CN2555426Y - Six-blade differential pump - Google Patents
Six-blade differential pump Download PDFInfo
- Publication number
- CN2555426Y CN2555426Y CN 02239208 CN02239208U CN2555426Y CN 2555426 Y CN2555426 Y CN 2555426Y CN 02239208 CN02239208 CN 02239208 CN 02239208 U CN02239208 U CN 02239208U CN 2555426 Y CN2555426 Y CN 2555426Y
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- CN
- China
- Prior art keywords
- eccentric
- gear
- gears
- noncircular
- impeller
- 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 utility model relates to a six-blade differential pump driven by an outer meshed non-round gear. The pump consists of two eccentric round gears fixed and connected to an input shaft according to 180 degree phase difference and having complete same knot curves; two non-round gears respectively meshed with the two eccentric round gears and having complete same knot curves, a pump shell and two impellers respectively fixed and connected with the two non-round gears and coaxially arranged in the pump shell. Each impeller is provided with three evenly distributed vanes; the adjacent vanes on the two impellers form six containing cavities with the pump shell. When the input shaft rotates, the eccentric gears get respectively meshed with the two non-round gears and drive the two non-round gears and the two impellers connected with the eccentric gears to rotate with different speeds, so as to ensure that the volumes of three containing cavities of the six closed containing cavities become bigger and the volumes of the other three become smaller, thereby realizing the liquid discharging and absorbing of the pump.
Description
Affiliated technical field
The utility model relate to a kind of utilize the periodicity variable speed of two that the two pairs of noncircular gears drive, that coaxial line is installed impellers to rotate (being called differential rotates) realizes that sealed volume changes and then finish the displacement pump of discharge opeing and imbibition process.
Background technique
At present, Chang Yong displacement pump has: capacity type vane pump, plunger pump, gear pump, screw pump.The common drawback of these displacement pumps is that displacement volume is littler than (discharge capacity/volume), makes displacement pump be difficult to be applied to the occasion of big discharge capacity.
Summary of the invention
The purpose of this utility model provides a kind of displacement volume than big novel displacement pump.
The technical solution adopted in the utility model is: identical two eccentric gears of pitch curve are connected firmly on input shaft by 180 ° of phase differences, and, these two eccentric gears respectively with identical, the coaxial mounted noncircular gears engagement of two pitch curves, these two noncircular gears again by two axles respectively be coaxially installed on pump case in two impellers connect.Have three on each impeller to equally distributed blade, adjacent vanes and pump case have constituted six sealing cavity volumes on two impellers.When input shaft rotates, eccentric gear meshes with two noncircular gears respectively, and two impeller variable speeds rotations that drive these two noncircular gears and connect with it, other three volumes diminish thereby make three volumes that distribute at interval in six sealing cavity volumes become greatly, realize the discharge opeing and the imbibition of pump.These the sealing cavity volumes volume and rate of volumetric change all bigger.
The beneficial effects of the utility model are, volume is little, and discharge capacity is big, and displacement volume is than big, the delivery pressure height.
Description of drawings
Fig. 1 is a principle sketch of the present utility model;
Fig. 2 is the meshing relation of two eccentric gears and two noncircular gears;
Fig. 3 is the relative position relation of two impellers;
When Fig. 4 is corner 0＜＜90 ° of two eccentric gears, the position of two noncircular gears;
When Fig. 5 is corner 0＜＜90 ° of two eccentric gears, the position of two impellers;
Fig. 6 is two eccentric gears when turning over 90 °, the position of two noncircular gears;
Fig. 7 is two eccentric gears when turning over 90 °, the position of two impellers;
When Fig. 8 is the 90 °＜ of corner＜270 ° of two eccentric gears, the position of two noncircular gears;
When Fig. 9 is the 90 °＜ of corner＜270 ° of two eccentric gears, the position of two impellers;
Figure 10 is two eccentric gears when turning over 270 °, the position of two noncircular gears;
Figure 11 is two eccentric gears when turning over 270 °, the position of two impellers;
When Figure 12 is the 270 °＜ of corner＜360 ° of two eccentric gears, the position of two noncircular gears;
When Figure 13 is the 270 °＜ of corner＜360 ° of two eccentric gears, the position of two impellers.
Among the figure 1, motor, 2, input shaft, 3, eccentric gear, 4, eccentric gear, 5, noncircular gear, 6, noncircular gear, 7, impeller shaft, 8, impeller shaft, 9, pump case, 10, impeller, 11, impeller, 12, outage, 13, imbibing hole.
Embodiment
In Fig. 1, identical eccentric gear of pitch curve (3) and eccentric gear (4) connect firmly on input shaft (2) by 180 ° of phase differences, identical noncircular gear of pitch curve (5) and noncircular gear (6) connect firmly with impeller shaft (7) and impeller shaft (8) respectively, and, respectively with eccentric gear (3) and eccentric gear (4) engagement.In Fig. 2, the relative eccentricity ε of eccentric gear is obtained by following set of equation with the relative centre distance c of eccentric gear with the noncircular gear engagement:
The eccentric distance e of eccentric gear is determined by following formula:
The centre distance A of e=R ε eccentric gear and noncircular gear engagement is determined by following formula:
The pitch curve of A=Rc noncircular gear is determined by following equation:
In the formula: the relative eccentricity of ε-eccentric gear;
The relative centre distance of c-eccentric gear and noncircular gear engagement;
The throw of eccentric of e-eccentric gear;
The centre distance of A-eccentric gear and noncircular gear engagement;
r
2The radius vector of-non-circular gear pitch curve;
The radius of R-eccentric gear pitch curve;
1The corner of-eccentric gear;
2The polar angle of-non-circular gear pitch curve.In Fig. 3, the impeller (10) and the impeller (11) that are coaxially installed in the pump case (9) connect firmly with impeller shaft (7) and impeller shaft (8) respectively.The blade that two symmetrical distributions are arranged respectively on impeller (10) and the impeller (11).Adjacent blades on impeller (10) and the impeller (11) and pump case have constituted six sealing cavity volume I, II, III, IV, V, VI respectively.When input shaft (2) when rotating counterclockwise, eccentric gear (3), (4) are begun to rotate counterclockwise with input shaft (2) by position shown in Figure 2.Under the driving of eccentric gear (3), (4), noncircular gear (5), (6) and impeller (10), (11) clockwise rotate.When eccentric gear (3), (4) and noncircular gear (5), (6) went to position shown in Figure 4, impeller (10), (11) went to position shown in Figure 5.At this moment, the angular velocity of impeller (10) is greater than the angular velocity of impeller (11), and the volume of enclosed cavity I, III, V diminishes, and fluid is discharged from outage (12); Meanwhile, it is big that the volume of enclosed cavity II, IV, VI becomes, and fluid sucks from imbibing hole (13).When input shaft (2) turns over 90 °, eccentric gear (3), (4) and noncircular gear (5), (6) go to position shown in Figure 6, when impeller (10), (11) go to position shown in Figure 7, impeller (10) equates with the angular velocity of impeller (11), it is minimum that the volume of enclosed cavity I, III, V reaches, it is maximum that the volume of enclosed cavity II, IV, VI reaches, and two blades of impeller this moment (10) are sealed two outages (12) just, and two blades of impeller (11) are sealed two imbibing holes (13) just.Input shaft (2) is rotated further, eccentric gear (3), (4) and noncircular gear (5), (6) go to position shown in Figure 8, when impeller (10), (11) go to position shown in Figure 9, the angular velocity of impeller (10) is less than the angular velocity of impeller (11), enclosed cavity I, III, V communicate with imbibing hole (13), and it is big that volume becomes, and fluid sucks from imbibing hole (13); Enclosed cavity II, IV, VI communicate with outage (12), and volume diminishes, and fluid is discharged from outage (12).Input shaft (2) turns over 270 °, eccentric gear (3), (4) and noncircular gear (5), (6) go to position shown in Figure 10, when impeller (10), (11) go to position shown in Figure 11, impeller (10) equates with the angular velocity of impeller (11), it is maximum that the volume of enclosed cavity I, III, V reaches, it is minimum that the volume of enclosed cavity II, IV, VI reaches, and two blades of impeller this moment (10) are sealed two imbibing holes (13) just, and two blades of impeller (11) are sealed two outages (12) just.Input shaft (2) is rotated further, eccentric gear (3), (4) and noncircular gear (5), (6) go to position shown in Figure 12, when impeller (10), (11) go to position shown in Figure 13, the angular velocity of impeller (10) is greater than the angular velocity of impeller (11), enclosed cavity I, III, V communicate with outage (12), and volume diminishes, and fluid is discharged from outage (12); Enclosed cavity II, IV, VI communicate with imbibing hole (13), and the volume change is big, and fluid sucks from imbibing hole (13).When input shaft (2) turned over 360 °, differential pump had been finished twice imbibition and twice discharge opeing process.
Claims (3)
1. blade differential pump, it is characterized in that: identical two eccentric gears of pitch curve connect firmly on input shaft by 180 ° of phase differences, and, these two eccentric gears respectively with identical, the coaxial mounted noncircular gears engagement of two pitch curves, these two noncircular gears again by two axles respectively be coaxially installed on pump case in two impellers connect.
2. six blade differential pumps according to claim 1 is characterized in that the relative eccentricity ε of eccentric gear is obtained by following set of equation with the relative centre distance c of eccentric gear with the noncircular gear engagement:
The eccentric distance e of eccentric gear is determined by following formula:
The centre distance A of e=R ε eccentric gear and noncircular gear engagement is determined by following formula:
The pitch curve of A=Rc noncircular gear is determined by following equation:
In the formula: ε---the relative eccentricity of eccentric gear;
The relative centre distance of c---eccentric gear and noncircular gear engagement;
The throw of eccentric of e---eccentric gear;
The centre distance of A---eccentric gear and noncircular gear engagement;
r
2---the radius vector of non-circular gear pitch curve;
R---the radius of eccentric gear pitch curve;
1---the corner of eccentric gear;
2---the polar angle of non-circular gear pitch curve.
3. six blade differential pumps according to claim 1 is characterized in that having on each impeller three equally distributed blades, and adjacent vanes and pump case have constituted six sealing cavity volumes on two impellers.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 02239208 CN2555426Y (en) | 2002-06-16 | 2002-06-16 | Six-blade differential pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 02239208 CN2555426Y (en) | 2002-06-16 | 2002-06-16 | Six-blade differential pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2555426Y true CN2555426Y (en) | 2003-06-11 |
Family
ID=33712665
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 02239208 Expired - Fee Related CN2555426Y (en) | 2002-06-16 | 2002-06-16 | Six-blade differential pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2555426Y (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006128331A1 (en) * | 2005-05-31 | 2006-12-07 | Lejun Pang | Rotary engine |
| CN103291607A (en) * | 2013-06-17 | 2013-09-11 | 浙江理工大学 | Incomplete gear mechanism-driven blade differential pump |
| CN103742404A (en) * | 2014-01-27 | 2014-04-23 | 浙江理工大学 | Six-blade differential pump driven by elliptic non-circular gears |
| CN103758749A (en) * | 2014-01-27 | 2014-04-30 | 浙江理工大学 | Sinusoidal non-circular gear driven six-vane differential velocity pump |
| CN103758750A (en) * | 2014-01-27 | 2014-04-30 | 浙江理工大学 | Six-blade differential pump driven by Fourier noncircular gears |
| CN103758753A (en) * | 2014-01-27 | 2014-04-30 | 浙江水利水电学院 | Six-blade differential speed pump driven by Pascal non-circular gears |
| CN113700646A (en) * | 2021-09-07 | 2021-11-26 | 南京工业泵厂 | Rotor pump |
-
2002
- 2002-06-16 CN CN 02239208 patent/CN2555426Y/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006128331A1 (en) * | 2005-05-31 | 2006-12-07 | Lejun Pang | Rotary engine |
| CN103291607A (en) * | 2013-06-17 | 2013-09-11 | 浙江理工大学 | Incomplete gear mechanism-driven blade differential pump |
| CN103291607B (en) * | 2013-06-17 | 2015-11-04 | 浙江理工大学 | The blade differential pump that intermittent gearing mechanism drives |
| CN103742404A (en) * | 2014-01-27 | 2014-04-23 | 浙江理工大学 | Six-blade differential pump driven by elliptic non-circular gears |
| CN103758749A (en) * | 2014-01-27 | 2014-04-30 | 浙江理工大学 | Sinusoidal non-circular gear driven six-vane differential velocity pump |
| CN103758750A (en) * | 2014-01-27 | 2014-04-30 | 浙江理工大学 | Six-blade differential pump driven by Fourier noncircular gears |
| CN103758753A (en) * | 2014-01-27 | 2014-04-30 | 浙江水利水电学院 | Six-blade differential speed pump driven by Pascal non-circular 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 |
| CN103758750B (en) * | 2014-01-27 | 2015-07-22 | 浙江理工大学 | Six-blade differential pump driven by Fourier noncircular gears |
| CN103758749B (en) * | 2014-01-27 | 2015-07-22 | 浙江理工大学 | Sinusoidal non-circular gear driven six-vane differential velocity pump |
| CN113700646A (en) * | 2021-09-07 | 2021-11-26 | 南京工业泵厂 | Rotor pump |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |