CN103291607B - The blade differential pump that intermittent gearing mechanism drives - Google Patents
The blade differential pump that intermittent gearing mechanism drives Download PDFInfo
- Publication number
- CN103291607B CN103291607B CN201310242593.8A CN201310242593A CN103291607B CN 103291607 B CN103291607 B CN 103291607B CN 201310242593 A CN201310242593 A CN 201310242593A CN 103291607 B CN103291607 B CN 103291607B
- Authority
- CN
- China
- Prior art keywords
- blade
- enclosed cavity
- pump
- gearing mechanism
- intermittent gearing
- 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.)
- Expired - Fee Related
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Abstract
The invention discloses the blade differential pump that a kind of intermittent gearing mechanism drives, comprise intermittent gearing mechanism drive system and the pump housing; Wherein, intermittent gearing mechanism drive system is made up of four pairs of intermittent gearing mechanisms, a live axle and two output shafts, live axle and threephase asynchronous machine connect firmly, two output shafts connect firmly with two impeller shafts respectively, each impeller shaft is provided with two blades, adjacent blades and pump case form enclosed cavity.There is the defects such as discharge capacity is little, radial force is uneven for the displacement pump used at present, the present invention adopts intermittent gearing mechanism drive system and is coaxially installed on the impeller combination in pump case, periodically engaged by partial gear and be separated, uniform rotation is changed into periodically non-uniform rotation, make the blade cyclic opening and closing on two impellers, thus the enclosed cavity volume cyclically-varying that adjacent blades and pump case are formed, realize discharge opeing and the imbibition process of pump, improve the applicability of displacement pump at industrial production and sphere of life.
Description
Technical field
The present invention relates to a kind of displacement pump, particularly relate to a kind of periodicity differential by driving intermittent gearing mechanism to realize impeller shaft to rotate, and then drive opening and closing of blade cyclic, to realize the change of enclosed cavity volume, complete the blade differential pump of the imbibition of blade differential pump and the intermittent gearing mechanism driving of discharge opeing process.
Background technique
Blade differential pump is a kind of novel displacement pump, namely rely on contain the cyclically-varying that liquid closes working space volume energy cycle passed to liquid.Current displacement pump to exist suffered by rotor that radial load is uneven, displacement volume than the defect such as little, make displacement pump be difficult to obtain applying comparatively widely.For expanding the application of displacement pump, the present invention proposes the blade differential pump that intermittent gearing mechanism drives, and improves volume ratio and discharge capacity, improves the application area of displacement pump, can be applicable to the occasions such as high-lift, huge discharge.
Summary of the invention
The object of the invention is to for the deficiencies in the prior art, the blade differential pump that a kind of intermittent gearing mechanism drives is provided.
The object of the invention is to be achieved through the following technical solutions: the blade differential pump that a kind of intermittent gearing mechanism drives, it is primarily of intermittent gearing mechanism drive system and pump housing composition, wherein, intermittent gearing mechanism drive system is primarily of live axle, first output shaft, second output shaft, the first partial gear is on the driving shaft installed, second partial gear, 3rd partial gear and the 4th partial gear, be arranged on the first cylindrical gears on the first output shaft, second cylindrical gears and the three cylindrical gear be arranged on the second output shaft and the 4th cylindrical gears composition, described first output shaft and the second output shaft coaxial, in initial position, first partial gear and the first cylindrical gears engage with the first cylindrical gears, second partial gear is separated with the second cylindrical gears with the second cylindrical gears, 3rd partial gear is separated with three cylindrical gear with three cylindrical gear, and the 4th partial gear and the 4th cylindrical gears engage with the 4th cylindrical gears, the pump housing is made up of the first impeller shaft, the second impeller shaft and pump case.First impeller shaft and the first output shaft connect firmly, and the second impeller shaft and the second output shaft connect firmly; First impeller shaft is fixedly connected with the first symmetrical blade and Three-blade; Second impeller shaft is fixedly connected with the second symmetrical blade and quaterfoil; First blade, the second blade and pump case form the first enclosed cavity, and the second blade, Three-blade and pump case form the second enclosed cavity, and Three-blade, quaterfoil and pump case form the 3rd enclosed cavity, and the first blade, quaterfoil and pump case form the 4th enclosed cavity; Pump case has the first liquid sucting port, the second liquid sucting port, the first liquid port and the second liquid port.
The present invention has following technique effect relative to prior art: blade differential pump of the present invention obtains cyclical movement rule accurately by intermittent gearing mechanism drive system, overcome the unbalanced defect of radial load suffered by blade, improve volume ratio and discharge capacity, improve the application area of displacement pump, can be applicable to the occasions such as high-lift, huge discharge.
Accompanying drawing explanation
Fig. 1 is the blade differential pump schematic diagram that intermittent gearing mechanism drives;
Fig. 2 is two impeller relative position relations in the pump housing;
Fig. 3 is the rotation speed relation of output shaft;
Fig. 4 is t
1the position of moment two impeller;
Fig. 5 is t
2the position of moment two impeller;
Fig. 6 is t
3the position of moment two impeller;
Fig. 7 is t
4the position of moment two impeller;
Fig. 8 is t
5the position of moment two impeller; ;
Fig. 9 is t
6the position of moment two impeller;
Figure 10 is t
7the position of moment two impeller;
Figure 11 is t
8the position of moment two impeller;
Figure 12 is t
9the position of moment two impeller;
In figure, intermittent gearing mechanism drive system 1, live axle 2, first partial gear 3, second partial gear 4, 3rd partial gear 5, 4th partial gear 6, the pump housing 7, second impeller shaft 8, first impeller shaft 9, 4th cylindrical gears 10, three cylindrical gear 11, second cylindrical gears 12, first cylindrical gears 13, first output shaft 14, second output shaft 15, first blade 16, first enclosed cavity 17, first liquid port 18, second blade 19, first liquid sucting port 20, second enclosed cavity 21, Three-blade 22, 3rd enclosed cavity 23, second liquid port 24, quaterfoil 25, second liquid sucting port 26, 4th enclosed cavity 27 and pump case 28.
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
As shown in Figure 1 and Figure 2, the blade differential pump that the invention provides intermittent gearing mechanism driving forms primarily of intermittent gearing mechanism drive system 1 and the pump housing 7.
Intermittent gearing mechanism drive system 1 is primarily of live axle 2, first output shaft 14, second output shaft 15, the first partial gear 3, second partial gear 4, the 3rd partial gear 5 and the 4th partial gear 6 is on driving shaft 2 installed, is arranged on the first cylindrical gears 13, second cylindrical gears 12 on the first output shaft 14 and the three cylindrical gear 11 be arranged on the second output shaft 15 and the 4th cylindrical gears 10 and forms; In initial position, the first partial gear 3 engages with the first cylindrical gears 13, the second partial gear 4 is separated with the second cylindrical gears 12, and the 3rd partial gear 5 is separated with three cylindrical gear 11, and the 4th partial gear 6 and the 4th cylindrical gears 10 engage.
The pump housing 7 is made up of the first impeller shaft 9, second impeller shaft 8 and pump case 28, and the first impeller shaft 9 and the first output shaft 14 connect firmly, and the second impeller shaft 8 and the second output shaft 15 connect firmly.
First impeller shaft 9 is fixedly connected with the first symmetrical blade 16 and Three-blade 22.
Second impeller shaft 8 is fixedly connected with the second symmetrical blade 19 and quaterfoil 25.
First blade 16, second blade 19 and pump case 28 form the first enclosed cavity 17; Second blade 19, Three-blade 22 and pump case 28 form the second enclosed cavity 21; Three-blade 22, quaterfoil 25 and pump case 28 form the 3rd enclosed cavity 23; First blade 16, quaterfoil 25 and pump case 28 form the 4th enclosed cavity 27.
Pump case 28 has the first liquid port 18 and the second liquid port 24, first liquid sucting port 20, second liquid sucting port 26.
The rotating speed n of the first impeller shaft 9 and the second impeller shaft 8
1and n
2as shown in Figure 3.T
1in the moment, the rotating speed of the first impeller shaft 9 is n
w, the rotating speed of the second impeller shaft 8 is n
w; t
2in the moment, the rotating speed of the first impeller shaft 9 is by n
wchange n into
s, the rotating speed of the second impeller shaft 8 is n
w; t
3in the moment, the rotating speed of the first impeller shaft 9 is by n
schange n into
w, the rotating speed of the second impeller shaft 8 is n
w; t
4in the moment, the rotating speed of the first impeller shaft 9 is n
w, the rotating speed of the second impeller shaft 8 is by n
wchange n into
s; t
5in the moment, the rotating speed of the first impeller shaft 9 is n
w, the rotating speed of the second impeller shaft 8 is by n
schange n into
w; t
6in the moment, the rotating speed of the first impeller shaft 9 is by n
wchange n into
s, the rotating speed of the second impeller shaft 8 is n
w; t
7in the moment, the rotating speed of the first impeller shaft 9 is by n
schange n into
w, the rotating speed of the second impeller shaft 8 is n
w; t
8in the moment, the rotating speed of the first impeller shaft 9 is n
w, the rotating speed of the second impeller shaft 8 is by n
wchange n into
s.T
9moment, then enter next cycle period.
As shown in Figure 4, at t
1moment, the rotating speed of the first impeller shaft 9 and the second impeller shaft 8 is equal, first blade 16, Three-blade 22 and the second blade 19, quaterfoil 25 rotating speed are identical with the second impeller shaft 8 with the first impeller shaft 9, first enclosed cavity 17 and the 3rd enclosed cavity 23 reach maximum, and the second enclosed cavity 21 and the 4th enclosed cavity 27 reach minimum.This moment, first blade 16 seals the second liquid sucting port 26, Three-blade 22 seals the first liquid sucting port 20, the blade differential pump that intermittent gearing mechanism drives stops imbibition, second blade 19 seals the first liquid port 18, quaterfoil 25 seals the second liquid port 24, and the blade differential pump that intermittent gearing mechanism drives stops discharge opeing.
As shown in Figure 5, from t
1moment moves to t
2moment, first blade 16, second blade 19, Three-blade 22 are identical with quaterfoil 25 rotating speed, the constancy of volume of the first enclosed cavity 17, second enclosed cavity 21, the 3rd enclosed cavity 23, the 4th enclosed cavity 27, the blade differential pump that intermittent gearing mechanism drives stops discharge opeing and imbibition.
As shown in Figure 6, from t
2moment moves to t
3moment, the rotating speed n of the first impeller shaft 9
1be greater than the rotating speed n of the second impeller shaft 8
2, the rotating speed of the first blade 16 and Three-blade 22 is greater than the rotating speed of the second blade 19 and quaterfoil 25, and the first enclosed cavity 17 and the 3rd enclosed cavity 23 diminish gradually, and liquid is discharged from the first liquid port 18 and the second liquid port 24 respectively; Second enclosed cavity 21 and the 4th enclosed cavity 27 become greatly gradually, and liquid sucks from the first liquid sucting port 20 and the second liquid sucting port 26 respectively; When moving to t
3in the moment, the volume of the first enclosed cavity 17 and the 3rd enclosed cavity 23 reaches minimum, and the volume of the second enclosed cavity 21 and the 4th enclosed cavity 27 reaches maximum.This moment, the first blade 16 seals the first liquid port 18, Three-blade 22 seals the second liquid port 24, and the blade differential pump that intermittent gearing mechanism drives stops discharge opeing; Second blade 19 seals the first liquid sucting port 20, quaterfoil 25 seals the second liquid sucting port 26, and the blade differential pump that intermittent gearing mechanism drives stops imbibition.
As shown in Figure 7, from t
3moment moves to t
4moment, the rotating speed n of the first impeller shaft 9
1equal the rotating speed n of the second impeller shaft 8
2, the first blade 16, second blade 19, Three-blade 22 are identical with quaterfoil 25 rotating speed.This moment, the first enclosed cavity 17, second enclosed cavity 21, the 3rd enclosed cavity 23, the 4th enclosed cavity 27 constancy of volume, the blade differential pump that intermittent gearing mechanism drives stops discharge opeing and imbibition.
As shown in Figure 8, from t
4moment moves to t
5moment, the rotating speed n of the first impeller shaft 9
1be less than the rotating speed n of the second impeller shaft 8
2the rotating speed of the second blade 19 and quaterfoil 25 is greater than the rotating speed of the first blade 16 and Three-blade 22, first enclosed cavity 17 and the 3rd enclosed cavity 23 become large gradually, liquid sucks from the first liquid sucting port 20 and the second liquid sucting port 26 respectively, second enclosed cavity 21 and the 4th enclosed cavity 27 diminish gradually, and liquid is discharged from the first liquid port 18 and the second liquid port 24 respectively; When moving to t
5in the moment, the volume of the first enclosed cavity 17 and the 3rd enclosed cavity 23 reaches maximum, and the volume of the second enclosed cavity 21 and the 4th enclosed cavity 27 reaches minimum.This moment, the first blade 16 seals the first liquid sucting port 20, Three-blade 22 seals the second liquid sucting port 26, and the blade differential pump that intermittent gearing mechanism drives stops imbibition; Second blade 19 seals the second liquid port 24, quaterfoil 25 seals the first liquid port 18, and the blade differential pump that intermittent gearing mechanism drives stops discharge opeing.
As shown in Figure 9, from t
5moment moves to t
6moment, the rotating speed n of the first impeller shaft 9
1equal the rotating speed n of the second impeller shaft 8
2, the first blade 16, second blade 19, Three-blade 22 are identical with quaterfoil 25 rotating speed.This moment, the first enclosed cavity 17, second enclosed cavity 21, the 3rd enclosed cavity 23, the 4th enclosed cavity 27 constancy of volume, the blade differential pump that intermittent gearing mechanism drives stops discharge opeing and imbibition.
As shown in Figure 10, from t
6moment moves to t
7moment, the rotating speed n of the first impeller shaft 9
1be greater than the rotating speed n of the second impeller shaft 8
2the rotating speed of the first blade 16 and Three-blade 22 is greater than the rotating speed of the second blade 19 and quaterfoil 25, first enclosed cavity 17 and the 3rd enclosed cavity 23 diminish gradually, liquid is discharged from the second liquid port 24 and the first liquid port 18 respectively, second enclosed cavity 21 and the 4th enclosed cavity 27 become greatly gradually, and liquid sucks from the second liquid sucting port 26 and the first liquid sucting port 20 respectively; When moving to t
7in the moment, the volume of the first enclosed cavity 17 and the 3rd enclosed cavity 23 reaches minimum, and the volume of the second enclosed cavity 21 and the 4th enclosed cavity 27 reaches maximum.This moment, first blade 16 seals the second liquid port 24, Three-blade 22 seals the first liquid port 18, the blade differential pump that intermittent gearing mechanism drives stops discharge opeing, second blade 19 seals the second liquid sucting port 26, quaterfoil 25 seals the first liquid sucting port 20, and the blade differential pump that intermittent gearing mechanism drives stops imbibition.
As shown in figure 11, from t
7moment moves to t
8moment, the rotating speed n of the first impeller shaft 9
1equal the rotating speed n of the second impeller shaft 8
2, the first blade 16, second blade 19, Three-blade 22 are identical with quaterfoil 25 rotating speed.This moment, the first enclosed cavity 17, second enclosed cavity 21, the 3rd enclosed cavity 23, the 4th enclosed cavity 27 constancy of volume, the blade differential pump that intermittent gearing mechanism drives stops discharge opeing and imbibition.
As shown in figure 12, from t
8moment moves to t
9moment, the rotating speed of the first impeller shaft 9
n 1be less than the rotating speed n of the second impeller shaft 8
2the rotating speed of the second blade 19 and quaterfoil 25 is greater than the rotating speed of the first blade 16 and Three-blade 22, first enclosed cavity 17 and the 3rd enclosed cavity 23 become large gradually, liquid sucks from the second liquid sucting port 26 and the first liquid sucting port 20 respectively, second enclosed cavity 21 and the 4th enclosed cavity 27 diminish gradually, and liquid is discharged from the second liquid port 24 and the first liquid port 18 respectively; When moving to t
9in the moment, the volume of the first enclosed cavity 17 and the 3rd enclosed cavity 23 reaches maximum, and the volume of the second enclosed cavity 21 and the 4th enclosed cavity 27 reaches minimum.This moment, the first blade 16 seals the second liquid sucting port 26, Three-blade 22 seals the first liquid sucting port 20, and the blade differential pump that intermittent gearing mechanism drives stops imbibition; Second blade 19 has sealed the first liquid port 18, quaterfoil 25 has sealed the second liquid port 24, and the blade differential pump that intermittent gearing mechanism drives stops discharge opeing.T
9in the moment, the blade differential pump that intermittent gearing mechanism drives then enters subsequent work circulation.
Claims (1)
1. the blade differential pump of an intermittent gearing mechanism driving, it is characterized in that, it is primarily of intermittent gearing mechanism drive system (1) and the pump housing (7) composition, wherein, intermittent gearing mechanism drive system (1) is primarily of live axle (2), first output shaft (14), second output shaft (15), be arranged on the first partial gear (3) on live axle (2), second partial gear (4), 3rd partial gear (5) and the 4th partial gear (6), be arranged on the first cylindrical gears (13) on the first output shaft (14), second cylindrical gears (12) and the three cylindrical gear (11) be arranged on the second output shaft (15) and the 4th cylindrical gears (10) composition, described first output shaft (14) and the second output shaft (15) are coaxially, in initial position, first partial gear (3) and the first cylindrical gears (13) engagement, second partial gear (4) is separated with the second cylindrical gears (12), 3rd partial gear (5) is separated with three cylindrical gear (11), the 4th partial gear (6) and the engagement of the 4th cylindrical gears (10), the pump housing (7) is made up of the first impeller shaft (9), the second impeller shaft (8) and pump case (28), first impeller shaft (9) and the first output shaft (14) connect firmly, and the second impeller shaft (8) and the second output shaft (15) connect firmly, first impeller shaft (9) is fixedly connected with symmetrical the first blade (16) and Three-blade (22), second impeller shaft (8) is fixedly connected with symmetrical the second blade (19) and quaterfoil (25), first blade (16), the second blade (19) and pump case (28) form the first enclosed cavity (17), second blade (19), Three-blade (22) and pump case (28) form the second enclosed cavity (21), Three-blade (22), quaterfoil (25) and pump case (28) form the 3rd enclosed cavity (23), and the first blade (16), quaterfoil (25) and pump case (28) form the 4th enclosed cavity (27), pump case (28) has the first liquid sucting port (20), the second liquid sucting port (26), the first liquid port (18) and the second liquid port (24).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310242593.8A CN103291607B (en) | 2013-06-17 | 2013-06-17 | The blade differential pump that intermittent gearing mechanism drives |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310242593.8A CN103291607B (en) | 2013-06-17 | 2013-06-17 | The blade differential pump that intermittent gearing mechanism drives |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103291607A CN103291607A (en) | 2013-09-11 |
| CN103291607B true CN103291607B (en) | 2015-11-04 |
Family
ID=49093005
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310242593.8A Expired - Fee Related CN103291607B (en) | 2013-06-17 | 2013-06-17 | The blade differential pump that intermittent gearing mechanism drives |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103291607B (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103758750B (en) * | 2014-01-27 | 2015-07-22 | 浙江理工大学 | Six-blade differential pump driven by Fourier noncircular gears |
| CN103758751B (en) * | 2014-01-27 | 2015-07-22 | 浙江理工大学 | Four-blade differential pump driven by elliptic non-circular gears |
| CN103758757B (en) * | 2014-01-27 | 2016-02-17 | 浙江理工大学 | Eight blade differential pumps that a kind of Fourier's noncircular gear drives |
| CN103742406B (en) * | 2014-01-27 | 2015-07-22 | 浙江理工大学 | Four-vane differential velocity pump driven by Fourier noncircular gears |
| CN103742404B (en) * | 2014-01-27 | 2015-07-22 | 浙江理工大学 | Six-blade differential pump driven by elliptic non-circular gears |
| CN107676254B (en) * | 2017-11-03 | 2023-06-09 | 浙江水利水电学院 | Sliding four-vane differential pump driven by non-circular gears with free transmission ratio |
| CN109058099A (en) * | 2018-09-18 | 2018-12-21 | 江苏钧微动力科技有限公司 | A kind of twayblade vector pump |
| CN114526234B (en) * | 2022-01-07 | 2023-12-15 | 安徽泰臻真空科技有限公司 | Air extractor for spherical tokamak device |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2346014A (en) * | 1941-04-02 | 1944-04-04 | Aero Supply Mfg Co Inc | Fluid pump |
| FR944904A (en) * | 1947-03-29 | 1949-04-20 | Rotary positive displacement pump | |
| FR2455687A1 (en) * | 1979-05-03 | 1980-11-28 | Bermes Robert | Rotary pump for artificial heart - has two double bladed rotors within cylindrical stator to define two pumping chambers |
| JPS59101592A (en) * | 1982-11-30 | 1984-06-12 | Sakuji Kajiyama | Rotary pump |
| JPH0494423A (en) * | 1990-08-11 | 1992-03-26 | Mikio Kurisu | Rotary engine |
| CN1378042A (en) * | 2002-05-08 | 2002-11-06 | 蔡康人 | Alternative rotary pump |
| CN2555426Y (en) * | 2002-06-16 | 2003-06-11 | 哈尔滨工业大学 | Six-blade differential pump |
| CN1782393A (en) * | 2004-12-01 | 2006-06-07 | 哈尔滨工业大学 | Rotary guide bar-gear mechanism ariven blade differential pump |
| CN203297094U (en) * | 2013-06-17 | 2013-11-20 | 浙江理工大学 | Differential velocity vane pump driven by incomplete gear mechanisms |
-
2013
- 2013-06-17 CN CN201310242593.8A patent/CN103291607B/en not_active Expired - Fee Related
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2346014A (en) * | 1941-04-02 | 1944-04-04 | Aero Supply Mfg Co Inc | Fluid pump |
| FR944904A (en) * | 1947-03-29 | 1949-04-20 | Rotary positive displacement pump | |
| FR2455687A1 (en) * | 1979-05-03 | 1980-11-28 | Bermes Robert | Rotary pump for artificial heart - has two double bladed rotors within cylindrical stator to define two pumping chambers |
| JPS59101592A (en) * | 1982-11-30 | 1984-06-12 | Sakuji Kajiyama | Rotary pump |
| JPH0494423A (en) * | 1990-08-11 | 1992-03-26 | Mikio Kurisu | Rotary engine |
| CN1378042A (en) * | 2002-05-08 | 2002-11-06 | 蔡康人 | Alternative rotary pump |
| CN2555426Y (en) * | 2002-06-16 | 2003-06-11 | 哈尔滨工业大学 | Six-blade differential pump |
| CN1782393A (en) * | 2004-12-01 | 2006-06-07 | 哈尔滨工业大学 | Rotary guide bar-gear mechanism ariven blade differential pump |
| CN203297094U (en) * | 2013-06-17 | 2013-11-20 | 浙江理工大学 | Differential velocity vane pump driven by incomplete gear mechanisms |
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| CN103291607A (en) | 2013-09-11 |
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