CN205534993U - Gear formula variable pump - Google Patents
Gear formula variable pump Download PDFInfo
- Publication number
- CN205534993U CN205534993U CN201620290160.9U CN201620290160U CN205534993U CN 205534993 U CN205534993 U CN 205534993U CN 201620290160 U CN201620290160 U CN 201620290160U CN 205534993 U CN205534993 U CN 205534993U
- Authority
- CN
- China
- Prior art keywords
- gear
- compensating groove
- section
- driven gear
- driving gear
- 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.)
- Active
Links
Landscapes
- Rotary Pumps (AREA)
Abstract
The utility model relates to a gear formula variable pump, driving gear and driven gear including the shell, in locating shell cavity, still be equipped with among the shell cavity one with the driven gear coaxial coupling and can with driven gear's axial displacement together cylindricality slider, be equipped with on the cylindricality slider along cylindricality slider shaft to the compensating groove that extends, the one end of compensating groove extend to driven gear the terminal surface and can with pocketed oil chamber intercommunication. Through such mode, at driven gear axial displacement's in -process, the compensating groove can communicate with the pocketed oil chamber to reduce the pressure fluctuation in pocketed oil chamber, reduce cavitation corrosion and cavitation phenomenon in the pocketed oil chamber.
Description
Technical field
This utility model relates to a kind of gear type variable rate pump, particularly to a kind of gear type variable rate pump as engine oil pump.
Background technology
In recent years, the problem such as environmental pollution and energy scarcity is increasingly severe, and auto industry is energy resource consumption and environmental pollution
Important sources.Automobile can by improving the method and measure such as the combination property of electromotor, body lightening, Brake energy recovery,
Reach the purpose of energy-saving and emission-reduction.Become displacement oil pump use on automobile, it is also possible to reach the purpose of automotive energy-saving emission-reducing.Machine
Oil pump is the important composition parts of vehicle lubricating system, its function be machine oil is increased to certain pressure after, then be transported to automobile and send out
The component surface that respectively rubs of motivation, by offer lubricating oil continuously to reduce the abrasion of each part, thus improves automobile engine
The stability of work and service life.In traditional automobile engine, use gear type dosing pump is as lubricating oil pump, along with electromotor
The raising of rotating speed, the fuel delivery of lubricating oil pump is linearly increasing, must be let out by pressure limiting valve by the lubricating oil that supply during the highest rotating speed more
Dew falls.Power needed for lubricating oil pump is provided by electromotor, and dosing pump can consume electromotor power consumption excessively when high rotating speed.Become discharge capacity
Lubricating oil pump can reasonably regulate pump delivery according to the needs of lubricating system, thus reduce the power consumption consumption of electromotor.According to
External research report can draw, uses the automobile engine becoming displacement oil pump can reduce the fuel oil consumption of 0.5%～2%,
And when electromotor works for a long time under high speed conditions, the fuel oil using the automobile of displacement-variable oil pump can reduce by 3% disappears
Consumption.
Gear type variable rate pump is usually used in automobile engine, and such as Chinese patent CN203384624U discloses a kind of variable displacement
Lubricating oil pump, this lubricating oil pump is a kind of gear type variable rate pump, the driving gear including shell, being located in shell inner cavity and driven gear,
Being additionally provided with a cylindrical slide coaxially connected with driven gear in shell inner cavity, cylindrical slide is coaxially connected with driven gear and can be with
Driven gear moves axially together；Every discharge capacity that turns can be changed by changing the engaging width of driven gear and driving gear, thus
Realize variable regulation.Operationally, the overlap coefficient of the engagement of driving gear and driven gear is more than 1, i.e. for gear type variable rate pump
Two pairs of gear teeth must be had simultaneously to be meshed, form pocketed oil chamber between driving gear and driven gear, the volume in pocketed oil chamber can be with gear
Rotation and change.When the volume in pocketed oil chamber reduces, the fluid in pocketed oil chamber is squeezed and produces high pressure, and by fluid from tired
Oil pocket is extruded, causes fluid to generate heat, and, the part such as the bearing of gear type variable rate pump also can unbalance stress；When pocketed oil chamber
When volume increases, pocketed oil intracavity can form parital vacuum, and the fluid in pocketed oil chamber can occur cavitation corrosion, noise, vibration and cavitation.
Here it is the pocketed oil phenomenon of gear pump, pocketed oil phenomenon can result in the pressure fluctuation of gear pump.In order to improve the workability of gear pump
Can, it is necessary to reduce the pressure fluctuation in pocketed oil chamber.
In gear type dosing pump, alleviating the main method of Oil-blocking Phenomenon in Gear Oil Pump is to open compensating groove on the sidewall of chamber in the enclosure, unloads
The design of lotus groove be external toothing the design of gear type dosing pump in one of of paramount importance link, the design of compensating groove is the most reasonable,
Directly influence service behaviour and the service life of gear pump.Compensating groove principal mode has: 1) relative driving gear and driven gear
The double square compensating groove that the line of centres is arranged symmetrically with；2) Double Circle that driving gear and the driven gear line of centres are arranged symmetrically with relatively
Compensating groove；3) relative driving gear and double compensating grooves of driven gear line of centres unsymmetrical arrangement.But these compensating grooves are opened in
On the two end cover plate of driving gear and driven gear, may be only available for driving gear and the driven gear end face feelings relative to invariant position
Condition, for becoming displacement gear pump, owing to the engaging width of driving gear and driven gear changes along with the rotation speed change of lubricating oil pump
Become, so driving gear can change relative to position with the end face of driven gear, so, due to fixed displacement formula gear pump and change
The architectural difference of displacement gear pump and the difference of working method, the compensating groove structure in gear type dosing pump cannot be applicable to become row
Flux gear pump, there is no the effective ways solving pocketed oil phenomenon in current variable gear wheel pump.
Utility model content
The shortcoming of prior art in view of the above, this utility model provides a kind of gear type variable rate pump, it is possible in release pocketed oil chamber
Pressure, reduce pressure fluctuation.
In order to achieve the above object and relevant purpose, a kind of gear type variable rate pump of the present utility model adopts the following technical scheme that one
Plant gear type variable rate pump, the driving gear including shell, being located in shell inner cavity and driven gear, driving gear and driven gear
Being meshed and form pocketed oil chamber, being additionally provided with a cylindrical slide in shell inner cavity, cylindrical slide is coaxially connected with driven gear and can be with
Driven gear moves axially together, is provided with along the axially extended compensating groove of cylindrical slide on cylindrical slide, and one end of compensating groove is prolonged
Extend the end face of driven gear and can connect with described pocketed oil chamber.
Further, cylindrical slide is provided with one section of arcwall face matched with the outside circle of driving gear, arranges on arcwall face
There is described compensating groove.
Further, shell is provided with inlet port and oil drain out, and described compensating groove is arranged on the center of driving gear and driven gear
Between line and oil drain out.
Further, being perpendicular to the cross section that compensating groove cross section is compensating groove of cylindrical slide axis, the cross section of compensating groove is from leaning on
One end of nearly driven gear end face is gradually increased to the other end.
Further, the axial length of compensating groove is more than or equal to driving gear with the maximum engagement width of driven gear with minimum
The difference of engaging width.
Preferably, it is perpendicular to the cross section that compensating groove cross section is compensating groove of cylindrical slide axis, driving gear and driven gear
Between the cross section of the line of centres and described compensating groove, minimum range is Bd, formula below determine:
In formula, m is the modulus of driving gear and driven gear；For driving gear and the angle of engagement of driven gear；For driving tooth
Wheel and the pressure angle of driven gear.
Further, the longitudinal section that compensating groove cross section is compensating groove of the dead in line with driving gear, the longitudinal section of compensating groove in
Rectangle/trapezoidal/triangle.
Further, being perpendicular to the cross section that compensating groove cross section is compensating groove of cylindrical slide axis, the cross section of compensating groove is one
Section is along the circular section of the outside circle extension of driving gear.
Further, the two ends of described circular section are 25 ° with the line angle at driving gear center.
Further, the cross section of compensating groove is 1～2mm along the size of driving gear radial direction.
As it has been described above, a kind of gear type variable rate pump of the present utility model, have the advantages that the post at gear type variable rate pump
It is provided with axially extended compensating groove on shape slide block, axially moves when the driven gear of gear type variable rate pump and make driving gear end face
During with driven gear end face the most at grade, owing to cylindrical slide moves together with driven gear, and the end face of compensating groove prolongs
Extend driven gear end face, so the cross section, pocketed oil chamber of driven gear end connects in driven gear end with compensating groove；By
Axially extending in compensating groove, the cross section, pocketed oil chamber of driving gear end connects in driving gear end with compensating groove, by this
The mode of sample, during driven gear axially moves, compensating groove can connect with pocketed oil chamber, thus reduces the pressure in pocketed oil chamber
Power is pulsed, and reduces the cavitation corrosion in pocketed oil chamber and cavitation phenomenon.
Accompanying drawing explanation
Fig. 1 is shown as the schematic perspective view of the gear type variable rate pump of this utility model embodiment, and housing portion does not shows.
Fig. 2 is shown as the schematic cross-section of A-A in Fig. 1, only shows driving gear and driven gear.
Fig. 3 is shown as the schematic cross-section of B-B in Fig. 1, only shows cylindrical slide and coordinates cylinder.
Fig. 4 is shown as the schematic perspective view of cylindrical slide.
Fig. 5 is shown as driving gear, driven gear, pocketed oil chamber and the schematic cross-section of compensating groove axially observed from driving gear.
Fig. 6 is shown as the schematic cross-section of C-C in Fig. 3, only shows the longitudinal section of compensating groove.
Piece mark explanation
1 driving gear 6 compensating groove
The cross section of 2 pocketed oil chamber 7 compensating grooves
The longitudinal section of 3 driven gear 8 compensating grooves
4 cylindrical slides 9 coordinate cylinder
5 arcwall faces
Detailed description of the invention
Below by way of specific instantiation, embodiment of the present utility model being described, those skilled in the art can be by this specification institute
The content disclosed understands other advantages of the present utility model and effect easily.This utility model can also be by the most different tools
Body embodiment is carried out or applies, and the every details in this specification can also be based on different viewpoints and application, at the not back of the body
Various modification or change is carried out under spirit of the present utility model.
Fig. 1 is shown as the schematic perspective view of the gear type variable rate pump of this utility model embodiment, and housing portion does not shows, such as Fig. 1
Shown in, a kind of gear type variable rate pump that this utility model provides, including shell (not showing in Fig. 1), it is located in shell inner cavity
Driving gear 1 and driven gear 3, driving gear 1 and driven gear 3 be meshed and form pocketed oil chamber 2 (see Fig. 2 and Fig. 5),
Being additionally provided with a cylindrical slide 4 in shell inner cavity, cylindrical slide 4 is coaxially connected with driven gear 3 and can be together with driven gear 3
Move axially；Cylindrical slide 4 is provided with along the axially extended compensating groove of cylindrical slide 46；One end of compensating groove 6 extends to
The end face of driven gear 3 also can connect with described pocketed oil chamber 2.So, because arranging on the cylindrical slide of gear type variable rate pump
Axially extended compensating groove, axially moves when the driven gear of gear type variable rate pump and makes driving gear end face and driven gear end
Face the most at grade time, owing to cylindrical slide moves together with driven gear, and the end face of compensating groove extends to driven gear
End face, so the cross section, pocketed oil chamber of driven gear end connects in driven gear end with compensating groove；Owing to compensating groove is axial
Extending, the cross section, pocketed oil chamber of driving gear end connects in driving gear end with compensating groove, by such mode,
During driven gear axially moves, compensating groove can connect with pocketed oil chamber, thus reduces the pressure fluctuation in pocketed oil chamber, reduces
Cavitation corrosion in pocketed oil chamber and cavitation phenomenon.
As shown in Figure 3 and Figure 4, in gear type variable rate pump, cylindrical slide 4 is provided with the outside circle of a section and driving gear 1
The arcwall face 5 matched, arcwall face 5, towards driving gear 1, driving gear 1 is also coaxially connected with one and cylindrical slide 4
On the cooperation cylinder 9 that matches of arcwall face 5, when driving gear 1, driven gear 3, cylindrical slide 4 and coordinate cylinder 9 to pacify
When being contained in shell (not shown) inner chamber, driving gear 1 and driven gear 3 are always at engagement and form pocketed oil
Chamber 2 (see Fig. 2 and Fig. 5), both sides, pocketed oil chamber 2 are oil sucting cavity (not shown) and oil-discharging cavity (not shown) respectively,
Due to shell inner cavity sidewall and driving gear 1 tooth top, the tooth top of driven gear 3, the external cylindrical surface of cylindrical slide 4, join
The external cylindrical surface closing cylinder 9 closely cooperates, and oil sucting cavity and oil-discharging cavity are kept apart by pocketed oil chamber, so oil sucting cavity and oil extraction
Chamber does not connects.When driving gear 1 and the full tooth of driven gear 3 engage, the end face alignment of driving gear 1 and driven gear 3,
Arcwall face 5 on cylindrical slide 4 coordinates with coordinating cylinder 9；Driven gear 3 move axially and with the gear teeth of driving gear 1
When being partially engaged with, the tooth top of driving gear 1 coordinates with the arcwall face 5 on cylindrical slide 4, as the preferred mode of one,
Described compensating groove 6 can be set on arcwall face 5, in gear type variable rate pump operation process, when pocketed oil chamber 2 rotates to off-load
Time at groove 6, compensating groove 6 connects with pocketed oil chamber 2, and when pocketed oil chamber 2 volume increases, fluid enters into pocketed oil chamber from compensating groove 6
In 2, reduce the cavitation corrosion in pocketed oil chamber 2 and cavitation phenomenon；When pocketed oil chamber 2 volume reduces, fluid enters into from pocketed oil chamber 2
In compensating groove 6, reduce the pressure in pocketed oil chamber 2.The shell of gear type variable rate pump is additionally provided with inlet port (figure does not shows
Go out) and oil drain out (not shown), fluid is sucked by gear type variable rate pump from inlet port, fluid after supercharging from oil extraction
Mouthful discharge, can arrange above-mentioned along cylindrical slide 4 between driving gear 1 and the line of centres of driven gear 3 and oil drain out
Axially extended compensating groove 6, so, when pocketed oil chamber 2 at the line of centres of driving gear 1 and driven gear 3 to oil drain out
During rotation, pocketed oil chamber 2 volume reduces, and fluid enters compensating groove 6 from pocketed oil chamber 2, reduces the pressure in pocketed oil chamber 2.
Gear type variable rate pump of the present utility model is commonly used as the lubricating oil pump of electromotor, and the lubricating system for electromotor provides machine oil,
Now, gear type variable rate pump is driven by the bent axle of electromotor, and when engine speed is the highest, the rotating speed of gear type variable rate pump is the highest,
Pocketed oil chamber 2 volume change the fastest, when pocketed oil chamber 2 volume increase the fastest time, cavitation corrosion and cavitation phenomenon are the most serious；
When pocketed oil chamber 2 volume reduce the fastest time, the pressure in pocketed oil chamber 2 is the biggest.When engine speed is the highest, pocketed oil chamber 2
When volume change is the fastest, fluid is required to flow between pocketed oil chamber 2 and compensating groove 6, so just requiring off-load the most rapidly
Through-flow open area between groove 6 and pocketed oil chamber 2 is the biggest, so, and fluid can quickly flow between pocketed oil chamber 2 and compensating groove 6
Dynamic, pocketed oil phenomenon could be eased goodly.When the rotating speed of electromotor increases, in order to make the oil drain out of gear type variable rate pump
The oil liquid pressure of output adapts with the lubricating system desirable pressure of electromotor, and the driven gear 3 of gear type variable rate pump can axially move
Move and make the engaging width between driving gear 1 and driven gear 3 reduce and turn discharge capacity so that change is every.For these reasons, in order to
The rotating speed making the through-flow open area between compensating groove 6 and pocketed oil chamber 2 and electromotor adapts and preferably alleviates pocketed oil phenomenon, as
Shown in Fig. 3 and Fig. 5, it is perpendicular to the cross section 7 that compensating groove 6 cross section is compensating groove of cylindrical slide 4 axis, the horizontal stroke of compensating groove
Cross section 7 is gradually increased to the other end from the one end near driven gear 3 end face.So, engine speed increase time, along with from
The distance that moving gear 3 moves axially increases, and cross section 7 area of the compensating groove of driving gear 1 end is the biggest, i.e. off-load
Through-flow open area between groove 6 and pocketed oil chamber 2 is the biggest.
Already described above, the driven gear 3 of gear type variable rate pump of the present utility model can move axially and make driving gear
1 changes with the engaging width of driven gear 3, thus reaches to become the purpose of discharge capacity.During driven gear 3 moves axially,
In order to make compensating groove 6 can connect with pocketed oil chamber 2, the axial length of compensating groove 6 should more than or equal to driving gear 1 with from
The maximum engagement width of moving gear 3 and the difference of minimum engaging width, so, driven gear 3 engages arbitrary with driving gear 1
Position, compensating groove 6 can connect with pocketed oil chamber 2 in the end of driving gear.Pocketed oil chamber 2 is always formed at driving gear
1 and driven gear 3 the line of centres near, compensating groove 6 should also be as being arranged on the center of driving gear 1 and driven gear 3 even
Near line, compensating groove 6 is wanted suitably relative to the position of driving gear 1 and driven gear 3 line of centres, in case inlet port and row
Hydraulic fluid port is connected by pocketed oil chamber 2 and compensating groove 6.Compensating groove can connect with oil sucting cavity or oil-discharging cavity individually, but compensating groove
Can not connect with oil sucting cavity or pocketed oil chamber simultaneously.Preferably, as it is shown in figure 5, driving gear 1 and the center of driven gear 3
Between the cross section 7 of line and described compensating groove, minimum range is Bd, formula below determine:
In formula, t0For the gear base pitch of driving gear 1 and driven gear 3, m is driving gear 1 and the gear of driven gear 3
Modulus；For driving gear 1 and the angle of engagement of driven gear 3；For driving gear 1 and the pressure angle of driven gear 3, on
Stating parameter and be driving gear 1 and the design parameter of driven gear 3, those skilled in the art can be according to driving gear 1 and driven
Self character and the two installation relation of gear 3 directly determine.As it is shown in figure 5, at a kind of gear type variable of the present utility model
In the embodiment of pump, the cross section 7 of compensating groove connects with oil-discharging cavity (not shown).
In gear type variable rate pump operation process, compensating groove 6 is wanted to connect with pocketed oil chamber 2, in actual design, and off-load
Cross section 7 shape of groove is the most unrestricted, as long as can connect with pocketed oil chamber 2 in gear type variable rate pump operation process, makees
For a kind of preferred embodiment, as shown in Figure 3 and Figure 5, the cross section 7 of compensating groove is one section of tooth top along driving gear 1
Circle extend circular section, circular section between two sections of anisodiametric isocentric circular arc, described two sections anisodiametric
Isocentric circular arc is all with the center of driving gear 1 as the center of circle, and the circular arc that wherein diameter is less overlaps with the outside circle of driving gear 1,
So, in gear pump with variable capacity operation process, when pocketed oil chamber 2 rotates to compensating groove 6, pocketed oil chamber 2 is positioned at driving tooth
Take turns the part at 1 tooth top necessarily to connect with compensating groove 6.Compensating groove 6 need enough length can make pocketed oil chamber 2 with
Compensating groove 6 can connect before pocketed oil chamber 2 is opened constantly, as it is shown on figure 3, at gear type variable rate pump of the present utility model
In, the two ends of the circular section of compensating groove 6 are 25 ° with the line angle theta at driving gear 1 center, i.e. surround compensating groove 6
The central angle θ of two sections of isocentric circular arc be 25 °.The size of the cross section 7 of compensating groove determines fluid at compensating groove 6 and pocketed oil
Between chamber 2 can smooth outflow, so also needing to the cross section 7 for compensating groove to determine rational width, the cross section of compensating groove
The cross section 7 of the i.e. compensating groove of 7 width along driving gear 1 size d radially, preferred at gear type variable rate pump of the present utility model
In embodiment, the cross section 7 of compensating groove is 1～2mm along size d of driving gear 1 radial direction.
In order to make the cross section 7 of compensating groove be gradually increased to the other end from the one end near driven gear 3 end face, as shown in Figure 6,
In compensating groove 6, the longitudinal section 8 that compensating groove 6 cross section is compensating groove of the dead in line with driving gear 1, can be by off-load
The longitudinal section 8 of groove is arranged to the trapezoidal shape shown in Fig. 6, it is also possible to be that triangle equal in width such as gradually increases to the other end from one end
Big shape, as long as can make the cross section 7 of compensating groove be gradually increased i.e. to the other end from the one end near driven gear 3 end face
Can.Certainly, need not to make the through-flow open area between compensating groove 6 and pocketed oil chamber 2 and the rotating speed of flourishing machine to adapt and more preferable
In the case of pocketed oil phenomenon is alleviated on ground, the longitudinal section 8 of compensating groove can be arranged to the cross section 7 of rectangle, i.e. compensating groove in cylindricality
The axial direction of slide block keeps constant.
Technical scheme based on above-described embodiment, a kind of gear type variable rate pump of the present utility model, by gear type variable rate pump
Being provided with axially extended compensating groove 6 on cylindrical slide 4, during driven gear 3 moves axially, compensating groove 6 can
Connect with pocketed oil chamber 2, thus reduce the pressure fluctuation in pocketed oil chamber 2, reduce the cavitation corrosion in pocketed oil chamber 2 and cavitation phenomenon.And,
The cross section 7 of compensating groove is gradually increased to the other end from the one end near driven gear 3 end face, when engine speed increases,
Through-flow open area between compensating groove 6 and pocketed oil chamber 2 also increases such that it is able to preferably alleviate pocketed oil phenomenon.
Above-described embodiment only illustrative principle of the present utility model and effect thereof, not for limiting this utility model.Any
Above-described embodiment all can be modified under spirit and the scope of the present utility model or change by those skilled in the art.
Therefore, such as art has usually intellectual without departing from the spirit disclosed in this utility model with under technological thought
All equivalences completed are modified or change, and must be contained by claim of the present utility model.
Claims (10)
1. a gear type variable rate pump, the driving gear (1) including shell, being located in shell inner cavity and driven gear (3), actively
Gear (1) and driven gear (3) are meshed and form pocketed oil chamber (2), are additionally provided with a cylindrical slide (4) in shell inner cavity,
Cylindrical slide (4) is coaxially connected with driven gear (3) and can move axially together with driven gear (3), it is characterized in that:
Being provided with along cylindrical slide (4) axially extended compensating groove (6) on cylindrical slide (4), one end of compensating groove (6) is prolonged
Extend the end face of driven gear (3) and can connect with described pocketed oil chamber (2).
2. gear type variable rate pump as claimed in claim 1, is characterized in that:
Cylindrical slide (4) is provided with one section of arcwall face (5) matched with the outside circle of driving gear (1), in arcwall face (5)
On be provided with described compensating groove (6).
3. gear type variable rate pump as claimed in claim 1, is characterized in that:
Shell is provided with inlet port and oil drain out, and described compensating groove (6) is arranged on driving gear (1) and driven gear (3)
Between the line of centres and oil drain out.
4. gear type variable rate pump as claimed in claim 1, is characterized in that:
It is perpendicular to the cross section (7) that compensating groove (6) cross section is compensating groove of cylindrical slide (4) axis, the cross section (7) of compensating groove
It is gradually increased to the other end from the one end near driven gear (3) end face.
5. gear type variable rate pump as claimed in claim 1, is characterized in that:
The axial length of compensating groove (6) more than or equal to driving gear (1) and driven gear (3) maximum engagement width with
The difference of minimum engaging width.
6. gear type variable rate pump as claimed in claim 1, is characterized in that:
Be perpendicular to the cross section (7) that compensating groove (6) cross section is compensating groove of cylindrical slide (4) axis, driving gear (1) and
Between the line of centres and the cross section (7) of described compensating groove of driven gear (3), minimum range is Bd, formula below determine:
In formula, m is driving gear (1) and the modulus of driven gear (3)；For driving gear (1) and driven gear (3)
The angle of engagement；For driving gear (1) and the pressure angle of driven gear (3).
7. gear type variable rate pump as claimed in claim 1, is characterized in that:
The longitudinal section (8) that compensating groove (6) cross section is compensating groove of the dead in line with driving gear (1), the vertical of compensating groove cuts
Face (8) is rectangular/trapezoidal/triangle.
8. gear type variable rate pump as claimed in claim 1, is characterized in that:
It is perpendicular to the cross section (7) that compensating groove (6) cross section is compensating groove of cylindrical slide (4) axis, the cross section of compensating groove
(7) it is one section of circular section along the outside circle extension of driving gear (1).
9. gear type variable rate pump as claimed in claim 8, is characterized in that:
The two ends of described circular section are 25 ° with the line angle at driving gear (1) center.
10. gear type variable rate pump as claimed in claim 8, is characterized in that:
The cross section (7) of compensating groove is 1～2mm along the size of driving gear (1) radial direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620290160.9U CN205534993U (en) | 2016-04-08 | 2016-04-08 | Gear formula variable pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620290160.9U CN205534993U (en) | 2016-04-08 | 2016-04-08 | Gear formula variable pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205534993U true CN205534993U (en) | 2016-08-31 |
Family
ID=56790600
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620290160.9U Active CN205534993U (en) | 2016-04-08 | 2016-04-08 | Gear formula variable pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205534993U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105697970A (en) * | 2016-04-08 | 2016-06-22 | 上海幸福摩托车有限公司 | Gear-type variable pump |
| CN107355664A (en) * | 2017-07-24 | 2017-11-17 | 中国第汽车股份有限公司 | A kind of rotor-type oil pump that can reduce charge oil pressure fluctuation intensity and flow noise |
-
2016
- 2016-04-08 CN CN201620290160.9U patent/CN205534993U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105697970A (en) * | 2016-04-08 | 2016-06-22 | 上海幸福摩托车有限公司 | Gear-type variable pump |
| CN107355664A (en) * | 2017-07-24 | 2017-11-17 | 中国第汽车股份有限公司 | A kind of rotor-type oil pump that can reduce charge oil pressure fluctuation intensity and flow noise |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN205534993U (en) | Gear formula variable pump | |
| CN105697970A (en) | Gear-type variable pump | |
| CN203532246U (en) | High-low pressure duplicate gear pump | |
| CN204738961U (en) | Variable type gear pump | |
| CN104121189B (en) | Double-action stepless speed variator oil pump | |
| CN203081678U (en) | Crystallization-preventing ceramic pump | |
| CN203516093U (en) | Pressure and flow control valve of steering oil pump | |
| CN207526683U (en) | A kind of novel gear type variable oil pump | |
| CN201884915U (en) | Engine oil pump with double oil outlets | |
| CN204663871U (en) | A kind of gear fuel supply pump | |
| CN204061164U (en) | Double-action stepless speed variator oil pump | |
| CN206738145U (en) | A kind of gear pump used suitable for the whole network distribution transmission ＆ distribution heating system | |
| CN205014001U (en) | Oil gas lubricating system of pulsed oiling | |
| CN205714738U (en) | There is the cycloid rotor pump of non-smooth surface | |
| CN205190097U (en) | Diesel engine fuel injection device | |
| CN105275805B (en) | A kind of oil injection type double-screw compressor | |
| CN206845357U (en) | A kind of diesel engine flow regulator | |
| CN206130140U (en) | Blast gate baffle | |
| CN202811152U (en) | Powder metallurgy adjusting gear sleeve for injection pump of B45-6 diesel engine fuel | |
| CN104776020B (en) | A kind of gear fuel supply pump | |
| CN202531327U (en) | Fuel injection pump plunger | |
| CN203430773U (en) | Pump body of gear pump | |
| CN203783889U (en) | Adjustable liquid medium conveying screw pump | |
| CN203585786U (en) | Rotor oil pump | |
| CN209649529U (en) | A kind of integrated molding hydraulic press |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190326 Address after: Building No. 18, 998 Tongji Road, Baoshan District, Shanghai, 20199 Patentee after: Huayu Pilberg Pump Technology Co., Ltd. Address before: 1999 No. 998 Tongji Road, Baoshan District, Shanghai Patentee before: Shanghai Xingfu Motorcycle Co., Ltd. |
|
| TR01 | Transfer of patent right |