CN113482912A - Large-discharge-capacity arc spiral gear pump without axial force - Google Patents
Large-discharge-capacity arc spiral gear pump without axial force Download PDFInfo
- Publication number
- CN113482912A CN113482912A CN202110900432.8A CN202110900432A CN113482912A CN 113482912 A CN113482912 A CN 113482912A CN 202110900432 A CN202110900432 A CN 202110900432A CN 113482912 A CN113482912 A CN 113482912A
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- Prior art keywords
- gear
- shaft
- gear shaft
- circular arc
- axial force
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- 238000007667 floating Methods 0.000 claims abstract description 25
- 238000007789 sealing Methods 0.000 claims abstract description 16
- 238000006073 displacement reaction Methods 0.000 claims abstract description 12
- 239000003921 oil Substances 0.000 claims description 67
- 239000010687 lubricating oil Substances 0.000 claims description 6
- 238000000034 method Methods 0.000 description 6
- 230000010354 integration Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
Images
Classifications
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- 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
- F04C2/14—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 toothed rotary pistons
- F04C2/16—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 toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
-
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
A large-displacement arc spiral gear pump without axial force comprises a front end cover (1), a pump body (3), a rear end cover (8), a driving gear shaft (4), a floating shaft sleeve (5), a driven gear shaft (12), an auxiliary driving gear shaft (7) and an auxiliary driven gear shaft (10), wherein the front end cover (1) and the rear end cover (8) are connected with the pump body (3) through positioning pins (2) and bolts (9), and an O-shaped sealing ring (13) is arranged between the end cover and the pump body (3) for sealing; in the pump body (3), the driving gear shaft (4) is connected with an external spline (7 a) of the auxiliary driving gear shaft (7) through an internal spline (4 b), the driven gear shaft (12) is connected with an external spline (10 a) of the auxiliary driven gear shaft (10) through an internal spline (12 b), and the axes of the two pairs of connecting shafts are parallel to each other; both sides of each gear shaft are provided with floating shaft sleeves (5); a sliding bearing (6) is arranged between the floating shaft sleeve (5) and the shaft for radial support.
Description
Technical Field
The invention relates to the technical field of hydraulic gear pumps, in particular to a large-discharge circular arc spiral gear pump technology.
Background
The hydraulic pump is the heart of the hydraulic system, and the function is for providing power for the hydraulic system, and hydraulic gear pump is one of hydraulic system's main power source, extensively is applied to agricultural machine, heavy industry machinery. The spiral tooth double-arc tooth-shaped hydraulic gear pump adopts an arc-involute-arc tooth shape, only one point of meshing is arranged at any cross section of the end face, and the problems of oil trapping, noise and large pressure pulsation of a straight tooth involute-shaped gear pump are effectively solved. However, since the helical teeth can generate meshing axial force and hydraulic axial force in the working process, an axial force counteracting device has to be additionally arranged, so that the complexity of the gear pump is increased, the potential internal leakage problem is increased, and the volumetric efficiency is reduced.
The Chinese patent named 'helical tooth double-arc tooth-shaped hydraulic gear pump with axial and radial static pressure support' (CN 110594150A) proposes that a high-pressure oil channel is formed in a rear end cover, high-pressure oil is respectively introduced into a cavity where a driving shaft is located in the rear end cover and a cavity where a driven shaft is located in the rear end cover, a plunger is used for forming a method for balancing the axial force of the driving shaft and the driven shaft through static pressure support, but a high-pressure contact surface is increased, and the potential internal leakage problem exists.
Chinese patent "one kind of gear pump and multiple pump" (CN 211474426U) proposes a multiple pump structure including multiple pump bodies capable of outputting a large flow rate of medium, but the structure has low integration level and many parts, and does not provide conditions for canceling axial force of the helical gear pump.
Disclosure of Invention
The invention aims to provide a large-discharge circular arc spiral gear pump without axial force.
The invention relates to a large-displacement arc spiral gear pump without axial force, which comprises a front end cover 1, a pump body 3, a rear end cover 8, a driving gear shaft 4, a floating shaft sleeve 5, a driven gear shaft 12, an auxiliary driving gear shaft 7 and an auxiliary driven gear shaft 10, wherein a right-handed driving gear 4a, a left-handed driven gear 12a, a left-handed auxiliary driving gear 7b and a right-handed auxiliary driven gear 10b are connected with the pump body 3 through a positioning pin 2 and a bolt 9, and an O-shaped sealing ring 13 is arranged between the end cover and the pump body 3 for sealing; in the pump body 3, the driving gear shaft 4 is connected with an external spline 7a of the auxiliary driving gear shaft 7 through an internal spline 4b, the driven gear shaft 12 is connected with an external spline 10a of the auxiliary driven gear shaft 10 through an internal spline 12b, and the axes of the two pairs of connecting shafts are parallel to each other; two sides of each gear shaft are provided with a floating shaft sleeve 5; a sliding bearing 6 is arranged between the floating shaft sleeve 5 and the shaft for radial support.
The invention has the advantages that the total axial force borne by the driving gear shaft and the total axial force borne by the auxiliary driving gear shaft are mutually offset, the total axial force borne by the driven gear shaft and the total axial force borne by the auxiliary driven gear shaft are mutually offset, an axial force offset device is removed, the structure of the pump is simplified, and the potential leakage loss of an axial force supporting structure is avoided; the two gear meshing pairs simultaneously absorb and discharge oil, and the gear pump has larger displacement; the gear pumps are separated and sealed through the floating shaft sleeves, the integration level is high, and the complex structure between the multiple pumps is avoided.
Drawings
Fig. 1 is an overall structural view of the present invention, fig. 2 is an installation view of a pump body and a floating boss, fig. 3 is a radial sectional view of the pump body, fig. 4 is an axial sectional view of the pump body, fig. 5 is a structural view of a driving gear shaft, fig. 6 is a structural view of a counter driven gear shaft, fig. 7 is a structural view of a driven gear shaft, fig. 8 is a structural view of a counter driving gear shaft, fig. 9 is a radial sectional view of a central floating boss 5-1, fig. 10 is a central end face sectional view of the central floating boss 5-1, and fig. 11 is a structural view of a rear end cap; the reference numbers and names are: the oil-saving pump comprises a front end cover 1, a positioning pin 2, a pump body 3, a pin hole 3a, a bolt hole 3b, an oil discharge cavity 3c, an oil suction cavity 3d, an oil suction hole 3e, an oil discharge hole 3f, an assembly hole 3g, an oil suction buffer cavity 3h, an oil discharge buffer cavity 3i, a driving gear shaft 4, a first right-handed circular arc gear 4a, a first positioning groove 4b, an inner spline 4c, a central floating shaft sleeve 5-1, a large mounting hole 5-1a, a small mounting hole 5-1b, a lubricating oil cavity 5-1c, an oil through hole 5-1d, a shaft end floating shaft sleeve 5-2, a sliding bearing 6, an auxiliary driving gear shaft 7, an outer spline 7a, a second positioning groove 7b, a first left-handed circular arc gear 7c, a rear end cover 8, an outer sealing groove 8a, a high-pressure oil groove 8b, an inner sealing groove 8c, a bolt hole 8d, a pin hole 8e, a shallow hole 8f, a bolt 9, an auxiliary driven gear shaft 10, a pin shaft 3e, a pump body and a pump body, The gear comprises an external spline 10a, a third positioning groove 10b, a second right-handed circular arc gear 10c, a positioning piece 11, a driven gear shaft 12, a second left-handed circular arc gear 12a, a fourth positioning groove 12b, an internal spline 12c, an O-shaped sealing ring 13, a lip-shaped sealing ring 14 and an elastic retaining ring 15.
Detailed Description
The invention designs the high-integration large-discharge gear pump without axial force by utilizing the equal and opposite total axial force borne by the gear shafts on the same axis to offset the axial force. The structure of which is shown in figure 1,
the left-handed auxiliary driving gear is connected with the pump body 3 through a positioning pin 2 and a bolt 9, and an O-shaped sealing ring 13 is arranged between the end cover and the pump body 3 for sealing; in the pump body 3, the driving gear shaft 4 is connected with an external spline 7a of the auxiliary driving gear shaft 7 through an internal spline 4b, the driven gear shaft 12 is connected with an external spline 10a of the auxiliary driven gear shaft 10 through an internal spline 12b, and the axes of the two pairs of connecting shafts are parallel to each other; two sides of each gear shaft are provided with a floating shaft sleeve 5; the driving gear shaft 4 and the driven gear shaft 12 form a pair of gear meshing pairs, the auxiliary driving gear shaft 7 and the auxiliary driven gear shaft 10 form a pair of gear meshing pairs, the gears are equal in size, and the rotation directions are opposite. A lip-shaped sealing ring 14 is arranged at the position, extending out of the front end cover 1, of the driving gear shaft 4, axial positioning is achieved through an elastic retaining ring 15, and external leakage possibly caused in the rotating process of the driving gear shaft 4 is prevented. A sliding bearing 6 is arranged in the floating shaft sleeve 5 to radially support the gear shaft.
Because the helical teeth can adopt the same axial force counteracting mode and structure form as the helical teeth, the helical teeth are also in the protection scope of the invention; the gear rotation combination described herein is not limited to this disclosure, and other gear rotation combinations that counteract axial forces are also within the scope of the present invention.
As shown in fig. 2 to 4, the pin hole 3a and the bolt hole 3b are respectively provided with a positioning pin 2 and a bolt 9 to realize positioning and connection between the pump body 3 and the front end cover 1 and the rear end cover 8. The assembly holes 3g fit the gear shafts 4, 7, 10, 12, the floating bushes 5 and the sliding bearings 6 therein. An oil suction hole 3e, an oil discharge hole 3f, an oil suction buffer cavity 3h and an oil discharge buffer cavity 3i are formed in the center of the pump body 3 and are all arranged on the same axis; an oil suction chamber 3d and an oil discharge chamber 3c are formed between the assembly hole 3g and the floating boss 5. When each gear shaft rotates, the gear on one side close to the oil suction cavity 3d is meshed and separated, the volume is increased to generate negative pressure, oil enters the oil suction hole 3e and then reaches the oil suction cavity 3d through the oil suction buffer cavity 3h, enters the two pairs of gear meshing pairs in the oil suction cavity 3d, the volume of one side close to the oil discharge cavity 3c is reduced due to the gear meshing, the oil is pressurized into high-pressure oil, and the high-pressure oil is discharged from the two pairs of gear meshing pairs respectively, collected through the oil discharge cavity 3c and then discharged along the oil discharge hole 3f through the oil discharge buffer cavity 3 i.
As shown in fig. 5 to 8, the right circular arc gear 4a of the driving gear shaft 4 is engaged with the left circular arc gear 12a of the driven gear shaft 12, and the left circular arc gear 7c of the auxiliary driving gear shaft 7 is engaged with the right circular arc gear 10c of the auxiliary driven gear shaft 10. The internal splines 4c of the driving gear shaft 4 are engaged with the external splines 7a of the counter driving gear shaft 7, and the internal splines 12c of the driven gear shaft 12 are engaged with the external splines 10a of the counter driven gear shaft 10. All gears have the same size and opposite rotation directions. In the working process of the gear, a meshing axial force and a hydraulic axial force are generated, the total axial force (the meshing axial force and the hydraulic axial force) borne by the driving gear shaft 4 and the auxiliary driving gear shaft 7 is equal in magnitude and opposite in direction, and the total axial force are mutually offset through the contacted shaft end surfaces; the total axial force (hydraulic axial force-meshing axial force) applied to the driven gear shaft 12 and the counter driven gear shaft 10 is equal in magnitude and opposite in direction, and is cancelled out by the end faces of the shaft in contact with each other.
As shown in fig. 1, 5 to 8, in order to ensure that the axial forces applied to the coaxial gear shafts are always equal, a first positioning groove 4b, a second positioning groove 7b, a third positioning groove 10b, and a fourth positioning groove 12b are respectively formed on the end surfaces of the driving gear shaft 4, the auxiliary driving gear shaft 7, the auxiliary driven gear shaft 10, and the driven gear shaft 12, which are close to the spline. The positioning grooves are arranged relative to the meshing line of the gear shaft, namely when the driving gear 4a and the auxiliary driving gear 7c and the driven gear 12a and the auxiliary driven gear 10c are installed, the contact area of the same axial gear and high-pressure oil is always equal at a certain moment in the rotation process of the gear shaft, and the corresponding area of each part is always synchronously rotated.
As shown in figures 1, 9 and 10, the floating shaft sleeve 5-1 is of a structure with two symmetrical ends and is provided with a large mounting hole 5-1a, a small mounting hole 5-1b and a lubricating oil cavity 5-1 c. A sliding bearing 6 and a shaft close to a spline end are arranged in the large mounting hole 5-1a, the contact part of the shaft end face is within the axial distance range of the lubricating oil cavity 5-1c, the lubricating oil cavity 5-1c is communicated with the oil discharge cavity 3c through the oil through hole 5-1d, high-pressure oil is introduced into the lubricating oil cavity 5-1d, the contact part of the shaft end face is lubricated and axially supported, and the spline connection part is lubricated.
As shown in fig. 11, the pin holes 8c and the bolt holes 8d are respectively provided with positioning pins 2 and bolts 9 to position and connect the rear end cover 8 and the pump body 3.
As shown in fig. 11, a high-pressure oil groove 8b is formed in an inner end surface connected to the pump body 3, high-pressure oil is introduced from the oil discharge cavity 3c and acts on the floating shaft sleeve 5, and the generated axial acting force axially compresses end surfaces of the first right-handed circular arc gear 4a, the first left-handed circular arc gear 7c, the second right-handed circular arc gear 10c and the second left-handed circular arc gear 12a respectively, so that an end surface gap can be reduced, and further, the leakage of the end surfaces of the gears can be reduced.
As shown in fig. 11, the shallow holes 8f are formed to prevent the counter drive gear shaft 7 and the counter driven gear shaft 10 from generating rotational friction with the end surfaces.
As shown in fig. 11, the outer seal groove 8a and the inner seal groove 8c are provided, and the O-ring 13 is added, so that the end surface leakage between the rear head cover 8 and the pump body 3 due to the introduced high-pressure oil can be prevented.
The invention works as follows: when the motor inputs torque, the driving gear shaft 4 drives the auxiliary driving gear shaft 7 to rotate through the internal and external splines 4c and 7a, and the driving gear shaft 4 and the auxiliary driving gear shaft 7 respectively drive the driven gear shaft 12 and the auxiliary driven gear shaft 10 to rotate in opposite directions through gear meshing pairs; when each gear shaft rotates, the separated part of the two pairs of gear meshing pairs generates negative pressure due to the volume increase, oil is sucked from the oil suction hole 3e of the pump body 3, flows to the oil suction cavity 3d through the oil suction buffer cavity 3h, then respectively enters the two pairs of gear meshing pairs through the oil suction cavity 3d, is subjected to gear pressurization, and then is collected through the oil discharge cavity 3c, enters the oil discharge hole 3f along the oil discharge buffer cavity 3i, and finally passes through an external pipeline supply system. In the process, because the axial force borne by the gear shaft is related to the rotation direction, the axial force borne by the driving gear shaft 4 is equal to the axial force borne by the auxiliary driving gear shaft 7 in magnitude and opposite in direction, and the axial forces borne by the driven gear shaft 12 and the auxiliary driven gear shaft 10 are equal in magnitude and opposite in direction through the contacted shaft end surfaces and are mutually offset through the contacted shaft end surfaces. In order to reduce the end surface leakage between the end surfaces of the gears and the floating shaft sleeve 5, a high-pressure oil groove 8b is formed in the inner end surface of the rear end cover 8 to introduce high-pressure oil in the oil discharge cavity 3c, the high-pressure oil acts on the floating shaft sleeve 5 to generate axial force, and the gear end surfaces are axially compressed to reduce end surface gaps.
Claims (10)
1. The utility model provides a big discharge capacity circular arc helical gear pump of no axial force, includes front end housing (1), the pump body (3), rear end cap (8), driving gear axle (4), unsteady axle sleeve (5), driven gear axle (12), vice driving gear axle (7), vice driven gear axle (10), dextrorotation driving gear (4 a), levogyration driven gear (12 a), levogyration counter drive gear (7 b), dextrorotation counter driven gear (10 b), its characterized in that: the front end cover (1) and the rear end cover (8) are connected with the pump body (3) through a positioning pin (2) and a bolt (9), and an O-shaped sealing ring (13) is arranged between the end cover and the pump body (3) for sealing; in the pump body (3), the driving gear shaft (4) is connected with an external spline (7 a) of the auxiliary driving gear shaft (7) through an internal spline (4 b), the driven gear shaft (12) is connected with an external spline (10 a) of the auxiliary driven gear shaft (10) through an internal spline (12 b), and the axes of the two pairs of connecting shafts are parallel to each other; both sides of each gear shaft are provided with floating shaft sleeves (5); a sliding bearing (6) is arranged between the floating shaft sleeve (5) and the shaft for radial support.
2. The large displacement circular arc helical gear pump without axial force of claim 1, wherein: an oil suction hole (3 e), an oil discharge hole (3 f), an assembling hole (3 g), an oil suction buffer cavity (3 h) and an oil discharge buffer cavity (3 i) are formed in the pump body (3); an oil suction cavity (3 d) and an oil discharge cavity (3 c) are formed between the pump body (3) and the floating shaft sleeve (5).
3. The large displacement circular arc helical gear pump without axial force of claim 1, wherein: the right-handed driving gear (4 a) is meshed with the left-handed driven gear (12 a), the left-handed auxiliary driving gear (7 b) is meshed with the right-handed auxiliary driven gear (10 b), and the right-handed driving gear (4 a) is equal to the left-handed auxiliary driving gear (7 b), and the left-handed driven gear (12 a) is opposite to the right-handed auxiliary driven gear (10 b) in size and rotation direction.
4. The large displacement circular arc helical gear pump without axial force of claim 3, wherein: and a first positioning groove (4 b), a second positioning groove (7 b), a third positioning groove (10 b) and a fourth positioning groove (12 b) are respectively formed on the end surfaces, close to the splines, of the driving gear shaft (4), the auxiliary driving gear shaft (7), the auxiliary driven gear shaft (10) and the driven gear shaft (12).
5. The large displacement circular arc helical gear pump without axial force of claim 1, wherein: the middle floating shaft sleeve (5-1) is of a structure with two symmetrical ends, and is provided with a large mounting hole (5-1 a), a small mounting hole (5-1 b), a lubricating oil cavity (5-1 c) and an oil through hole (5-1 d), wherein the oil through hole (5-1 d) is communicated with the oil discharge cavity (3 c).
6. The large displacement circular arc helical gear pump without axial force of claim 1, wherein: the rear end cover (8) is provided with a high-pressure oil groove (8 b), an inner sealing groove (8 a), an outer sealing groove (8 c) and a shallow hole (8 f), wherein the high-pressure oil groove (8 b) is communicated with the oil discharge cavity (3 c).
7. The large displacement circular arc helical gear pump without axial force of claim 1, wherein: the pin hole (8 c) and the bolt hole (8 d) are respectively provided with a positioning pin (2) and a bolt (9), so that the positioning and the connection between the rear end cover (8) and the pump body (3) are realized.
8. The large displacement circular arc helical gear pump without axial force of claim 1, wherein: a high-pressure oil groove (8 b) is formed in the inner end face connected with the pump body (3), high-pressure oil is introduced from the oil discharge cavity (3 c) to act on the floating shaft sleeve (5), and the generated axial acting force axially compresses the end faces of the first right-handed circular arc gear (4 a), the first left-handed circular arc gear (7 c), the second right-handed circular arc gear (10 c) and the second left-handed circular arc gear (12 a) respectively, so that the end face clearance can be reduced, and the gear end face leakage is reduced.
9. The large displacement circular arc helical gear pump without axial force of claim 1, wherein: the shallow holes (8 f) are formed, so that the auxiliary driving gear shaft (7) and the auxiliary driven gear shaft (10) can be prevented from generating rotary friction with the end faces.
10. The large displacement circular arc helical gear pump without axial force of claim 1, wherein: set up outer seal groove (8 a), interior seal groove (8 c), install O type sealing washer (13) additional, can prevent to take place the terminal surface because of the high-pressure oil that introduces between rear end cover 8 and the pump body 3 and leak.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110900432.8A CN113482912A (en) | 2021-08-06 | 2021-08-06 | Large-discharge-capacity arc spiral gear pump without axial force |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110900432.8A CN113482912A (en) | 2021-08-06 | 2021-08-06 | Large-discharge-capacity arc spiral gear pump without axial force |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113482912A true CN113482912A (en) | 2021-10-08 |
Family
ID=77944618
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110900432.8A Pending CN113482912A (en) | 2021-08-06 | 2021-08-06 | Large-discharge-capacity arc spiral gear pump without axial force |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN113482912A (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2211506Y (en) * | 1994-11-10 | 1995-11-01 | 青州液压件厂 | Improved two linkage gear pump |
| JP2001193671A (en) * | 1999-12-28 | 2001-07-17 | Shimadzu Corp | Multiple gear pump/motor |
| CN102562583A (en) * | 2012-02-10 | 2012-07-11 | 长治液压有限公司 | Triple gear pump |
| CN104481874A (en) * | 2014-11-27 | 2015-04-01 | 上海轩安环保科技有限公司 | Herringbone gear pump |
| CN107489611A (en) * | 2017-08-17 | 2017-12-19 | 合肥力威汽车油泵有限公司 | A kind of small impact gear-type oil pump |
| CN209671206U (en) * | 2019-04-08 | 2019-11-22 | 合肥长源液压股份有限公司 | A kind of compact-sized double-gear oil pump |
| CN110594150A (en) * | 2019-10-24 | 2019-12-20 | 山东大学 | Spiral tooth double-arc tooth-shaped hydraulic gear pump with axial and radial static pressure support |
-
2021
- 2021-08-06 CN CN202110900432.8A patent/CN113482912A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2211506Y (en) * | 1994-11-10 | 1995-11-01 | 青州液压件厂 | Improved two linkage gear pump |
| JP2001193671A (en) * | 1999-12-28 | 2001-07-17 | Shimadzu Corp | Multiple gear pump/motor |
| CN102562583A (en) * | 2012-02-10 | 2012-07-11 | 长治液压有限公司 | Triple gear pump |
| CN104481874A (en) * | 2014-11-27 | 2015-04-01 | 上海轩安环保科技有限公司 | Herringbone gear pump |
| CN107489611A (en) * | 2017-08-17 | 2017-12-19 | 合肥力威汽车油泵有限公司 | A kind of small impact gear-type oil pump |
| CN209671206U (en) * | 2019-04-08 | 2019-11-22 | 合肥长源液压股份有限公司 | A kind of compact-sized double-gear oil pump |
| CN110594150A (en) * | 2019-10-24 | 2019-12-20 | 山东大学 | Spiral tooth double-arc tooth-shaped hydraulic gear pump with axial and radial static pressure support |
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| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20211008 |