CN1058456A - Scroll-type fluid machinery - Google Patents
Scroll-type fluid machinery Download PDFInfo
- Publication number
- CN1058456A CN1058456A CN91103680A CN91103680A CN1058456A CN 1058456 A CN1058456 A CN 1058456A CN 91103680 A CN91103680 A CN 91103680A CN 91103680 A CN91103680 A CN 91103680A CN 1058456 A CN1058456 A CN 1058456A
- Authority
- CN
- China
- Prior art keywords
- rotary vortex
- drive sleeve
- vortex body
- sleeve
- centrifugal force
- 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
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Classifications
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/003—Systems for the equilibration of forces acting on the elements of the machine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C1/00—Rotary-piston machines or engines
- F01C1/02—Rotary-piston machines or engines 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
- F01C1/0207—Rotary-piston machines or engines 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
- F01C1/0215—Rotary-piston machines or engines 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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention provides a kind of scroll-type fluid machinery, wherein: static volute body and rotary vortex body are meshing with each other by the heliconid of arranging respectively on its end plate, one drive sleeve is installed in rotation on from the sleeve that rotary vortex body end plate outer surface core stretches out, drive pin that stretches out from running shaft is slidably mounted in out in the sliding eye drive sleeve, it is characterized in that: the balancer weight gauge block that can eliminate the power energy imbalance of the rotary vortex body of doing planetary motion is arranged on the drive sleeve.Even when running shaft ran up, the contact pressure between the heliconid of static volute body and the heliconid of rotary vortex body can be not excessive yet in addition.
Description
The present invention relates to a kind of compressor, scroll-type fluid machinery of decompressor and similar machinery of being used as.
Japan Patent is text No.59-120794(No.120794/1984 openly temporarily) a kind of turning radius changeable mechanism in order to turning radius according to variation of gas pressure and when being applied to centrifugal force on the rotary vortex body of vortex-type compressor and changing rotary vortex body automatically and do planetary motion disclosed.
As shown in Figure 5 and Figure 6, in this mechanism, oscillation bearing 03 is installed in out in the sliding eye 02 on running shaft 01 upper-end surface, thereby can only be along the longitudinal sliding motion in hole and can not be around the axle rotation of self, divide the pin 05 that stretches out to be inserted in the oscillation bearing 03 downwards from the bottom central part of the end plate 04a of rotary vortex body 04, thereby can rotate with respect to this bearing.
In Fig. 5 and Fig. 6, heliconid 06b is arranged on the internal surface of static volute body 06 end plate 06a, be meshing with each other to form compression chamber 07 with the heliconid 04b on the internal surface that is arranged in rotary vortex body 04 end plate 04a, 08 is a framework, 09 is to bear the thrust bearing that acts on the thrust on the rotary vortex body 04,010 is the bearing of the upper end of a supporting rotating shaft 01, O
1Be the axle center of running shaft 01, O
2Be the center of pin 05, α is the true dip direction of sliding eye 02 and the angle between the eccentric direction.
When running shaft 01 was rotated by the similar device driving of motor not shown in the figures and other, sliding eye 02 was passed through in rotation, and oscillation bearing 03 and pin 05 pass on the rotary vortex body 04.Rotary vortex body 04 is done planetary motion along the circumference that with throw of eccentric r is radius, and rotary vortex body then is obstructed by the effect of certain mechanism not shown in the figures along the rotation of self axle.Therefore, when the volume of compression chamber 07 reduced, gas was inhaled into compression chamber 07, and to the central mobile of spiral, gas is gradually reduced and arrives central bore 012, and emits by air vent 011.
When rotary vortex body 04 is done the moving operation of planet, in rotary vortex body 04 upper edge eccentric direction effect a centrifugal force Fc is arranged, gas in the compression chamber 07 has a gas load Fg along the directive effect vertical with centrifugal force Fc, and the F that makes a concerted effort of centrifugal force Fc and gas directed force F g acts on the center O of pin 05
2On.
Here, the representation of centrifugal force Fc (1) is as follows:
Fc＝ (w)/(g) rω
2（1）
Wherein, W is the weight of rotary vortex body,
γ is the turning radius of rotary vortex body planetary motion,
ω is the angular velocity of rotation of rotary vortex body,
G is a gravity accleration.
The representation (2) of making a concerted effort is as follows:
The representation (3) of the direction of F and the angle theta between the eccentric direction is as follows with joint efforts:
θ＝tan
-1{Fg/Fc} （3）
When the F that makes a concerted effort acts on the oscillation bearing 03 by pin 05, oscillation bearing 03 vertically moves the effect lower edge sliding eye 02 of the F ' of component longitudinally of the lower edge sliding eye 02 of making a concerted effort, so that the radius r of planetary motion increases, and the heliconid 04b of rotary vortex body 04 is because contact pressure F " effect contact with the heliconid 06b of static volute body 06.
In addition, the representation (4) of the component F ' of F is as follows down with joint efforts:
F′＝FCos（α+θ） （4）
Contact pressure F " representation (5) as follows:
F″＝F′Cosα＝FCos（α+θ）·Cosα （5）
In above-mentioned existing vortex-type compressor, when the angular velocity of rotation ω of rotary vortex body 04 increased, the centrifugal force Fc that acts on the rotary vortex body 04 also increased, and this point can be found out from representation (1) significantly.Then, along with the increase of centrifugal force Fc, the θ angle will diminish, and this point can be found out from representation (3) significantly.Thereby " increase, this can find out from representation (4) and (5) significantly for component F ' and contact pressure F.
Because contact pressure F " with angular velocity of rotation ω square speed increase " excessive problem, thereby increased wearing and tearing and the noise of heliconid 04b and 06b that just there is a contact pressure F when running shaft 01 high speed rotating in this.
An object of the present invention is to provide a kind of scroll-type fluid machinery that addresses the above problem.
Another object of the present invention provides has a kind ofly made further improved scroll-type fluid machinery to above-mentioned fluid machinery.
In order to achieve the above object, main points of the present invention are as described in following (1) and (2) bar.
(1) a kind of scroll-type fluid machinery, be furnished with heliconid respectively on the end plate of its static volute body and rotary vortex body and be meshing with each other, one drive sleeve is installed in rotation on the sleeve that core stretches out from the outer surface of rotary vortex body end plate, a drive pin that stretches out from running shaft is contained in out the sliding eye in drive spool slidably, it is characterized in that: a balancer weight gauge block is arranged on drive sleeve, and this weight block produces one and act on the opposite centrifugal force of centrifugal force direction on the rotary vortex body when rotary vortex body is done planetary motion.
In by said structure provided by the invention, equilibrium block produces one and act on the opposite centrifugal force of centrifugal force direction on the rotary vortex body when rotary vortex body is done planetary motion.Therefore, can prevent that the contact pressure between the heliconid of the heliconid of rotary vortex body and static volute body from exceeding ability to bear when the running shaft high speed rotating.
(2) a kind of scroll-type fluid machinery, wherein static volute body and rotary vortex body are meshing with each other by the heliconid that is arranged on its end plate, one drive sleeve is installed in rotation on the sleeve that core stretches out from the outer surface of rotary vortex body end plate, a drive pin that stretches out from the running shaft axle center is contained in out the sliding eye in drive sleeve slidably, it is characterized in that on drive sleeve, having the uneven and balancer weight gauge block that is provided with of power that causes do planetary motion for the balance rotating volute body, the axial position of the center of gravity of balancer weight gauge block haply with the axial centre position consistency of drive sleeve.
In by said structure provided by the invention, effect by the balancer weight gauge block, can prevent that the contact pressure between the heliconid on rotary vortex body and the static volute body is excessive, and the moment that drive sleeve is verted that produces owing to the centrifugal force that acts on the equilibrium block has disappeared, thereby has suppressed verting of drive sleeve.
Fig. 1 and Fig. 2 are first embodiment of the present invention, and wherein Fig. 1 is the sectional arrangement drawing of major component, and Fig. 2 is along the drawing in side sectional elevation of II-II line among Fig. 1;
Fig. 3 and Fig. 4 are second embodiment of the present invention, and wherein Fig. 3 is the sectional arrangement drawing of major component, the front elevation after Fig. 4 comes for rotary vortex body is removed;
Fig. 5 and Fig. 6 are an example of vortex-type compressor in the prior art, and wherein Fig. 5 is the part sectional arrangement drawing, and Fig. 6 is along the drawing in side sectional elevation of VI-VI line among Fig. 5.
To carefully illustrate embodiment according to qualifications of the present invention with reference to the accompanying drawings below.
Fig. 1 and Fig. 2 have shown first embodiment of the present invention.
In Fig. 1 and Fig. 2, static volute body 1 comprises an end plate 1a and the heliconid 1b that is arranged on its internal surface.Rotary vortex body 2 comprises an end plate 2a and the heliconid 2b that is arranged on its internal surface.This two static volute body 1 and rotary vortex body 2 are in eccentric position mutually, throw of eccentric is the radius r of planetary motion, this two volute body is meshing with each other under the situation of 180 ° of transfers as shown in the figure, is the point symmetry compression chamber 3 at center with the spiral center thereby form a series of.One cylindrical sleeve 4 stretches out from the outer surface middle body of the end plate 2a of rotary vortex body 2, and a drive sleeve 5 is installed in rotation in the sleeve 4 by bearing 6.In drive sleeve 5, have a sliding eye 7, from the end face of running shaft 8 stretch out and with axis of rotation O
1The drive pin 9 that departs from r is installed in the sliding eye 7.The tangent plane of sliding eye 7 is a notched circle by forming to the straight-line cutting of a certain specific direction as shown in Figure 2.In addition, also to form a diameter littler and the breach circle of same profile arranged than above-mentioned breach circle for the tangent plane of eccentric drive pin 9.Thereby the straight section 9a of drive pin 9 contacts along straight line with the straight section 7a of sliding eye 7.Therefore, drive pin 9 can move and can move along all directions in the interstice coverage between the outer round surface of the internal circular surfaces of sliding eye 7 and pin 9 along straight line.
In addition, be fixed with a balancer weight gauge block 10 on drive sleeve 5, when rotary vortex body 2 was done planetary motion, balancer weight gauge block 10 produced one and act on the opposite centrifugal force of centrifugal force direction on the rotary vortex body 2.
When running shaft 8 rotations, driving force passes on the drive sleeve 5 by the straight section 7a on the sliding eye 7 from the straight section 9a on the drive pin 9, and further passes on the rotary vortex body 2 by bearing 6 and sleeve 4.Thereby rotary vortex body 2 is along the axle center O with running shaft 8
1Being the center of circle, is that the circumference of radius is done planetary motion with throw of eccentric r.Then, suck that gas in the compression chamber 3 is gradually reduced and move and volume arrives central chamber 11 when reducing to the spiral center, emit by air vent 12 from that again at compression chamber 3.
Now, because the rotation of rotary vortex body 2 comprises rotary vortex body 2, sleeve 4, bearing 6 and drive sleeve 5 produce one along running shaft 8 axle center O in interior unbalanced weight
1Center O with drive sleeve 5
2The centrifugal force of eccentric direction, but on balancer weight gauge block 10, also produce one and the opposite centrifugal force of above-mentioned centrifugal force direction simultaneously.
Thereby, might make heliconid 2b on the rotary vortex body 2 act on pressure on the heliconid 1b on the static volute body 1 be contact pressure constant and and the rotating speed of running shaft 8 irrelevant.
Owing to can produce one and act on the balancer weight gauge block of the opposite centrifugal force of centrifugal force direction on the rotary vortex body of planetary motion being furnished with one on the drive sleeve, thereby just can make heliconid and the contact pressure between the heliconid on the static volute body on the rotary vortex body unlikely excessive when running shaft runs up.
Therefore, spirochetal heel and toe wear just can be avoided.Thereby can prevent the reduction of scroll-type fluid machinery service behaviour and can prolong its life-span.
In the scroll-type fluid machinery in above-mentioned first embodiment shown in Figure 1, the position of the center of gravity G of balancer weight gauge block 10 is positioned at the axial lower position of drive sleeve 5.This layout of drive sleeve 5 and balancer weight gauge block 10 is just in order to slide it and eccentric drive pin 9 also can just be slidably mounted in the sliding eye 7 on the upper-end surface of running shaft 8.Therefore, in Fig. 1 because when rotary turbine 2 is done planetary motion, act on the effect of the centrifugal force F on balancer weight gauge block 10 centers of gravity, can vert in the direction of the clock by the integral body that balancer weight gauge block 10 and drive sleeve 5 are formed.Thereby, just produced the problem that swivel bearing 6 tilts to turn round, the running that the lower surface of drive sleeve 5 also can be done to tilt on the upper surface of running shaft 8.
Therefore, the present invention also provides a kind of scroll-type fluid machinery that can address the above problem.
Fig. 3 and Fig. 4 have shown second embodiment of the present invention.
As shown in Fig. 3 and Fig. 4, the thickness of the Vertical direction of the axial position of balancer weight gauge block 10 center of gravity G by increasing balancer weight gauge block 10 and almost flushing with the axial centre position of drive sleeve 5.
Other structure and Fig. 1 are with almost completely identical shown in Fig. 2, and the label of appropriate section is also identical.
When rotary vortex body 2 was done planetary motion, the drive sleeve 5 and the balancer weight gauge block 10 that are fixed together were also done above-described planetary motion, and effect has centrifugal force F on the center of gravity G of balancer weight gauge block 10.Because the axial centre position of the axial position of center of gravity G and drive sleeve 5 is consistent substantially, thus since the effect of centrifugal force F and on drive sleeve 5 tilt torque of generation obviously weaken or disappear.
In the present invention, as mentioned above, the center of gravity axial position of the balancer weight gauge block almost axial centre with drive sleeve is consistent.Thereby the tilt torque of the drive sleeve that produces based on acting on the centrifugal force on the balancer weight gauge block disappears or has weakened, thereby has suppressed verting of drive sleeve.
Consequently, might prevent to support the inclination running of swivel bearing of drive sleeve and the inclination running of end face on the running shaft end face of drive sleeve, thereby prevent the heel and toe wear and the fault that produce owing to above-mentioned inclination running, thereby can improve the reliability of scroll-type fluid machinery.
Claims (3)
1, a kind of scroll-type fluid machinery, wherein: static volute body and rotary vortex body are meshing with each other by the heliconid of arranging respectively on its end plate, one drive sleeve is installed in rotation on from the sleeve that stretch out the outer surface central position of rotary vortex body end plate, drive pin that stretches out from running shaft is slidably mounted in out in the sliding eye drive sleeve, it is characterized in that: a balancer weight gauge block that can produce and act on the opposite centrifugal force of centrifugal force direction on the rotary vortex body of planetary motion is being arranged on the drive sleeve.
2, scroll-type fluid machinery according to claim 1 is characterized in that: suitable substantially at centrifugal force that produces on the balancer weight gauge block and the centrifugal force that acts on the rotary vortex body of planetary motion.
3, a kind of scroll-type fluid machinery, wherein: static volute body and rotary vortex body are meshing with each other by the heliconid of arranging respectively on its end plate, one drive sleeve is installed in rotation on from the sleeve that the outer surface core of rotary vortex body end plate stretches out, drive pin that stretches out from running shaft is slidably mounted in out in the sliding eye drive sleeve, it is characterized in that: have one to be used for the unbalanced balancer weight gauge block of power that balance produces owing to the planetary motion of rotary vortex body on drive sleeve, the axial position of above-mentioned balancer weight gauge block center of gravity and the axial centre position of drive sleeve are consistent substantially.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP195701/90 | 1990-07-24 | ||
| JP19570190 | 1990-07-24 | ||
| JP89969/90 | 1990-08-28 | ||
| JP8996990U JPH0741843Y2 (en) | 1990-08-28 | 1990-08-28 | Scroll type fluid machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1058456A true CN1058456A (en) | 1992-02-05 |
| CN1020497C CN1020497C (en) | 1993-05-05 |
Family
ID=26431347
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN91103680A Expired - Fee Related CN1020497C (en) | 1990-07-24 | 1991-06-03 | Scroll type fluid machinery |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0468605B1 (en) |
| KR (1) | KR960000092B1 (en) |
| CN (1) | CN1020497C (en) |
| AU (1) | AU634059B2 (en) |
| CA (1) | CA2042203C (en) |
| DE (1) | DE69104927T2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1034831C (en) * | 1993-09-03 | 1997-05-07 | 三菱重工业株式会社 | Drive bushing for scroll fluid machine |
| CN104271959A (en) * | 2012-03-23 | 2015-01-07 | 比策尔制冷机械制造有限公司 | Crankshaft with aligned drive and counterweight locating features |
| CN111089055A (en) * | 2018-10-23 | 2020-05-01 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN116097001A (en) * | 2020-08-05 | 2023-05-09 | 株式会社电装 | Compressor and method for manufacturing compressor |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3236144B2 (en) * | 1993-09-14 | 2001-12-10 | 株式会社デンソー | Compressor |
| JP2682790B2 (en) * | 1993-12-02 | 1997-11-26 | 株式会社豊田自動織機製作所 | Scroll compressor |
| JPH07324689A (en) * | 1994-05-31 | 1995-12-12 | Mitsubishi Heavy Ind Ltd | Scroll type fluid compressor |
| US5496157A (en) * | 1994-12-21 | 1996-03-05 | Carrier Corporation | Reverse rotation prevention for scroll compressors |
| LU91082B1 (en) * | 2004-06-04 | 2005-12-05 | Wurth Paul Sa | Device to replace the main channel of a blast furnace. |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5819875B2 (en) * | 1980-03-18 | 1983-04-20 | サンデン株式会社 | Scroll compressor |
| JPS5979086A (en) * | 1982-10-27 | 1984-05-08 | Hitachi Ltd | Scroll hydraulic machine |
| JPS59120794A (en) * | 1982-12-27 | 1984-07-12 | Mitsubishi Electric Corp | Scroll compressor |
| JPS59142480U (en) * | 1983-03-15 | 1984-09-22 | サンデン株式会社 | Scroll type fluid device |
| US4954057A (en) * | 1988-10-18 | 1990-09-04 | Copeland Corporation | Scroll compressor with lubricated flat driving surface |
-
1991
- 1991-05-09 CA CA002042203A patent/CA2042203C/en not_active Expired - Fee Related
- 1991-05-10 AU AU76452/91A patent/AU634059B2/en not_active Ceased
- 1991-06-03 CN CN91103680A patent/CN1020497C/en not_active Expired - Fee Related
- 1991-06-11 DE DE69104927T patent/DE69104927T2/en not_active Expired - Fee Related
- 1991-06-11 EP EP91250153A patent/EP0468605B1/en not_active Expired - Lifetime
- 1991-07-24 KR KR1019910012679A patent/KR960000092B1/en not_active IP Right Cessation
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1034831C (en) * | 1993-09-03 | 1997-05-07 | 三菱重工业株式会社 | Drive bushing for scroll fluid machine |
| CN104271959A (en) * | 2012-03-23 | 2015-01-07 | 比策尔制冷机械制造有限公司 | Crankshaft with aligned drive and counterweight locating features |
| US9909586B2 (en) | 2012-03-23 | 2018-03-06 | Bitzer Kuehlmaschinenbau Gmbh | Crankshaft with aligned drive and counterweight locating features |
| CN111089055A (en) * | 2018-10-23 | 2020-05-01 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor having a plurality of scroll members |
| CN111089055B (en) * | 2018-10-23 | 2024-09-06 | 谷轮环境科技（苏州）有限公司 | Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a |
| CN116097001A (en) * | 2020-08-05 | 2023-05-09 | 株式会社电装 | Compressor and method for manufacturing compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| DE69104927D1 (en) | 1994-12-08 |
| CA2042203C (en) | 1996-02-13 |
| KR920002929A (en) | 1992-02-28 |
| CA2042203A1 (en) | 1992-01-25 |
| EP0468605A1 (en) | 1992-01-29 |
| AU634059B2 (en) | 1993-02-11 |
| AU7645291A (en) | 1992-01-30 |
| CN1020497C (en) | 1993-05-05 |
| EP0468605B1 (en) | 1994-11-02 |
| KR960000092B1 (en) | 1996-01-03 |
| DE69104927T2 (en) | 1995-03-09 |
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| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |