CN104895791A - Rolling rotor type compression mechanism and compressor comprising same - Google Patents
Rolling rotor type compression mechanism and compressor comprising same Download PDFInfo
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- CN104895791A CN104895791A CN201410081937.6A CN201410081937A CN104895791A CN 104895791 A CN104895791 A CN 104895791A CN 201410081937 A CN201410081937 A CN 201410081937A CN 104895791 A CN104895791 A CN 104895791A
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Abstract
A rolling rotor type compression mechanism (10) comprising: an eccentric shaft (20); a cylinder (40); a rotor (30), the rotor (30) being driven by the eccentric shaft (20) and making a rotary motion in the cylinder (40); and a slide (50), the slide (50) being pressed towards the rotor (30) to separate a working chamber in the cylinder (40), characterized in that, at the minimum radial distance between the rotor (30) and the cylinder (40), a seal (60) capable of abutting against the cylinder (40) is provided on the rotor (30). The invention also provides a compressor comprising the rolling rotor type compression mechanism. The rolling rotor type compression mechanism eliminates the radial clearance between the rotor and the cylinder wall, reduces the leakage between compression cavities to the minimum and improves the volumetric efficiency of the compression mechanism. And, relative rotation between the rotor and the eccentric shaft is avoided. The rolling rotor type compression mechanism has the advantages of small number of parts, simple structure, low cost and reliable operation.
Description
Technical field
The present invention relates to a kind of rolling rotor type compressor structure, more specifically, relate to a kind of rolling rotor type compressor structure eliminating radial clearance between rotor and cylinder.The invention still further relates to a kind of compressor comprising this rolling rotor type compressor structure.
Background technique
Statement in this section only provides and relates to background information of the present disclosure, and it may not form prior art.
Rolling rotor type compressor structure and utilize the equipment such as the compressor of this mechanism, pump due to advantages such as component are few, reliable, is used widely in a lot of field such as refrigeration, fluid conveying.
The present invention aims to provide a kind of high efficiency rolling rotor type compressor structure and comprises the compressor of this mechanism, wherein, eliminates the radial clearance between rotor and cylinder wall and prevents rotor and eccentric shaft from relatively rotating.
Summary of the invention
An object of the present invention is to provide a kind of high efficiency rolling rotor type compressor structure, in the whole working procedure of this mechanism, eliminates the radial clearance between rotor and cylinder wall.
Another object of the present invention is to provide a kind of high efficiency rolling rotor type compressor structure, wherein, avoid the relative movement between rotor and eccentric shaft.
According to an aspect of the present invention, provide a kind of rolling rotor type compressor structure and achieve above object, this rolling rotor type compressor structure comprises: eccentric shaft; Cylinder; Rotor, described rotor is driven by described eccentric shaft, in described cylinder, do rotation motion; And slide plate, described slide plate is compressed by towards described rotor, and to be separated out active chamber in described cylinder, wherein, the minimum place of the radial distance between described rotor and described cylinder, described rotor is provided with can against the Sealing of described cylinder.
By the radial distance between rotor and cylinder, minimum place arranges Sealing, simply, reliably realizes sealing in the whole working procedure of compressing mechanism.
According to a further aspect in the invention, a kind of compressor comprising this rolling rotor type compressor structure is provided.
By above aspect of the present invention, eliminate the radial clearance between rotor and cylinder wall, the leakage between compression chamber is down to minimum, improve the volumetric efficiency of compressing mechanism.Further, relatively rotating between rotor and eccentric shaft is avoided.Few according to the number of spare parts of rolling rotor type compressor structure of the present invention, structure is simple, and cost is low and reliable.
Accompanying drawing explanation
Only by way of example embodiments of the present invention are described hereinafter with reference to accompanying drawing, in the accompanying drawings:
Fig. 1 shows the working principle of conventional rolling rotor type compressor structure.
Fig. 2 shows radial force that rotor is subject in the position near cylinder and the tangential force change curve with angle of eccentricity.
Fig. 3 schematically shows the radial clearance between rotor and cylinder.
Fig. 4 schematically shows the structure of the rolling rotor type compressor structure according to one embodiment of the present invention.
Fig. 5 schematically shows Sealing and enlarged view around thereof.
Fig. 6, Fig. 7, Fig. 8 and Fig. 9 schematically show a work cycle according to rolling rotor type compressor structure of the present invention in order.
Figure 10 shows according to the contact force of the Sealing of the present invention situation of change with angle of eccentricity.
Figure 11 and Figure 12 shows the other mode of execution according to Sealing of the present invention.
Figure 13, Figure 14 and Figure 15 schematically show the some mode of executions according to groove of the present invention.
Embodiment
Fig. 1 shows the working principle of conventional rolling rotor type compressor structure.Rolling rotor type compressor structure is designated as 100 generally, and it comprises live axle 102, rotor 104, cylinder 106, slide plate 108, spring 110 and air inlet system 112 and venting gas appliance 114 etc.Wherein, slide plate 108 is resisted against all the time on rotor 104 under the effect of spring 110.Eccentric cam 103 on live axle 102 and rotor 104 frictional fit, when live axle 102 is rotated about axis under the drive of motor equal power device, the inwall that eccentric cam 103 rotor driven 104 is close to cylinder 106 revolves round the sun, thus between rotor 104 and cylinder 106, form two active chambers, the volume of these two active chambers increases along with the change of angle of rotor or reduces, and completes the process of air-breathing, compression and exhaust.
Particularly, Fig. 1 shows the several positions in a work cycle of this compressing mechanism, and wherein, rotor turns round in the cylinder in the counterclockwise direction.At I place, position, the active chamber (calling in the following text " air aspiration cavity A ") on the left of slide plate starts air-breathing, and the active chamber (calling in the following text " compression chamber B ") on the right side of slide plate starts pressurized gas; At II place, position, air aspiration cavity A continues air-breathing, and compression chamber B continues compression; At III place, position, air aspiration cavity A continues air-breathing, and when reaching certain pressure in compression chamber B, exhaust valve is opened, and compression chamber B starts exhaust; At IV place, position, air aspiration cavity A continues air-breathing, and compression chamber B is vented end; At V place, position, air aspiration cavity A air inlet terminates, and compression chamber B becomes and is communicated with air aspiration cavity A, and enters next circulation.
Fig. 2 shows radial force that rotor is subject in the position near cylinder and the tangential force change curve with live axle corner, the upper right corner of figure symbolically shows the relative position of live axle and rotor, and (great circle represents rotor, roundlet represents live axle), thus the rotor-position of live axle corner represented by the point of 0 degree is shown.As can be seen from the figure, when rotor is in diverse location, the symbol of radial force there will be change, when radial force is timing, represents that rotor can near cylinder wall, thus make radial clearance therebetween reduce; When radial force is for time negative, represent that rotor can away from cylinder wall, thus make radial clearance therebetween increase.Due to the above-mentioned motion of rotor, the radial clearance of compressor with rolling rotor structure can not be done too little, otherwise the interference of rotor and cylinder wall may occur in some region, causes friction and clashes into.Fig. 3 schematically shows the radial clearance D between rotor and cylinder.
Owing to there is this inevitable radial clearance, make, between the compression chamber of compressor with rolling rotor structure (the right chamber in Fig. 1) and air aspiration cavity (the left chamber in Fig. 1), leakage loss occurs, volumetric efficiency is lower.
On the other hand, Fig. 2 also show the sizable tangential force suffered by rotor.Due in the rolling rotor type compressor structure of routine, the mode only adopting friction (interference) to coordinate between rotor with live axle is assembled together, in some cases, this tangential force can cause relatively rotating continually between rotor and live axle, namely rotor except revolving round the sun under the drive of live axle, also can carry out rotation.Which results in the friction between part, and also reduce the efficiency of compressing mechanism, harmful effect is produced for Energy harvesting.
In order to more clearly represent principle of the present invention, schematically show only according to the eccentric shaft 20 in the rolling rotor type compressor structure 10 of a preferred embodiment of the present invention, rotor 30, cylinder 40 and slide plate 50 in Fig. 4, and eliminating spring, air inlet system, venting gas appliance and other parts, these parts are well known by persons skilled in the art.
Improvements according to rolling rotor type compressor structure 10 of the present invention are, except the slide plate that common rolling piston compressor structure has, the position that radial clearance between rotor 30 and cylinder 40 is minimum, rotor 30 is provided with can against the Sealing 60 of cylinder 40.
Specifically, in rotor 30, nearest apart from cylinder wall 42 in rotation process position, the outer surface of rotor 30 is provided with groove 32, and the axial length of groove 32 can be substantially equal to the axial length of rotor 30.Sealing 60 is embedded in groove 32, thus the surface 62 of Sealing 60 is contacted with the inwall 42 of cylinder 40.
Sealing 60 such as can be made up of resin materials such as Teflons, also can be made up of metallic material such as copper, iron, aluminium, as long as this material can tolerate the working environment of this rolling rotor type compressor structure inside, and provide the intensity needed for sealing.
Fig. 5 shows the details of groove 32 and Sealing 60 large, and shows the stressed of Sealing 60.It should be noted that the parts in Fig. 5 are not drawn in proportion.As shown in Figure 5, the form of Sealing 60 in slide block, in cross section perpendicular to axial direction, thickness in the circumferential direction of Sealing 60 is less than the thickness of groove 32, the width in the radial direction of groove 60 is less than the width sum of groove 32 and radial clearance, thus both direction between Sealing 60 and groove 32 all has gap, be incorporated into the back side 64 place back to cylinder 40 of Sealing 60 to allow the pressure of compression chamber by the side of Sealing 60.In addition, the size of Sealing 60 should be guaranteed in the whole work cycle of compressing mechanism, and Sealing 60 can both remain in groove 32 and can not come off.
Sealing 60 is compressed the power that cavity pressure Pc and air aspiration cavity compression Ps applies, compression chamber pressure P c is greater than air aspiration cavity pressure P s, in structure as above, both pressure difference Δ P(Δ P=Pc-Ps) cause by Sealing 60 down and extrude towards cylinder wall 42.
Contact force F between Sealing 60 to cylinder wall 42 is directly proportional to the lifting surface area S of pressure difference Δ P and Sealing 60.
Lifting surface area S=L × the W of Sealing 60, wherein, L is the length (not shown) on the axial direction (direction vertical with paper in Fig. 5) of Sealing 60, and W is the thickness in the circumferential direction of slide block.
Due in the almost whole working procedure of rolling type rotor compression mechanism 10, compression chamber pressure P c is greater than air aspiration cavity pressure P s, therefore contact force F total energy keep on the occasion of.By contact force F is remained on the occasion of, in whole working procedure, prevent Sealing 60 to depart from cylinder wall 42.Thus the radial clearance eliminated between rotor 30 and cylinder 40, achieve the sealing between compression chamber and air aspiration cavity.
On the other hand, because the stressed F of Sealing 60 is relevant with the pressure difference of slide block both sides, when pressure difference is less, stressed F is less, and when pressure difference is larger, stressed F is comparatively large, therefore, it is possible to automatically regulate contact force, brings extra resistance can not to the rotation of rotor 30.
Although the surface 62 that there is shown Sealing 60 has the shape with cylinder wall 42 complementation, thus improves sealing effect as much as possible.But should be appreciated that Sealing 60 can have much different shapes, as being the curved surface with cylinder wall 42 with different curvature, or the shape in other projection.
In order to make Sealing 60 always be in the minimum position of radial distance between rotor 30 and cylinder wall 40, preferably, be connected being fixed by fixing part 70 between rotor 30 with eccentric shaft 20.This firmness be fixedly connected with is preferably higher than common frictional fit.As shown in the figure, fixing part 70 can be dismountable, as keyway fixing part, pin-and-hole fixing part etc., also can be any non-removable fixing part known to those skilled in the art, as being welded and fixed portion.
The position of this fixing part 70 can relative in diametric(al) with the position of Sealing 60 (as shown in the figure), also can be positioned at any suitable position on rotor 30 and/or eccentric shaft 20, be connected as long as rotor 30 can be firmly fixed with eccentric shaft 20.Thus, achieve rotor 30 and the synchronous rotary of eccentric shaft 20, improve the rotating speed of rotor 30, and be therefore conducive to forming oil film between Sealing 60 and adjacent part, improve sealing further.
Fig. 6 to Fig. 9 shows a work cycle according to rolling rotor type compressor structure of the present invention in order.As shown in Figures 6 to 9, under any circumstance, Sealing 60 always remains in the minimum place of radial distance between rotor 30 and cylinder wall 40, thus achieves good sealing.
Figure 10 shows according to the contact force of the Sealing of the present invention situation of change with angle of eccentricity.With similar in Fig. 2, the top of figure symbolically shows eccentric shaft and rotor, and (great circle represents rotor, roundlet represents eccentric shaft), thus the rotor-position of angle of eccentricity represented by the point of 0 degree (can see, the angle of eccentricity starting point in Figure 10 is different from Fig. 2) is shown.Can see by Figure 10, except being (now compression chamber and suction chamber in communication) near 0 degree at angle of eccentricity, contact force is roughly outside 0, in the whole working procedure of rolling rotor, all achieve total on the occasion of gratifying contact force.
Foregoing merely illustrate a kind of preferred implementation of Sealing 60, it adopts mobilizable slide block, utilizes the pressure difference between compression chamber and air aspiration cavity to realize sealing.
Figure 11 shows another mode of execution of Sealing 60, wherein, arranges elastic component radially, as spring etc. between the diapire and the back side of Sealing 60 of groove 32.Sealing 60 can extrude towards cylinder wall 42 by further, guarantees to eliminate the radial clearance between rotor 30 and cylinder wall 42.
Figure 12 shows another mode of execution of Sealing 60, and wherein, Sealing 60 is the elastomer seals being resisted against groove 32 and cylinder 40 in radial directions.In the whole working procedure of compressing mechanism 10, utilize the elasticity of Sealing 60 self, the back side 64 of Sealing 60 is all the time against the bottom of groove 32, and surface of contact 62 is against cylinder wall 42.
Although in a preferred embodiment of the invention, Sealing 60 is all arranged in groove 32, should be appreciated that in appropriate circumstances, also Sealing 60 can be set directly on rotor 30 by the mode such as bonding and not arranged groove.
As shown in Figure 6, along with the rotation of rotor 30, when Sealing 60 is near slide plate 50, slide plate 50 likely stretches out downwards and enters in the groove 32 of rotor 30 under the effect of spring (as spring 108, see Fig. 1), thus causes stuck or part to be damaged.In order to avoid this situation, preferably, can be designed by least one in the parameters such as the quantity to groove 32, shape and size, enter to stop slide plate 50.Such as, can by rotor 30, the one or both sides providing walls of groove 32 realizes.Figure 13 to Figure 15 shows several mode of executions of groove 32.In fig. 13, the axial length of groove 32 is less than the axial length of rotor 30, and groove 32 is presented axially in the centre of rotor 30, that is, the both sides on the axial direction of groove 32 have wall portion.In fig. 14, be provided with two grooves 32 separated by wall portion, in two grooves 32, have a Sealing respectively.In fig .15, groove 32 in the axial direction near one end of rotor 30, that is, is provided with wall portion in the side of groove 32.Should be appreciated that in the mode of execution of Figure 13 to Figure 15, quantity, the size and dimension of Sealing match with groove 32 respectively.According to these mode of executions, those skilled in the art can imagine anti-slip limiting plate 50 and enter multiple configuration in groove 32, such as, can change the quantity of groove 32 further, or the profile design of groove 32 is become and the unmatched shape of slide plate 50, thus avoids slide plate 50 to enter.
According to an aspect of the present invention, rotor is provided with groove, Sealing is contained in described groove.
Preferably, eccentric shaft and rotor are can not mode be fixed together in relative rotation.Fixing part between eccentric shaft and rotor is dismountable or non-removable.Fixing part comprise following in one or more: keyway fixing part, pin-and-hole fixing part, be welded and fixed portion.
By by eccentric shaft and rotor can not mode be fixed together in relative rotation, all the time Sealing can be remained on the minimum place of radial distance between rotor and cylinder, and the friction avoided because rotor brings relative to eccentric shaft turns and efficiency reduce.In addition, contribute to forming oil film between Sealing and adjacent part, improve sealing further.
Preferably, groove is with in circumferential direction and in the radial direction and have the mode in gap to hold Sealing between Sealing.Sealing can move based on the pressure difference between active chamber.
By designing mobilizable Sealing by this way, the pressure difference of Sealing both sides can be utilized to be pressed against on cylinder wall by Sealing.And because the sealing force of Sealing is relevant with pressure difference, therefore, it is possible to regulate the contact force of Sealing and cylinder adaptively, bring excessive resistance can not to the rotation of rotor.
Alternatively, between the diapire and the back side of Sealing of groove, spring is provided with.
By arranging spring, the stability of sealing can be improved further.
Alternatively, Sealing is the elastomer seal being resisted against groove and cylinder in radial directions.
By elastomer seal, sealing reliably, stably can be realized in another way.
Preferably, Sealing has with the surface of cylinder contact the shape matched with the surface of cylinder.
With the surface of contact of cylinder, there is the shape matched with cylinder surface by what make Sealing, the area of sealing surfaces can be increased, thus improve sealing effect.
Preferably, Sealing is contained in epitrochanterian groove, and at least one in the quantity of groove, size and dimension is designed to stop entering of slide plate.The axial length of groove is less than the axial length of rotor.Alternatively, the wall portion stopping that slide plate enters is provided with in the one or both sides of groove.Alternatively, be provided with two grooves, two grooves are by stopping that the wall portion that slide plate enters is spaced apart.
Designed by the quantity to groove, size and dimension, the stuck or damage parts caused because slide plate enters groove can be avoided.
Additionally provide a kind of compressor comprising this rolling rotor type compressor structure.
Below be only illustrative embodiments of the present invention, by reference to the accompanying drawings and after specification, those skilled in the art easily can make multiple transformation to the present invention, and all these transformations all fall in the scope of claims.
Claims (15)
1. a rolling rotor type compressor structure (10), comprising:
Eccentric shaft (20);
Cylinder (40);
Rotor (30), described rotor (30) is driven by described eccentric shaft (20), in described cylinder (40), do rotation motion; With
Slide plate (50), described slide plate (50) is compressed by towards described rotor (30), to be separated out active chamber in described cylinder (40),
It is characterized in that, the minimum place of radial distance between described rotor (30) and described cylinder (40), described rotor (30) is provided with can against the Sealing of described cylinder (40) (60).
2. rolling rotor type compressor structure (10) as claimed in claim 1, it is characterized in that, described rotor (30) is provided with groove (32), and described Sealing (60) is contained in described groove (32).
3. rolling rotor type compressor structure (10) as claimed in claim 2, is characterized in that, described eccentric shaft (20) and described rotor (30) are can not mode be fixed together in relative rotation.
4. rolling rotor type compressor structure (10) as claimed in claim 3, it is characterized in that, the fixing part (70) between described eccentric shaft (20) and described rotor (30) is dismountable or non-removable.
5. rolling rotor type compressor structure (10) as claimed in claim 4, is characterized in that, described fixing part (70) comprise following in one or more: keyway fixing part, pin-and-hole fixing part, be welded and fixed portion.
6. rolling rotor type compressor structure (10) as claimed in claim 2, is characterized in that, described groove (32) is with in circumferential direction and/or in the radial direction and have the mode in gap to hold described Sealing (60) between described Sealing (60).
7. rolling rotor type compressor structure (10) as claimed in claim 6, it is characterized in that, described Sealing (60) can move based on the pressure difference between active chamber.
8. rolling rotor type compressor structure (10) as claimed in claim 6, is characterized in that, between the diapire and the back side of described Sealing (60) of described groove (32), be provided with spring.
9. rolling rotor type compressor structure (10) as claimed in claim 2, it is characterized in that, described Sealing (60) is the elastomer seal being resisted against described groove (32) and described cylinder (40) in radial directions.
10. rolling rotor type compressor structure (10) as claimed in any one of claims 1-9 wherein, it is characterized in that, the surface contacted with described cylinder (40) of described Sealing (60) has the shape matched with the surface of described cylinder (40).
11. rolling rotor type compressor structures (10) as claimed in any one of claims 1-9 wherein, is characterized in that, at least one in the quantity of described groove (32), size and dimension is designed to stop entering of described slide plate (50).
12. rolling rotor type compressor structures (10) as claimed in claim 11, is characterized in that, the axial length of described groove (32) is less than the axial length of described rotor (30).
13. rolling rotor type compressor structures (10) as claimed in claim 11, is characterized in that, are provided with the wall portion stopping that described slide plate (50) enters in the one or both sides of described groove (32).
14. rolling rotor type compressor structures (10) as claimed in claim 11, is characterized in that, are provided with two grooves (32), and described two grooves (32) are by stopping that the wall portion that described slide plate (50) enters is spaced apart.
15. 1 kinds of compressors comprising the rolling rotor type compressor structure according to any one of claim 1 to 14.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410081937.6A CN104895791A (en) | 2014-03-06 | 2014-03-06 | Rolling rotor type compression mechanism and compressor comprising same |
| PCT/CN2014/094950 WO2015131633A1 (en) | 2014-03-06 | 2014-12-25 | Rolling rotor type compression mechanism and compressor comprising mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410081937.6A CN104895791A (en) | 2014-03-06 | 2014-03-06 | Rolling rotor type compression mechanism and compressor comprising same |
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| Publication Number | Publication Date |
|---|---|
| CN104895791A true CN104895791A (en) | 2015-09-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410081937.6A Pending CN104895791A (en) | 2014-03-06 | 2014-03-06 | Rolling rotor type compression mechanism and compressor comprising same |
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| Country | Link |
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| CN (1) | CN104895791A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110296074A (en) * | 2019-07-22 | 2019-10-01 | 杨啟波 | Low friction occlusion pump |
| CN113446222A (en) * | 2021-08-09 | 2021-09-28 | 张海霞 | Air conditioner compressor |
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| CH223597A (en) * | 1938-07-30 | 1942-09-30 | Sulzer Ag | Rotary compressor with eccentric rotating piston. |
| US4345886A (en) * | 1978-03-10 | 1982-08-24 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Rotary compressor with vanes in the housing and suction through the rotor |
| JPH0821388A (en) * | 1994-07-06 | 1996-01-23 | Shuichi Kitamura | Oilless type rotary pump |
| JP2005307764A (en) * | 2004-04-19 | 2005-11-04 | Mitsubishi Electric Corp | Rotary compressor |
| JP2010116783A (en) * | 2008-11-11 | 2010-05-27 | Daikin Ind Ltd | Fluid machine |
| CN203756529U (en) * | 2014-03-06 | 2014-08-06 | 艾默生环境优化技术(苏州)有限公司 | Rolling rotor type compression mechanism and compressor comprising same |
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2014
- 2014-03-06 CN CN201410081937.6A patent/CN104895791A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH223597A (en) * | 1938-07-30 | 1942-09-30 | Sulzer Ag | Rotary compressor with eccentric rotating piston. |
| US4345886A (en) * | 1978-03-10 | 1982-08-24 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Rotary compressor with vanes in the housing and suction through the rotor |
| JPH0821388A (en) * | 1994-07-06 | 1996-01-23 | Shuichi Kitamura | Oilless type rotary pump |
| JP2005307764A (en) * | 2004-04-19 | 2005-11-04 | Mitsubishi Electric Corp | Rotary compressor |
| JP2010116783A (en) * | 2008-11-11 | 2010-05-27 | Daikin Ind Ltd | Fluid machine |
| CN203756529U (en) * | 2014-03-06 | 2014-08-06 | 艾默生环境优化技术(苏州)有限公司 | Rolling rotor type compression mechanism and compressor comprising same |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110296074A (en) * | 2019-07-22 | 2019-10-01 | 杨啟波 | Low friction occlusion pump |
| CN113446222A (en) * | 2021-08-09 | 2021-09-28 | 张海霞 | Air conditioner compressor |
| CN113446222B (en) * | 2021-08-09 | 2023-08-04 | 深圳市中祥润实业有限公司 | Air conditioner compressor |
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Application publication date: 20150909 |