CN110778495A - Non-contact high-energy cycloidal rotor with high volume utilization rate and light weight for pump - Google Patents
Non-contact high-energy cycloidal rotor with high volume utilization rate and light weight for pump Download PDFInfo
- Publication number
- CN110778495A CN110778495A CN201911199018.8A CN201911199018A CN110778495A CN 110778495 A CN110778495 A CN 110778495A CN 201911199018 A CN201911199018 A CN 201911199018A CN 110778495 A CN110778495 A CN 110778495A
- Authority
- CN
- China
- Prior art keywords
- segment
- pitch circle
- cycloid
- rotor
- energy
- 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.)
- Withdrawn
Links
- 230000007704 transition Effects 0.000 claims abstract description 26
- 230000009286 beneficial effect Effects 0.000 abstract description 3
- 230000000694 effects Effects 0.000 description 3
- 239000013585 weight reducing agent Substances 0.000 description 2
- 150000001875 compounds Chemical class 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
Images
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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/126—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
-
- 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
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/126—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
-
- 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
- F04C2240/20—Rotors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
A non-contact high-energy cycloidal rotor with high volume utilization rate and light weight for pump is characterized in that the half-impeller profile of the high-energy cycloidal rotor consists of six profile sections, namely a top concentric circular arc section outside a pitch circle, an outer transition circular arc section outside the pitch circle, an outer swing line section outside the pitch circle, an inner swing line section inside the pitch circle, an inner transition circular arc section inside the pitch circle and a valley circular arc section inside the pitch circle, which are connected end to end. The invention has the following advantages: 1) the rotor structure belongs to a full convex-concave conjugate mode, and conjugate leakage between rotors can be effectively reduced; 2) the two cycloid segments are located at the point 4 on the pitch circle due to the inflection point, then the normal angle is started
αThe shape coefficient of the rotor can be obviously improved without upper limit; 3) the top concentric angle has little influence on the shape coefficient and the volume utilization coefficient, and can be beneficial to improving the relative large value of radial leakage; 4) higher volume due to large top concentric angle, high form factor, large volume utilization factor and radial, conjugate, low leakageEfficiency.
Description
Technical Field
The invention relates to a cycloidal rotor for a pump, in particular to a high-performance cycloidal rotor with 2 vanes, 3 vanes and 4 vanes, which mainly has high volume utilization rate and is called as a high-energy cycloidal rotor for short.
Background
The rotor pump is divided into a contact type and a non-contact type, and the latter is widely applied to a roots pump. The involute, arc and cycloid rotors are the most commonly referred to, but the involute and arc rotors belong to a full convex-convex and partial convex-concave mode, and the comprehensive curvature radius between non-contact contours of the rotors is relatively small, so that the suppression of internal leakage between the rotors is not facilitated. While cycloids are often used in internal-meshing pumps, a single cycloidal convex rotor, although belonging to a full convex-concave mode, is extremely disadvantageous in terms of weight reduction of the pump, as shown in fig. 1, with 1+1/2=1.5 for 2 lobes, 1+1/3=1.33 for 3 lobes, and 1+1/4=1.25 for 4 lobes.
Pump volumetric efficiency = volumetric efficiency coefficient of rotor
λX (1-internal leakage rate). Among them, the existing studies show that
λ≈1－1/
ε 2I.e. the form factor of the rotor defined by "maximum radius at the top/radius at the pitch circle
εThe larger the volume utilization factor
λHigher; the internal leakage rate mainly comprises the radial, axial and conjugate internal leakage rate of three pumps, and the prior research shows that the shape factor
εThe larger the internal leak rate.
The lightweight performance of the pump mainly depends on the volume utilization rate of the pump, particularly the volume utilization coefficient of the rotor
λ，
λThe larger the weight reduction effect, the better. The prior research shows that
λ≈1－1/
ε 2I.e. the form factor of the rotor defined by "maximum radius at the top/radius at the pitch circle
εThe larger the volume utilization factor
λThe higher.
Therefore, on the premise of meeting the requirements of large form factor and low internal leakage rate required by high volume utilization rate and continuing the advantage characteristics of a single cycloid rotor, a high-energy cycloid rotor with higher volume utilization rate and good lightweight performance is provided, as shown in fig. 2.
Disclosure of Invention
The invention provides the profile structure of the 2-blade, 3-blade and 4-blade high-energy cycloid rotors, so that higher volume utilization rate and better lightweight performance of the non-contact type rotor for the pump are realized.
The technical solution of the invention is as follows:
the utility model provides a high, the light-weighted non-contact high energy cycloid rotor for pump of volume utilization, its characterized in that: the profile size of the high-energy cycloid rotor body and the conjugate body is completely the same, and the high-energy cycloid rotor is generally called, the half-impeller profile of the high-energy cycloid rotor is composed of six profile sections of a top concentric arc section outside a pitch circle, an outer transition arc section outside the pitch circle, an outer cycloid section outside the pitch circle, an inner cycloid section inside the pitch circle, an inner transition arc section inside the pitch circle and a valley arc section inside the pitch circle, the starting point normal line section of the outer cycloid section outside the pitch circle passes through the intersection point 8 of the top axis and the pitch circle of the rotor, the terminal point 4 is positioned on the pitch circle, and the steepness degree of the outer cycloid section outside the pitch circle is formed by the included angle between the starting point normal line section and the top axis
αUnder the unique control, the center of the top concentric arc segment is the center of the rotor
oRadius is defined by the angle
αTop concentric fillet
σControlled by the control that the outer transition arc section passes through 2 and 3 and the circle center is 2
oAt the intersection with the origin normal line segment 38, the inner cycloid segment is the conjugate contour of the outer cycloid segment on the conjugate body, and the inner transition arc segment and the valley arc segment are the top concentric arc segment and the outer transition arc segment on the conjugate body.
The high-energy cycloid rotors are 2-blade, 3-blade and 4-blade high-energy cycloid rotors.
The size of the valley circular arc segment is the same as that of the top concentric circular arc segment.
The size of the inner transition circular arc section is the same as that of the outer transition circular arc section.
The steepness of the outer swing line segment is determined by the initial included angle
αControl, the degree of steepness determines the length of the starting point normal line segment and the starting included angle
αTop concentric fillet
σTogether determine the form factor of the rotor,
αthe larger the shape factor;
σthe smaller the form factor, the larger, but the less effective the radial seal.
The above-mentioned
αThe upper limit value of (2) is mainly limited by the strength condition of the rotor valley, and the contour inflection points of the epicycloidal segment and the hypocycloidal segment are all points 4 on the pitch circle, namely
αAny value of the angle does not cause geometric interference such as 'corner' on the outer swing line segment and the inner swing line segment, particularly the inner swing line segment, which is the same as the common gradual angleOpen-line, circular arc rotors are quite different.
The invention has the beneficial effects that: the non-contact high-energy cycloid rotor for the pump, which is high in volume utilization rate and light in weight, has the following advantages:
1) the rotor belongs to a full convex-concave conjugate mode, can effectively reduce conjugate leakage between rotors, and is completely different from full convex-convex involute and partial convex-concave arc rotors.
2) The two cycloid segments are located at the point 4 on the pitch circle due to the inflection point, then the normal angle is started
αThe form factor of the rotor can be increased significantly without an upper limit, which is distinct from other conventional rotors.
3) The top concentric angle has little effect on the form factor, the volume utilization factor, and can take advantage of relatively large values for radial leakage, as opposed to other conventional rotors.
4) Higher volumetric efficiency is achieved due to the large top concentric angle, high form factor, large volume utilization factor, and radial, conjugate, low leakage.
Drawings
Figure 1 is a schematic profile view of a 3-lobe single cycloid rotor.
Fig. 2 is a schematic profile view of a 3-lobe high energy gerotor.
Fig. 3 is a half-vane profile configuration diagram of a 3-vane high-energy gerotor.
Wherein: point 4, end point, point 8, intersection point, 12, top concentric arc segment, 23, outer transition arc segment, 34, outer swing segment, 38, starting point normal segment, 45, inner swing segment, 56, inner transition arc segment, 67, valley arc segment.
Detailed Description
The invention is further described with reference to the following figures and detailed description.
Example (2-lobe, 3-lobe, 4-lobe high-energy cycloid rotor)
The profile of the half impeller of the 2-blade, 3-blade and 4-blade high-energy cycloid rotor consists of six sections of profiles which are connected end to end together and are a top concentric circular arc section 12, an outer transition circular arc section 23, an outer cycloid section 34, an inner cycloid section 45, an inner transition circular arc section 56 and a valley circular arc section 67 on the outer side of a pitch circle, as shown in figure 2.
Wherein, the starting point normal line segment 38 of the outer swing line segment 34 outside the pitch circle passes through the intersection point 8 of the rotor top axis and the pitch circle, the terminal point 4 is positioned on the pitch circle, and the steepness of the outer swing line segment 34 outside the pitch circle is determined by the included angle between the starting point normal line segment 38 and the top axis
αThe center of the top concentric arc segment 12 is the center of the rotor under the unique control
oRadius is defined by the angle
αTop concentric fillet
σControlled by the control that the outer transition arc section 23 passes through the points 2 and 3 and the circle center is 2
oAt the intersection with 38, the inner swing line segment 45 is the conjugate contour of the outer swing line segment 34 on the conjugate, and the inner transition circular arc segment 56 and the valley circular arc segment 67 are the top concentric circular arc segment 12 and the outer transition circular arc segment 23 on the conjugate.
Firstly, the radius of the roller is obtained according to the cycloid forming principle that the roller rolls on the pitch circle
r o Is composed of
In the formula (I), the compound is shown in the specification,
Nthe number of rotor blades.
In FIG. 3, line segment 38 is shown
o2 at an intersection of
kPoint of contact
kAlso the center of the outer transition arc segment 23,
k8、
kohas a length of
l、
m. Then, in delta
okIn 8, from the geometric relationship
To obtain
Then, the form factor of the high-energy cycloid rotor
εIs/are as follows
Can find out
αUpper limit value
α p In the formula (I), wherein,
ε p to be strengthened by the rotor valleyThe maximum shape factor defined by the condition.
Secondly, according to the forming principle of epicycloid and hypocycloid, from the determined
αConstructing an outer cycloid section 34 and an inner cycloid section 45; top concentric fillet
σAnd form factor
εConstructing a top concentric arc segment 12 and a valley arc segment 67; constructing an outer transition circular arc section 23 according to the geometric relationship determined by the top concentric circular arc section 12 and the epicycloid section 34; the inner transition circular arc segment 56 is constructed by the geometric relationship defined by the valley circular arc segment 67 and the hypocycloid segment 45.
Finally, to
σWhen the angle is =3 degrees as an example,
α=15 °, 30 °, 45 °, 60 ° and
Nunder =2, 3, 4
ɛ(
α,
N) As shown in Table 1, it can be seen that
αThe larger the size of the tube is,
ɛthe larger, the higher the form factor than a single cycloid rotor or even other rotors. Corresponding volume utilization factor
λ(
α,
N) As shown in Table 2, it can be seen that
αThe larger the size of the tube is,
ɛthe larger the size of the tube is,
λthe larger the capacity utilization factor is, the higher the capacity utilization factor is than for a single cycloid rotor or even for other rotors.
TABLE 1 variation of shape factor with starting Normal Angle and leaf number: (
σ=3)
TABLE 2 variation of volume utilization factor with initial normal angle and leaf number: (
σ=3)
To be provided with
αIn the case of an example of =30 °,
σ=2 °, 4 °, 6 °, 8 °, 10 ° and
Nunder =2, 3, 4
ɛ(
σ,
N) As shown in Table 3, it can be seen that
σThe larger the size of the tube is,
ɛthe larger, but
σTo pair
ɛThe influence of (A) is very small and can be ignored. In this way it is possible to obtain,
σa relatively large value may be beneficial for improving radial leakage, as opposed to other rotors such as involute, circular arc rotors.
TABLE 3 variation of shape factor with center half angle and leaf number: (
α=30)
The non-contact high-energy cycloid rotor for the pump with high volume utilization rate and light weight has the advantages that:
1) the rotor belongs to a full convex-concave conjugate mode, can effectively reduce conjugate leakage between rotors, and is completely different from full convex-convex involute and partial convex-concave arc rotors.
2) The two cycloid segments are located at the point 4 on the pitch circle because of the inflection point, and the initial normal angle can significantly improve the shape factor of the rotor without an upper limit, which is quite different from other common rotors.
3) The top concentric angle has little effect on the form factor, the volume utilization factor, and can take advantage of relatively large values for radial leakage, as opposed to other conventional rotors.
4) Higher volumetric efficiency is achieved due to the large top concentric angle, high form factor, large volume utilization factor, and radial, conjugate, low leakage.
Claims (6)
1. The utility model provides a high, the light-weighted non-contact high energy cycloid rotor for pump of volume utilization, its characterized in that: the high-energy cycloid rotor body and the conjugate have the same contour size and are collectively called high-energy cycloid rotors, the half impeller contour of the high-energy cycloid rotor consists of six contour segments, namely a top concentric circular arc segment 12 on the outer side of a pitch circle, an outer transition circular arc segment 23 on the outer side of the pitch circle, an outer cycloid segment 34 on the outer side of the pitch circle, an inner cycloid segment 45 on the inner side of the pitch circle, an inner transition circular arc segment 56 on the inner side of the pitch circle and a valley circular arc segment 67 on the inner side of the pitch circle, a starting point normal line segment 38 of the outer cycloid segment 34 on the outer side of the pitch circle passes through a crossing point 8 of a top axis of the rotor and the pitch circle, a terminal point 4 is positioned on the pitch circle, and the steepness of the outer cycloid segment 34 on the outer side of
αThe center of the top concentric arc segment 12 is the center of the rotor under the unique control
oRadius is defined by the angle
αTop concentric fillet
σControlled by the external transition arc section 23 passing through 2 and 3 with the circle center being 2
oAt the intersection with the origin normal line segment 38, the hypocycloid segment 45 is conjugateThe conjugate contour of the outer cycloid segment 34 on the body, the inner transition arc segment 56 and the valley arc segment 67 are the top concentric arc segment 12 and the outer transition arc segment 23 on the conjugate body.
2. The non-contact high-energy cycloid rotor for a pump of claim 1 having high volumetric efficiency and light weight, wherein: the high-energy cycloid rotors are 2-blade, 3-blade and 4-blade high-energy cycloid rotors.
3. The non-contact high-energy cycloid rotor for a pump of claim 1 having high volumetric efficiency and light weight, wherein: the valley circular arc segment 67 has the same size as the top concentric circular arc segment 12.
4. The non-contact high-energy cycloid rotor for a pump of claim 1 having high volumetric efficiency and light weight, wherein: the inner transition arc segment 56 has the same dimensions as the outer transition arc segment 23.
5. The non-contact high-energy cycloid rotor for a pump of claim 1 having high volumetric efficiency and light weight, wherein: the steepness of the epicycloidal segment 34 is determined by the initial angle
αControl, the degree of steepness determines the length of the origin normal line segment 38, the origin angle
αTop concentric fillet
σTogether determine the form factor of the rotor,
αthe larger the shape factor;
σthe smaller the form factor, the larger, but the less effective the radial seal.
6. The non-contact high-energy cycloid rotor for a pump of claim 1 having high volumetric efficiency and light weight, wherein: the above-mentioned
αIs mainly limited by the strength condition of the rotor valley, because the contour inflection points of the epicycloidal segment 34 and the hypocycloidal segment 45 are all points 4 on the pitch circle, namely
αAny value of the magnetic field does not cause geometric interference such as 'corner points' on the sections of the outer swing line section 34 and the inner swing line section 45, particularly the inner swing line section 45, which is completely connected with common involute and circular arc rotorsDifferent.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911199018.8A CN110778495A (en) | 2019-11-29 | 2019-11-29 | Non-contact high-energy cycloidal rotor with high volume utilization rate and light weight for pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911199018.8A CN110778495A (en) | 2019-11-29 | 2019-11-29 | Non-contact high-energy cycloidal rotor with high volume utilization rate and light weight for pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110778495A true CN110778495A (en) | 2020-02-11 |
Family
ID=69393333
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911199018.8A Withdrawn CN110778495A (en) | 2019-11-29 | 2019-11-29 | Non-contact high-energy cycloidal rotor with high volume utilization rate and light weight for pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110778495A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113217377A (en) * | 2021-05-11 | 2021-08-06 | 宿迁学院 | Constant output flow double-rotor pair for pump and constant output flow calculation method |
| CN113931837A (en) * | 2021-10-12 | 2022-01-14 | 宿迁学院 | Easy-to-machine convex rotor with inner arc limit profile |
| CN115289004A (en) * | 2022-01-11 | 2022-11-04 | 宿迁学院 | Rapid reverse solving method for Roots rotor volume utilization coefficient |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN203189267U (en) * | 2013-04-17 | 2013-09-11 | 大连交通大学 | Conjugated internal-external cycloid involute-type rotor of roots vacuum pump |
| CN204827918U (en) * | 2015-07-31 | 2015-12-02 | 山东伯仲真空设备股份有限公司 | Three leaf lobe pump rotors of cycloid formula |
| CN205578260U (en) * | 2016-04-22 | 2016-09-14 | 山东伯仲真空设备股份有限公司 | Novel three leaf lobe pump rotor molded liness |
| US20180245590A1 (en) * | 2015-08-17 | 2018-08-30 | Eaton Intelligent Power Limited | Hybrid profile supercharger rotors |
| CN209212565U (en) * | 2018-11-20 | 2019-08-06 | 宿迁学院 | A kind of involute rotor pushed up with radial seal with width |
| CN211202285U (en) * | 2019-12-20 | 2020-08-07 | 宿迁学院 | Non-contact high-energy cycloid rotor |
-
2019
- 2019-11-29 CN CN201911199018.8A patent/CN110778495A/en not_active Withdrawn
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN203189267U (en) * | 2013-04-17 | 2013-09-11 | 大连交通大学 | Conjugated internal-external cycloid involute-type rotor of roots vacuum pump |
| CN204827918U (en) * | 2015-07-31 | 2015-12-02 | 山东伯仲真空设备股份有限公司 | Three leaf lobe pump rotors of cycloid formula |
| US20180245590A1 (en) * | 2015-08-17 | 2018-08-30 | Eaton Intelligent Power Limited | Hybrid profile supercharger rotors |
| CN205578260U (en) * | 2016-04-22 | 2016-09-14 | 山东伯仲真空设备股份有限公司 | Novel three leaf lobe pump rotor molded liness |
| CN209212565U (en) * | 2018-11-20 | 2019-08-06 | 宿迁学院 | A kind of involute rotor pushed up with radial seal with width |
| CN211202285U (en) * | 2019-12-20 | 2020-08-07 | 宿迁学院 | Non-contact high-energy cycloid rotor |
Non-Patent Citations (2)
| Title |
|---|
| 刘俊泉等: "石油化工应用技术", 中国石化出版社, pages: 261 - 267 * |
| 李玉龙等: "泵用转子型线的摆线构造方法研究", 真空科学与技术学报, vol. 38, no. 12, pages 1025 - 1028 * |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113217377A (en) * | 2021-05-11 | 2021-08-06 | 宿迁学院 | Constant output flow double-rotor pair for pump and constant output flow calculation method |
| CN113931837A (en) * | 2021-10-12 | 2022-01-14 | 宿迁学院 | Easy-to-machine convex rotor with inner arc limit profile |
| CN115289004A (en) * | 2022-01-11 | 2022-11-04 | 宿迁学院 | Rapid reverse solving method for Roots rotor volume utilization coefficient |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110778495A (en) | Non-contact high-energy cycloidal rotor with high volume utilization rate and light weight for pump | |
| CN109630409B (en) | Elliptical arc type roots pump rotor with high effective volume rate | |
| CN102352840B (en) | Screw rotor end face profile pair and construction method thereof | |
| CN108930650B (en) | Double-end claw type pump rotor and molded lines thereof | |
| CN104776027B (en) | Strict seal type dry screw vacuum pump screw rotor | |
| JP3807922B2 (en) | Single screw compressor with non-equal width teeth | |
| CN110030191B (en) | Vortex molded line tooth head structure of vortex compressor and correction method thereof | |
| CN105422448A (en) | Variable-tooth-width variable-pitch screw rotor | |
| CN211202285U (en) | Non-contact high-energy cycloid rotor | |
| CN110762011B (en) | Claw type pump rotor and claw type pump | |
| CN211314539U (en) | Hyperbolic rotor for Roots pump | |
| CN210218104U (en) | Variable cross-section scroll wrap of scroll compressor | |
| CN107989792B (en) | Full smooth screw rotor | |
| CN110645172B (en) | Screw vacuum pump rotor and screw vacuum pump | |
| CN208089543U (en) | The modified screw compressor in dynamic and static dish-type the end of a thread portion | |
| CN107084131A (en) | A kind of complete smooth screw rotor based on eccentric circle involute | |
| CN108019348B (en) | Screw rotor comprising elliptical arcs | |
| CN110439811B (en) | Rotor profile of double-screw compressor | |
| CN211082247U (en) | Universal high-form-factor profile structure for pump rotor | |
| CN107882735B (en) | A kind of bidentate Twin-screw vacuum pump with stringent closed type rotor line | |
| CN113530818B (en) | Single-head twisted lobe roots pump rotor and lobe pump | |
| CN108343605B (en) | Three-jaw type vacuum pump | |
| CN110821828B (en) | Hyperbolic rotor for Roots pump | |
| CN211116576U (en) | Full convex-concave non-contact type top circular cycloid rotor | |
| CN111779674B (en) | Rotor molded line of multi-lobe Roots pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WW01 | Invention patent application withdrawn after publication | ||
| WW01 | Invention patent application withdrawn after publication |
Application publication date: 20200211 |