CN1206795A - Multi-blade type impeller Roots blower (pump) structure with counter-flow device - Google Patents
Multi-blade type impeller Roots blower (pump) structure with counter-flow device Download PDFInfo
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- CN1206795A CN1206795A CN 97121015 CN97121015A CN1206795A CN 1206795 A CN1206795 A CN 1206795A CN 97121015 CN97121015 CN 97121015 CN 97121015 A CN97121015 A CN 97121015A CN 1206795 A CN1206795 A CN 1206795A
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Abstract
The present invention relates to a multiblade type spiral Roots blower (pump) structure with countercurrent device. It adopts a kind of multiblade type blade wheel, and said blade top has a certain width, at the same time of meeting the conditions of that gamma 1 is greater than or equal to alpha-beta 1 + epsilon 1, gamma 2 is greater than or equal to alpha-beta 1 + epsilon 2 and theta is greater than or equal to gamma 1 + mu + gamma 2, it can isolate the countercurrent air admission, low-pressure air admission of machine shell inlet and high-pressure exhaustion of machine shell outlet each from other and make them do not interfere mutually so as to obviously raise its noise-reducing and cooling effect. Its blade top is equipped with labyrinth groove, so that it can further reduce radial leakage, collect and receive the dust particles and prevent blade and machine shell working surface from wearing.
Description
The present invention relates to the structure of a kind of roots blower (pump), particularly a kind of Multiblade impeller roots blower (pump) structure with backflow device.
The structure of existing roots blower (pump) and operation sketch include pair of parallel axle 1 as shown in Figure 1, and one two leaf-type impeller 4 is housed on the every parallel axes 1, utilize the synchromesh gear that is loaded on axle head, two impellers 4 are meshing with each other do counterrotating.Two-parallel axis 1 is loaded in the casing 3 with impeller 4, and casing 3 upper and lower ends are respectively equipped with casing suction port 2 and casing relief opening 7.When impeller 4 rotated in casing 3, the right cusp that is positioned at the vane tip 17 of relief opening 7 was Q, and when the Q point was sitting at the position of casing face end T, by the volume V of impeller 4 with casing 3 sealings, its pressure was suction pressure P
1When the slit occurring in case Q departs from T, the pressurized gas of casing relief opening 7 are with pressure P
2, the slit between Q, T is poured volume V and is compressed, and impeller 4 is produced flow-reversing impingement, noise and vibration that blast air is bigger because of periodically pulsing brings.Along with the needs of production development, the exhaust pressure P of requirement
2Increase day by day, not only make influence of noise even more serious, and the also greatly rising of the temperature of high pressure gas, and the normal operation and the operating life of serious threat roots blower (pump), thereby a long-term unsolved difficult problem both at home and abroad become.
Since the seventies, start with to reduce the bodily fluids kinetic noise from improving housing construction, people have carried out a large amount of explorations, before its major measure is exactly the slit appearance of attempting between Q, T, a part of high pressure air (or high pressure gas) is imported volume V in advance carry out pre-loading, make the pressure of V increase to P
3, P
3With P
2Between differential pressure dwindle as far as possible, to reduce flow-reversing impingement and noise.
Middle nineteen seventies, U.S. De Laisai (DRESSER) company has released the Roots's Webster blower that has Webster structure (Whispair), i.e. the first the boost product of noise reduction measure of adverse current that adopts in the world.Also released Roots's Webster vacuum pump of the straight-through atmosphere of exhaust simultaneously, its adverse current air inlet duct directly is communicated with atmosphere, utilize the differential pressure of cool air to the vacuum pump negative pressure, directly enters V with the generation adverse current double effects that noise reduction and adverse current cool off that boosts.But because impeller 4 is two blade profiles, adverse current air inlet duct is very near from relief opening, so in case adverse current air inlet duct be opened, soon because of the appearance in slit between Q, the T, the backflow that makes counter-current gas be subjected to high pressure gas is disturbed, and can't give full play to the usefulness of its noise reduction and cooling.The applicant has proposed utility application December nineteen ninety-five to Patent Office of the People's Republic of China for this reason, application number: 95235177.3, and title: the Roots blower, the vacuum pump new structure that have backflow device.Its objective is the near excessively shortcoming of adverse current inlet hole track pitch relief opening at two blade profile roots blowers (pump), adopt the wide blade tip type of two leaves impeller profile, to move in the adverse current air inlet duct, can prolong that adverse current is boosted and the process of adverse current cooling improving the usefulness of noise reduction and cooling, but still can't thoroughly eliminate the interference of high pressure gas to the adverse current air inlet.
Early eighties, the wild pool of Japan's space group ironworker has released ARJ type roots blower (pump), adopt trilobal cross impeller and aforesaid backflow device, make adverse current air inlet duct in suction port, move 30 ° along the housing working surface, thereby improved the adverse current effect, but because of the three leaf circular arc molded lines of impeller profile that adopt, so can not eliminate the negative influence of high pressure gas to the adverse current air inlet for using always.
Purpose of the present invention just is to overcome above-mentioned the deficiencies in the prior art, and a kind of roots blower that has backflow device and adopt the Multiblade impeller (pump) structure is provided, and makes adverse current air inlet and high pressure gas isolated, thereby strengthens noise reduction and cooling effect significantly.
Multiblade impeller roots blower (pump) structure of band backflow device provided by the invention, comprise roots blower (pump) and adverse current supplier, see also Fig. 2, Fig. 3 and Fig. 4, the adverse current supplier is arranged on the casing in the adverse current air inlet duct of gas transmission in casing by the adverse current suction tude, the technical measures that realize goal of the invention are: impeller adopts the Multiblade impeller, its vane tip is provided with top width, and being set in the casing working surface initial point S point of casing suction port and adverse current air inlet duct is γ to the formed central angle in axle center between the intersection point U point on the casing working surface
1, casing face end T point and adverse current air inlet duct are γ to the formed central angle in axle center between the following intersection point W point on the casing working surface
2, the top width of vane tip is β to the formed central angle in axle center
1, the center line of two adjacent blades is α to the formed central angle in axle center, is positioned at that cusp is M on the blade top width in adverse current duct, following cusp is N, is known by Fig. 3, when M point and U point overlap, promptly is in the adverse current air inlet and just will pours volume V by the slit between M, the U
1Carry out the critical localisation of pre-loading, be inlet end closed angle ε to the formed central angle in axle center this moment between right cusp P of the blade top width of inlet end and casing working surface initial point S
1, the right cusp P of inlet end blade top width point then exists P, S slit, inlet end closed angle ε on the left side that S is ordered
1, be decided to be negative value.Find from U.S. De Laisai (DRESSER) DVJ of company type Webster vacuum pump material object: ε
1Reach about in the of-15 °, recommend ε
1Be advisable for=0～-10 °.The top width of the vane tip on the impeller is B
1, impeller diameter is D, then B
1Pairing central angle β
1=2arcsin B
1/ D.The low-pressure admission that guarantees adverse current air inlet and casing suction port does not produce interference, then should satisfy:
γ
1〉=alpha-beta
1+ ε
1(1) condition; In like manner, in Fig. 4, the following cusp N that is positioned at the blade top width in adverse current duct overlaps with the following intersection point W of adverse current air inlet duct on the casing working surface, promptly being in the adverse current air inlet is near completion, and don't with the high pressure gas of casing relief opening mutually on the critical localisation of mutual interference, right cusp Q and the casing face end T that be positioned at the blade top width of exhaust end this moment are exhaust end closed angle ε to the formed central angle in axle center
2, the Q point promptly exists Q, T slit on the left side that T is ordered, exhaust end closed angle ε
2Be decided to be negative value, recommend ε
2=0～-10 °, guarantee that the adverse current air inlet in adverse current air inlet duct and the high pressure gas of casing relief opening do not produce interference, then should satisfy
γ
2〉=alpha-beta
1+ ε
2(2) condition.
If the angle of the vertical axis in casing working surface initial point S and casing Coal Face Passing Through axle center is δ
1, the angle of the vertical axis in the line in casing face end T and axle center and casing Coal Face Passing Through axle center is δ
2Common δ
1And δ
2All about 10 °.The formed central angle in wide UW axle center, adverse current air inlet duct is μ, and usually μ is about in the of 20 °, then casing working surface central angle θ=180 that the axle center is formed °+δ
1+ δ
2, when
θ 〉=γ
1+ μ+γ
2Realize when (3) then can guarantee above-mentioned formula (1), (2) really on the structure, thereby the high pressure gas of low-pressure admission, casing relief opening of really accomplishing adverse current air inlet and casing suction port is isolated mutually and do not disturb mutually, realized the object of the invention, realized that promptly Multiblade impeller roots blower (pump) structure of band backflow device provided by the invention should satisfy condition simultaneously:
γ
1≥α-β
1+ε
1
γ
2≥α-β
1+ε
2
θ≥γ
1+μ+γ
2
Further describe the present invention below in conjunction with accompanying drawing, embodiment.
Fig. 1 is existing roots blower (pump) structure and operation sketch schematic representation;
Fig. 2 is the structural representation of one embodiment of the present of invention (only showed right-hand part, left side and right-hand part symmetry, as follows);
Fig. 3 is Fig. 2 induction part operating structure schematic representation;
Fig. 4 is Fig. 2 discharge portion operating structure schematic representation;
Fig. 5 is a workflow preferred embodiment schematic representation of the present invention;
Fig. 6 is a workflow preferred embodiment schematic representation of the present invention;
Fig. 7 has the maze trough structural representation for preferred embodiment impeller top width of the present invention;
Fig. 8 is further embodiment of this invention five leaf-type impeller structural representations.
Among the figure, 1-parallel axes, 2-casing suction port, 3-casing, the 4-impeller, 5-blade, 6-blade, 7-casing relief opening, 8-adverse current supplier, 9-adverse current suction tude, 10-adverse current air inlet duct, 11-motor, the 12-intake silencer, 13-exhaust silencer, 14-roots blower (pump), 15-outlet pipe, 16-vane tip, the 17-interstage cooler, 18-maze trough, 19-backflow silencing apparatus, the 20-air intake filter, S-casing working surface initial point, T-casing face end.V, V1-volume, P1, P2, P3-pressure, U-adverse current air inlet duct intersection point on the casing working surface, the following intersection point of W-adverse current air inlet duct on the casing working surface, γ
1Between 2 of-S, the U to the formed central angle in axle center, γ
2Between 2 of-T, the W to the formed central angle in axle center, β
1-blade top width is to the formed central angle in axle center, the center line of the adjacent blade of α-two is to the formed central angle in axle center, P-is positioned at the right cusp of blade top width of inlet end, P '-be positioned at inlet end blade top width left side cusp, M-is positioned at cusp on the blade top width of adverse current air inlet duct, and N-is positioned at cusp under the blade top width of adverse current air inlet duct, and Q-is positioned at the right cusp of blade top width of exhaust end, the blade top width left side cusp of Q '-be positioned at exhaust end, ε
1-inlet end closed angle, ε
2-exhaust end closed angle, δ
1The angle of the vertical axis in-casing working surface beginning S and casing Coal Face Passing Through axle center, δ
2The angle of the vertical axis in the line in-casing face end T and axle center and casing Coal Face Passing Through axle center, the central angle that θ-casing working surface forms the axle center, μ-wide UW in adverse current air inlet duct is to the formed central angle in axle center, O-axle center, B
1The top width of-vane tip, the D-impeller diameter.
Embodiment as Multiblade impeller roots blower (pump) structure of band backflow device of the present invention, structural representation such as Fig. 2, Fig. 3, Fig. 4, Fig. 7 and shown in Figure 8, Multiblade impeller roots blower (pump) structure that the invention provides the band backflow device comprises roots blower (pump) and adverse current supplier, adverse current supplier 8 is arranged on the casing 3 in the adverse current air inlet duct 10 of gas transmission in casing 3 by adverse current suction tude 9, is γ to the formed central angle in axle center in the casing working surface initial point S of casing suction port 2 and adverse current air inlet duct 10 between the intersection point U on the casing working surface
1, between the following intersection point W on the casing working surface, be γ to the formed central angle in axle center in the casing face end T of casing relief opening 7 and adverse current air inlet duct 10
2, the top width of the vane tip of Multiblade impeller 4 is B
1, B
1To the formed central angle in axle center is β
1α is the angle between the Multiblade impeller two adjacent blade centrelines, be positioned at that cusp is M on the top width of blade in adverse current air inlet duct 10, following cusp is N, know by Fig. 3, Fig. 4, when M and U point overlap, between the right cusp P of top width of the blade 5 of inlet end and casing working surface initial point S, be inlet end closed angle ε to the formed central angle in axle center
1, when N and W point overlap, between cusp Q and casing face end, be exhaust end closed angle ε to the formed central angle in axle center at the top width of the blade of exhaust end
2, described each angle should be satisfied γ simultaneously
1〉=alpha-beta
1+ ε
1And γ
2〉=alpha-beta
1+ ε
2Condition; Counting n when the Multiblade impeller blade is 3,4,5 or more, and then two adjacent interlobate central angle alpha just should be 120 °, 90 °, 72 ° or 360 ° of n.When the Multiblade impeller is a trilobal cross, when promptly the Multiblade impeller blade is counted n=3, referring to Fig. 3 and Fig. 4, this moment γ
1=γ
2=90 °, inlet and outlet end closed angle ε is got in the central angle alpha between two blades=120 °
1=ε
2=-10 °, the then necessary top width B that guarantees the vane tip of impeller
1Institute is to central angle β
1It is 15 °～25 °, the trilobal cross line of this blade top width broad, aforementioned condition formula (1), (2) and (3) be can satisfy simultaneously, the low-pressure admission of adverse current air inlet and casing suction port 2 and the isolated and non-interfering mutually requirement of high pressure gas of casing relief opening 7 just realized.When the number of blade n=4 of impeller, referring to Fig. 3 and Fig. 4, θ=200 °, 10 central angle μ=20, adverse current air inlet duct °, then γ
1=γ
2=90 ° of requirements that can comprehensively guarantee aforementioned condition formula (1), (2) and (3), and structurally be achieved.And can adopt B to four leaves and the Multiblade impeller more than four leaves
1The impeller profile of=0 on-bladed top width.
The impeller of roots blower (pump) 14 has adopted bigger blade top width B in Multiblade impeller roots blower (pump) structure of band backflow device of the present invention
1, to high pressure reduce down radial leakage, to improve operational efficiency very favourable.Particularly when containing more serious small dust in work air inlet and the adverse current air inlet, because B
1Broad; at the resistance grit vane tip 16 is played great protective action aspect the accident of grinding disablement; as a kind of better embodiment; as shown in Figure 7; the top width of the vane tip of Multiblade impeller is provided with maze trough 18; it can further reduce radial leakage; improve operational efficiency; and when dust-laden is serious; maze trough 18 on the blade top width can be used as dust collecting trough; take in the grit in work air inlet and the adverse current air inlet; prevent from vane tip and casing working surface are caused wearing and tearing, can also rotate, transfer to casing relief opening 7 and discharge with air-flow with being accommodated on the blade top width grit in the maze trough 18 with impeller.
Fig. 8 adopts the structural representation of five leaf-type impeller molded lines for the present invention, and its working principle is the same, does not repeat them here.
Preferred embodiment as Multiblade impeller roots blower (pump) structure of band backflow device of the present invention, as Fig. 3, Fig. 4, Fig. 5, Fig. 7 and shown in Figure 8, directly feed the Roots pump of atmosphere for exhaust, its adverse current supplier 8 can directly be communicated with atmosphere, with the source of the gas of atmosphere as the adverse current air inlet, enter in the casing 3 by adverse current air inlet duct 10 by adverse current suction tude 9, the air-flow that Roots pump 14 is discharged through casing relief opening 7 both can directly enter atmosphere, also can enter atmosphere by outlet pipe 15, reduce noise pollution environment by exhaust silencer 13.As better embodiment, adverse current supplier 8 is when obtaining the adverse current charge air flow from atmosphere, and preferably the intake silencer 12 through band filter cleaner 20 enters in the casing 3 again.Because there is bigger natural differential pressure in the low temperature atmosphere to Roots pump import lower negative pressure, so the double effects that can realize boosting most economical adverse current noise reduction and adverse current cool off.
Preferred embodiment as Multiblade impeller roots blower (pump) structure of band backflow device of the present invention, as Fig. 2, Fig. 3, Fig. 4, Fig. 6, Fig. 7 and shown in Figure 8, for exhaust pressure is the Roots pump that positive roots blower and exhaust are not communicated with atmosphere, adverse current supplier 8 can be communicated with the exhaust end 7 of roots blower (pump) 14, its adverse current air feed is provided by high pressure gas, as better embodiment, when adverse current supplier 8 is obtained source of the gas from roots blower (pump) 14 exhausts, preferably pass through interstage cooler 17, or through backflow silencing apparatus 19, or interstage cooler 17 and backflow silencing apparatus 19 for contacting, cooling, gas after the noise elimination is entered in the casing 3 by adverse current air inlet duct 10 through adverse current suction tude 9, to realize the boost double effects of noise reduction and adverse current cooling of adverse current.
Multiblade impeller roots blower (pump) structure of band backflow device of the present invention has adopted the Multiblade impeller, and make being provided with of backflow device satisfy corresponding condition, the mutual interference mutually of fully isolated adverse current air inlet and high pressure gas and low-pressure admission, to obtain best adverse current effect, strengthen noise reduction and cooling effect significantly, guarantee the efficient normal operation of roots blower (pump), improve operating life.
Claims (16)
1, a kind of Multiblade impeller roots blower (pump) structure with backflow device comprises roots blower (pump) and adverse current supplier, and the adverse current supplier is arranged on the casing in the adverse current air inlet duct of gas transmission in casing by the adverse current suction tude, it is characterized in that; Impeller adopts the Multiblade impeller, and its vane tip (16) is provided with top width, and being positioned at the casing working surface initial point S of casing suction port (2) and adverse current air inlet duct (10) is γ to the formed central angle in axle center between the intersection point U on the casing working surface
1, being positioned at the casing face end T of casing relief opening (7) and adverse current air inlet duct (10) is γ to the formed central angle in axle center between the following intersection point W on the casing working surface
2, the top width B of the vane tip (16) of Multiblade impeller (4)
1To the formed central angle in axle center is β
1The center line of two adjacent blades is α to the formed central angle in axle center, be positioned at that cusp is M on the blade top width in adverse current air inlet duct (10), following cusp is N, adverse current air inlet duct (10) is μ to the formed central angle in axle center, the casing working surface is θ to the formed central angle in axle center, when M point and U point overlap, is inlet end closed angle ε to the formed central angle in axle center between the right cusp P of top width of the blade of inlet end and casing working surface initial point S
1, when N point and W point overlap, between right cusp Q of the blade top width of exhaust end and casing face end T, be exhaust end closed angle ε to the formed central angle in axle center
2, described each angle should be satisfied following relationship simultaneously:
γ
1≥α-β
1+ε
1
γ
2≥α-β
1+ε
2
θ≥γ
1+μ+γ
2。
2, according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 1, it is characterized in that described Multiblade impeller (4) number of blade n is 3,4,5 or more, central angle alpha is 120 °, 90 °, 72 ° or 360 °/n between two adjacent blades.
3, according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 2, it is characterized in that described Multiblade impeller (4) is a trilobal cross, when being Multiblade impeller (4) number of blade n=3, the top width of the vane tip (16) of impeller (4) is to the formed central angle β in axle center
1It is 15 °～25 °; The number of blade n of described Multiblade impeller 〉=4 o'clock, the top width B of vane tip (16)
1Can be 0.
4,, it is characterized in that the top width of the vane tip (16) of described Multiblade impeller is provided with maze trough (18) according to Multiblade impeller roots blower (pump) structure of claim 1 or 2 or 3 described band backflow devices.
5, according to Multiblade impeller roots blower (pump) structure of claim 1 or 2 or 3 described band backflow devices, it is characterized in that described roots blower (pump) is the Roots pump that row directly feeds atmosphere, its adverse current supplier (8) can be communicated with atmosphere, and its adverse current air inlet is directly provided by atmosphere.
6, according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 4, it is characterized in that described roots blower (pump) is the Roots pump that exhaust directly feeds atmosphere, its adverse current supplier (8) can be communicated with atmosphere, and its adverse current air inlet is directly provided by atmosphere.
7,, it is characterized in that described adverse current supplier (8) band air intake filter (20) and intake silencer (12) according to Multiblade impeller roots blower (pump) structure of claim 1 or 2 or 3 described band backflow devices.
8,, it is characterized in that described adverse current supplier (8) band air intake filter (20) and intake silencer (12) according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 4.
9, according to Multiblade impeller Roots blower (pump) structure of claim 1 or 2 or 3 described band backflow devices, it is characterized in that described roots blower (pump) (14) is the Roots pump that roots blower and exhaust are not communicated with atmosphere, its adverse current supplier (8) is to be communicated with roots blower (pump) (14) casing relief opening (7), and its adverse current air feed is provided by high pressure gas.
10, according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 4, it is characterized in that described roots blower (pump) (14) is the Roots pump that roots blower and exhaust are not communicated with atmosphere, its adverse current supplier (8) is to be communicated with roots blower (pump) (14) casing relief opening (7), and its adverse current air feed is provided by high pressure gas.
11,, it is characterized in that described adverse current supplier (8) is an interstage cooler (17) according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 9.
12,, it is characterized in that described adverse current supplier (8) is an interstage cooler (17) according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 10.
13, according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 9, it is characterized in that described adverse current supplier (8) take back stream silencing apparatus (19).
14, according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 10, it is characterized in that described adverse current supplier (8) take back stream silencing apparatus (19).
15,, it is characterized in that the interstage cooler (17) and the backflow silencing apparatus (19) of said adverse current supplier (8) band polyphone according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 9.
16,, it is characterized in that the interstage cooler (17) and the backflow silencing apparatus (19) of described adverse current supplier (8) band polyphone according to Multiblade impeller roots blower (pump) structure of the described band backflow device of claim 10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN971210152A CN1094174C (en) | 1997-11-20 | 1997-11-20 | Multi-blade type impeller Roots blower (pump) structure with counter-flow device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN971210152A CN1094174C (en) | 1997-11-20 | 1997-11-20 | Multi-blade type impeller Roots blower (pump) structure with counter-flow device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1206795A true CN1206795A (en) | 1999-02-03 |
| CN1094174C CN1094174C (en) | 2002-11-13 |
Family
ID=5176139
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN971210152A Expired - Fee Related CN1094174C (en) | 1997-11-20 | 1997-11-20 | Multi-blade type impeller Roots blower (pump) structure with counter-flow device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1094174C (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102878084A (en) * | 2012-08-04 | 2013-01-16 | 百事德机械（江苏）有限公司 | Counter flow cooling structure of single-stage negative-pressure roots blower |
| CN104265636A (en) * | 2014-09-10 | 2015-01-07 | 山东省章丘鼓风机股份有限公司 | Counter-flow cooling dry type Roots vacuum pump |
| US9004891B2 (en) | 2007-04-23 | 2015-04-14 | Edwards Limited | Vacuum pump |
| CN114151332A (en) * | 2020-09-07 | 2022-03-08 | 南通兴国通用机械有限公司 | Roots pump of making an uproar falls against current |
| WO2024199376A1 (en) * | 2023-03-31 | 2024-10-03 | 北京通嘉宏瑞科技有限公司 | Roots vacuum pump rotor having wavy biomimetic structure, profile design method, and roots vacuum pump |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2489887A (en) * | 1946-07-11 | 1949-11-29 | Roots Connersville Blower Corp | Rotary pump |
| JPH0733834B2 (en) * | 1986-12-18 | 1995-04-12 | 株式会社宇野澤組鐵工所 | Inner partial-flow reverse-flow cooling multistage three-leaf vacuum pump in which the outer peripheral temperature of the housing with built-in rotor is stabilized |
| US4859158A (en) * | 1987-11-16 | 1989-08-22 | Weinbrecht John F | High ratio recirculating gas compressor |
| US5090879A (en) * | 1989-06-20 | 1992-02-25 | Weinbrecht John F | Recirculating rotary gas compressor |
| CN2250437Y (en) * | 1995-12-01 | 1997-03-26 | 山东省章丘鼓风机厂 | New structure of Roots blower and vacuum pump with counter current device |
-
1997
- 1997-11-20 CN CN971210152A patent/CN1094174C/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9004891B2 (en) | 2007-04-23 | 2015-04-14 | Edwards Limited | Vacuum pump |
| CN102878084A (en) * | 2012-08-04 | 2013-01-16 | 百事德机械（江苏）有限公司 | Counter flow cooling structure of single-stage negative-pressure roots blower |
| CN104265636A (en) * | 2014-09-10 | 2015-01-07 | 山东省章丘鼓风机股份有限公司 | Counter-flow cooling dry type Roots vacuum pump |
| CN114151332A (en) * | 2020-09-07 | 2022-03-08 | 南通兴国通用机械有限公司 | Roots pump of making an uproar falls against current |
| WO2024199376A1 (en) * | 2023-03-31 | 2024-10-03 | 北京通嘉宏瑞科技有限公司 | Roots vacuum pump rotor having wavy biomimetic structure, profile design method, and roots vacuum pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1094174C (en) | 2002-11-13 |
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