing 522 is arranged on orbiter 40, therefore moves
Scroll plate 40 also can eccentric rotary.Said structure is simple, be easily achieved.Preferably, above-mentioned bent axle 51 and the second cylindrical portion 5211
Linked together by pin.
When assembling quantity more than 3 due to bearing pin 70, interference may be there is, the problem producing bad assembling.For understanding
Certainly this problem, as in figure 2 it is shown, in embodiment one, the inwall of the second cylindrical portion 5211 forms installing hole, the one of bent axle 51
End stretch in installing hole and with installing hole matched in clearance.Said structure is capable of the regulation of radial compliance offset, eccentric bushing 521
Circumference certain slewing area, bent axle 51 can be had can to produce relatively rotating in the range of 0 ° to 5 ° with the second cylindrical portion 5211,
Thus solve the problem that bearing pin 70 is easily interferenceed with the inwall of clutch shaft bearing 81.
If it should be noted that D1< if 2r+d, one end of above-mentioned bent axle 51 is used to stretch in installing hole and and installing hole
The scheme of matched in clearance, is assembled to the inner wall of clutch shaft bearing 81, the inwall of clutch shaft bearing 81 and bearing pin 70 by bearing pin 70
Though orbiter 40 rotation can be prevented intimate contact constraint, but pump housing radial clearance now may be made excessive, cause interior leakage
Phenomenon.Therefore the internal diameter of clutch shaft bearing 81 controls at D1=2r+d+ (0.02～0.12) mm scope, can control rationally to suppress dynamic
Scroll plate 40 rotation, it is to avoid the phenomenon revealed in the pump housing occurs.
As shown in Figure 6, the screw compressor of embodiment two is with the difference of embodiment one: clutch shaft bearing 81 for sliding bearing or
Wear-resisting steel loop, the second bearing 90 is rolling bearing, the first shaft part and the inner ring interference fit of the second bearing 90, clutch shaft bearing 81
Being arranged on orbiter 40, the second bearing 90 is arranged on support 30.When screw compressor orbiter 40 relative to
During fixed scroll 20 eccentric motion, bearing pin 70 and the contact internal walls of clutch shaft bearing 81, bearing pin 70 can be around the second bearing 90 center
Rotate, and realize bearing pin 70 and roll on clutch shaft bearing 81 inwall, it is achieved sliding friction is converted to rolling friction, reduces and rubs
Wipe power consumption, finally improve performance.
Following is a brief introduction of installation process:
Bearing pin 70 is arranged on support 30 by the second bearing 90, bearing pin 70 interference at the inner wall of the second bearing 90, the
The outer wall interference of two bearings 90, on support 30, orbiter 40 offers the second mating holes 62, and clutch shaft bearing 81 accommodates
In the second mating holes 62, clutch shaft bearing 81 and the second mating holes 62 matched in clearance, fit clearance controls 0.02mm～0.12mm
Scope.
In embodiment two, the internal diameter D of clutch shaft bearing 812=2r+d, wherein r is the eccentric arm of fixed scroll 20, and d is pin
The diameter of axle 70.Principle is similar to embodiment one and does not repeats them here.
As it is shown in fig. 7, the difference of the screw compressor of embodiment three and embodiment one is: the first shaft part and the first mating holes 61
Between matching relationship.Specifically, the first mating holes 61 is arranged on orbiter 40, and the second mating holes 62 is arranged on support
On 30, the first shaft part is arranged in the first mating holes 61 with interference, and clutch shaft bearing 81 is rolling bearing, and the first antifriction part also wraps
Including the adapter sleeve 82 that the inner ring with clutch shaft bearing 81 coordinates, the second shaft part is coordinated with the inner ring of clutch shaft bearing 81 by adapter sleeve 82.
As it is shown in fig. 7, in embodiment three, adapter sleeve 82 includes the first cylindrical portion 821 and is arranged on the first cylindrical portion 821
The connection post 822 of bottom, connects post 822 and extends towards support 30 and coordinate with the inner ring of clutch shaft bearing 81, the first cylindrical portion
The inwall of 821 forms rotation space, and the second shaft part stretches in rotation space and coordinates with the inwall of the first cylindrical portion 821.Specifically,
When the orbiter 40 of screw compressor is relative to fixed scroll 20 eccentric motion, bearing pin 70 is interior with the first cylindrical portion 821
Wall contacts, and under the effect of frictional force, bearing pin 70 promotes whole adapter sleeve 82 around the center rotating of clutch shaft bearing 81, it is achieved pin
Sliding friction between axle 70 and the inwall of the first cylindrical portion 821 is converted to rolling friction, reduces friction power loss so that compressor
Can the operating of high-speed and high-efficiency ground.
Following is a brief introduction of installation process:
Bearing pin 70 interference is on orbiter 40, and adapter sleeve 82 has the first cylindrical portion 821 and is connected to the first cylindrical portion 821
On connection post 822, the inwall of the first cylindrical portion 821 is coated with high-abrasive material, connects post 822 and clutch shaft bearing 81 endoporus interference,
Being arranged on support 30, the first cylindrical portion 821 can be around clutch shaft bearing 81 center rotating.
In embodiment three, the internal diameter of the first cylindrical portion 821 is equal to D3=2r+d+t, wherein r is the eccentric arm of fixed scroll 20,
D is the diameter of bearing pin 70, and t is target offset.Preferably, target offset scope t is between 0.02mm～0.12mm.Principle
It is similar to embodiment one do not repeat them here.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for those skilled in the art
For, the present invention can have various modifications and variations.All within the spirit and principles in the present invention, any amendment of being made, etc.
With replacement, improvement etc., should be included within the scope of the present invention.
Claims (14)
1. a screw compressor, it is characterised in that including:
Casing (10)；
Fixed scroll (20), is arranged in described casing (10)；
Support (30), is arranged in described casing (10) and is connected with described fixed scroll (20), described support (30)
On have and dodge hole；
Orbiter (40), is folded between described fixed scroll (20) and described support (30), described orbiter
(40) cooperate with described fixed scroll (20)；
Drive division (50), be located in described in dodge in hole, described drive division (50) is connected with described orbiter (40)
To drive described orbiter (40) eccentric motion；
Auxiliary section, including the first mating holes (61) being oppositely arranged and the second mating holes (62), described first mating holes (61)
It is arranged on described orbiter (40) with in described second mating holes (62), described first mating holes (61)
It is arranged on described support (30) with another in described second mating holes (62)；
Bearing pin (70), is arranged between described support (30) and described orbiter (40), and described bearing pin (70) wraps
Include the first shaft part being arranged in described first mating holes (61) and be arranged in described second mating holes (62)
Two shaft parts, described second shaft part can circle in described second mating holes (62)；
First antifriction part, is arranged between hole wall and described second shaft part of described second mating holes (62) and with described
Two shaft parts coordinate, in order to reduce the friction between the hole wall of described bearing pin (70) and described second mating holes (62).
Screw compressor the most according to claim 1, it is characterised in that described first antifriction part includes clutch shaft bearing (81),
Described clutch shaft bearing (81) is fixed in described second mating holes (62), described second shaft part and described clutch shaft bearing (81)
Inwall coordinate.
Screw compressor the most according to claim 2, it is characterised in that described screw compressor also includes the second antifriction part,
Described second antifriction part is arranged between hole wall and described first shaft part of described first mating holes (61), described to reduce
Friction between the hole wall of bearing pin (70) and described first mating holes (61).
Screw compressor the most according to claim 3, it is characterised in that described second antifriction part is the second bearing (90), institute
State the first shaft part to coordinate with the inwall of described second bearing (90).
Screw compressor the most according to claim 4, it is characterised in that described clutch shaft bearing (81) and described second bearing
(90) it is rolling bearing, described first shaft part and the inner ring interference fit of described second bearing (90).
Screw compressor the most according to claim 5, it is characterised in that the internal diameter D of described clutch shaft bearing (81)1=2r+d+t,
Wherein said r is the eccentric arm of described fixed scroll (20), and described d is the diameter of described bearing pin (70), described t
For target offset.
Screw compressor the most according to claim 4, it is characterised in that described clutch shaft bearing (81) is sliding bearing or resistance to
Mill steel loop, described second bearing (90) is rolling bearing, described first shaft part and the inner ring of described second bearing (90)
Interference fit, described clutch shaft bearing (81) is arranged on described orbiter (40), and described second bearing (90) sets
Put on described support (30).
Screw compressor the most according to claim 7, it is characterised in that the internal diameter D of described clutch shaft bearing (81)2=2r+d,
Wherein said r is the eccentric arm of described fixed scroll (20), and described d is the diameter of described bearing pin (70).
Screw compressor the most according to claim 2, it is characterised in that described first mating holes (61) is arranged on described dynamic
In scroll plate (40), described second mating holes (62) is arranged on described support (30), described first shaft part interference
Be arranged on described first mating holes (61) in, described clutch shaft bearing (81) is rolling bearing, described first antifriction part
Also including the adapter sleeve (82) coordinated with the inner ring of described clutch shaft bearing (81), described second shaft part passes through described adapter sleeve
(82) inner ring with described clutch shaft bearing (81) coordinates.
Screw compressor the most according to claim 9, it is characterised in that described adapter sleeve (82) includes the first cylindrical portion (821)
And it being arranged on the connection post (822) of described first cylindrical portion (821) bottom, described connection post (822) is towards described
Support (30) extends and coordinates with the inner ring of described clutch shaft bearing (81), the inwall shape of described first cylindrical portion (821)
Becoming rotation space, described second shaft part stretches in described rotation space and coordinates with the inwall of described first cylindrical portion (821).
11. screw compressors according to claim 10, it is characterised in that the internal diameter of described first cylindrical portion (821) is equal to
D3=2r+d+t, wherein said r are the eccentric arm of described fixed scroll (20), and described d is described bearing pin (70)
Diameter, described t is target offset.
12. screw compressors according to claim 1, it is characterised in that described drive division (50) include bent axle (51) with
And the eccentric rotary portion (52) being connected with described bent axle (51), described bent axle (51) be located in described in dodge in hole, institute
State eccentric rotary portion (52) to be arranged between described bent axle (51) and described orbiter (40).
13. screw compressors according to claim 12, it is characterised in that described eccentric rotary portion (52) includes eccentric bushing (521)
And the 3rd bearing (522) being arranged between described orbiter (40) and described eccentric bushing (521), described bias
Set (521) includes the second cylindrical portion (5211) and is arranged on the biasing post (5212) of described second cylindrical portion (5211) bottom,
Described biasing post (5212) extends towards described orbiter (40) and coordinates with the inner ring of described 3rd bearing (522),
Described second cylindrical portion (5211) and the one end fits of described bent axle (51).
14. screw compressors according to claim 13, it is characterised in that the inwall of described second cylindrical portion (5211) is formed
Installing hole, one end of described bent axle (51) stretch in described installing hole and with described installing hole matched in clearance.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610539504.XA CN106014979B (en) | 2016-07-08 | 2016-07-08 | Screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610539504.XA CN106014979B (en) | 2016-07-08 | 2016-07-08 | Screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106014979A true CN106014979A (en) | 2016-10-12 |
| CN106014979B CN106014979B (en) | 2018-06-26 |
Family
ID=57109014
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610539504.XA Active CN106014979B (en) | 2016-07-08 | 2016-07-08 | Screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106014979B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107605726A (en) * | 2017-09-04 | 2018-01-19 | 珠海格力电器股份有限公司 | Screw compressor and there is its air conditioner |
| CN112901486A (en) * | 2021-01-25 | 2021-06-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Move vortex dish balance structure, scroll compressor and air conditioner |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002005050A (en) * | 2000-06-20 | 2002-01-09 | Fujitsu General Ltd | Scroll compressor |
| CN203035551U (en) * | 2012-12-20 | 2013-07-03 | 安徽省大富机电技术有限公司 | Scroll compressor, air conditioner and automobile |
| CN203670520U (en) * | 2014-01-09 | 2014-06-25 | 申科滑动轴承股份有限公司 | Insulated joint for bearings |
| CN205858666U (en) * | 2016-07-08 | 2017-01-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Screw compressor |
-
2016
- 2016-07-08 CN CN201610539504.XA patent/CN106014979B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002005050A (en) * | 2000-06-20 | 2002-01-09 | Fujitsu General Ltd | Scroll compressor |
| CN203035551U (en) * | 2012-12-20 | 2013-07-03 | 安徽省大富机电技术有限公司 | Scroll compressor, air conditioner and automobile |
| CN203670520U (en) * | 2014-01-09 | 2014-06-25 | 申科滑动轴承股份有限公司 | Insulated joint for bearings |
| CN205858666U (en) * | 2016-07-08 | 2017-01-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Screw compressor |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107605726A (en) * | 2017-09-04 | 2018-01-19 | 珠海格力电器股份有限公司 | Screw compressor and there is its air conditioner |
| CN112901486A (en) * | 2021-01-25 | 2021-06-04 | 珠海格力节能环保制冷技术研究中心有限公司 | Move vortex dish balance structure, scroll compressor and air conditioner |
| CN112901486B (en) * | 2021-01-25 | 2022-04-22 | 珠海格力节能环保制冷技术研究中心有限公司 | Move vortex dish balance structure, scroll compressor and air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106014979B (en) | 2018-06-26 |
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