CN106762612A - A kind of high-pressure spiral gear pump with gapless external toothing tooth form - Google Patents
A kind of high-pressure spiral gear pump with gapless external toothing tooth form Download PDFInfo
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- CN106762612A CN106762612A CN201710015789.1A CN201710015789A CN106762612A CN 106762612 A CN106762612 A CN 106762612A CN 201710015789 A CN201710015789 A CN 201710015789A CN 106762612 A CN106762612 A CN 106762612A
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- Prior art keywords
- driven
- gear
- axle journal
- tooth
- helical gear
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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
- F04C2/18—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 similar tooth forms
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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
- F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
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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
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Gears, Cams (AREA)
- Rotary Pumps (AREA)
- Gear Transmission (AREA)
Abstract
The invention discloses a kind of high-pressure spiral gear pump with gapless external toothing tooth form, mainly it is made up of driving gear shaft, driven gear shaft, the pump housing, bearing assembly, front cover component and rear case component.Driving and driven gear shaft helical gear contrate tooth profile is identical, and each tooth is made up of addendum circle arc, involute, tooth root circular arc.In engagement process, due to tooth top and tooth root be circular arc, using helical tooth, master and slave helical gear is at a fully engaged, in the absence of the closing space of volume change, tight mesh is realized, be inherently eliminated pocketed oil phenomenon, therefore stable working, noise is low, pulse free, and efficiency high, long service life.All adjacent curves are tangent in junction in screw serrated form, when form milling or plunge grinding are processed, tool bit life.Maximum working pressure of the invention is up to 32MPa, and noise is less than 60dBA, is particularly well-suited to the occasion for having strict demand to noise.
Description
Technical field
The invention belongs to gear-type hydraulic pump technical field, it is related to a kind of high-pressure pump, more specifically, it relates to a kind of tool
There is the high-pressure spiral gear pump of gapless external toothing tooth form.
Background technology
External gear-type hydraulic pump common in the market all uses evolvent type straight-tooth gear, because involute is straight
Bottom clearance and bottom gap are there is in gear, in engagement process, volume is there is always between intermeshing tooth top and tooth root
The closing space of change, forms pocketed oil phenomenon, therefore shock loading can be produced in operation process, increases power loss, and draw
Vibration and noise, flow and pressure fluctuation are played, the stationarity and service life of work is reduced, and these are for hydraulic system
It is very unfavorable.
The content of the invention
It is a primary object of the present invention to regarding to the issue above, there is provided a kind of high pressure with gapless external toothing tooth form
Helical gear pump.
A kind of high-pressure spiral gear pump with gapless external toothing tooth form, including driving gear shaft 1, driven gear shaft 2,
The pump housing 3, bearing assembly 4, front cover component 5 and rear case component 6；Hollow knot of the section just as 8 word holes is provided with the cavity of the pump housing 3
Structure, for installing driving gear shaft 1, driven gear shaft 2 and bearing assembly 4, one end connection front cover component 5 of the pump housing 3, the other end
Connection rear case component 6；The side of the pump housing 3 is provided with snout cavity 31, opposite side and is provided with outlet plenum 32.
The driving gear shaft 1 is provided with active helical gear 11, and the driven gear shaft 2 is provided with driven helical gear
21, the active helical gear 11 is dextrorotation, and the driven helical gear 21 is left-handed, both diameter parallels arrangement, Liang Zhezhuan
Dynamic in opposite direction, intermeshing, both contrate tooth profiles are identical, and the contrate tooth profile curve of each tooth is by addendum circle arc aa', gradually open
Line ab and a'b', tooth root circular arc bc and b'c' composition, each section of curve are tangent connection, are formed and nibbled outside gapless in junction
Tooth form is closed, involute ab and a'b' transmit torque in engagement process.
When using, transported medium enters from snout cavity 31, by active helical gear 11, the tooth of driven helical gear 21
The confined space that groove is formed with 8 word holes of the pump housing 3 is transported to outlet plenum 32.
The technical scheme for further limiting is as follows：
The outside circle da of the active helical gear 11 and the contrate tooth profile of driven helical gear 21, root circle df, reference circle dj with
And the basic circle db of involute is concentric circles in tooth form, and addendum circle arc radius and fillet radius are equal, are ro。
The contrate tooth profile of the active helical gear 11 and driven helical gear 21 is uniformly distributed along the circumference by Z tooth, preferential choosing
It is 5~19 with tooth number Z；The end face overlap coefficient of the contrate tooth profile is εα=0.5, axially coincident coefficient is εβ=1.0, it is total to overlap
Coefficient 1.5.
The active helical gear 11 is equal with the facewidth B of driven helical gear 21, and helical pitch T is also equal, and helical pitch T etc.
Tooth number Z, i.e. T=B × Z are multiplied by facewidth B.
The structure of the driving gear shaft 1 includes active helical gear 11, actively the first axle journal 12, actively the second axle journal 13
With spindle nose 14；The active helical gear 11, actively the first axle journal 12, actively the second axle journal 13, spindle nose 14 are concentric shafts；Actively
First axle journal 12 and actively the second axle journal 13 is located at the both sides of active helical gear 11, for coordinating with bearing assembly 4, actively the
One axle journal 12 and the actively equal diameters of the second axle journal 13；The spindle nose 14 is connected with actively the first axle journal 12, on spindle nose 14
Keyway 141 is provided with, for being connected with prime mover.
The structure of the driven gear shaft 2 includes driven helical gear 21, driven first axle journal 22 and driven second axle journal
23；The driven helical gear 21, driven first axle journal 22 and driven second axle journal 23 are concentric shafts；The driven He of first axle journal 22
Driven second axle journal 23 is located at the both sides of driven helical gear 21, for coordinating with bearing assembly 4；Driven first axle journal 22 and from
The equal diameters of dynamic second axle journal 23.
The first axle journal of the active 12, actively the second axle journal 13, driven first axle journal 22, driven second axle journal 23 coordinate
Sliding bearing 42 is installed, axle sleeve 41 is provided between the sliding bearing 42 and the pump housing 3.
The rear case component 6 includes bonnet 61, alignment pin 62, driving gear balance weight 63, driven gear balance weight 64, close
Seal 65 and rear cover screw 66；The structure of the bonnet 61 include two pin-and-holes, 611, eight mounting holes 612, high pressure oilhole 613,
Driving gear balance pipe 614, driven gear balance pipe 615, trapezoidal oil-way 616, seal groove 617；The driving gear
The correspondence driving gear shaft 1 of balance pipe 614, hole is built with driving gear balance weight 63；The driven gear balance pipe 615 correspondence from
Movable gear shaft 2, hole is built with driven gear balance weight 64；Described high pressure oilhole 613 is by driving gear balance pipe 614 and driven
Gear balance pipe 615 is connected with the outlet plenum 32 of pump；Trapezoidal oil-way 616 connects the snout cavity 31 of pump.
The driving gear balance weight 63 is acted on the afterbody for promoting driving gear shaft 1 then by the hydraulic oil of outlet plenum 32
Axial force on balance driving gear shaft 1；The driven gear balance weight 64 be subject to the hydraulic oil of outlet plenum 32 effect promote from
The afterbody of movable gear shaft 2 axial force then on balance driven gear axle 2.
Advantageous Effects of the invention embody in the following areas：
（1）The present invention eliminates pocketed oil phenomenon, tooth top and tooth root tight mesh from tooth form this basic factor first, it is to avoid
The annular seal space of volume change is produced between tooth top and tooth root, and all adjacent curves of tooth form are tangent in junction, therefore
Principal and subordinate's gear stable working in engagement process, noise is low, pulse free, it is ensured that keep the volume of stabilization to imitate in working life
Rate, long service life.
（2）Maximum working pressure of the invention is up to 32MPa, and noise is less than 60dBA, is particularly well-suited to have noise
The occasion of strict demand.
（3）The all adjacent curves of whole tooth form of helical gear are tangent in junction, in driving and driven helical gear type face
Process in, significantly improve form cutter or the wearability of abrasive grinding wheel, service life extension.
Brief description of the drawings
Fig. 1 is schematic structural view of the invention.
Fig. 2 is structural profile schematic diagram of the present invention.
Fig. 3 is the A-A sectional views of Fig. 2 of the present invention.
Based on Fig. 4, driven helical gear axle mesh schematic representation.
Fig. 5 is single tooth form schematic diagram of the invention.
Fig. 6 is the engagement process schematic diagram of driving and driven helical gear of the invention.
Fig. 7 driving and driven helical gear contrate tooth profile engagement comparison diagrams when being the different numbers of teeth.
Fig. 8 is rear cover structure schematic diagram of the present invention.
Fig. 9 is conventional involute spur gear mesh schematic representation.
Sequence number in upper figure：
Driving gear shaft 1, actively active helical gear 11, the first monodentate 111, actively the second monodentate 112, actively the first axle journal
12nd, the second axle journal 13 of active, spindle nose 14, keyway 141；
Driven gear shaft 2, driven helical gear 21, driven first monodentate 211, driven second monodentate 212, driven first axle journal
22nd, driven second axle journal 23；
The pump housing 3, snout cavity 31, outlet plenum 32；
Bearing assembly 4, axle sleeve 41, sliding bearing 42；
Front cover component 5；
Rear case component 6, bonnet 61, pin-and-hole 611, mounting hole 612, high pressure oilhole 613, driving gear balance pipe 614, driven gear
Balance pipe 615, trapezoidal oil-way 616, seal groove 617, alignment pin 62, driving gear balance weight 63, driven gear balance
Block 64, sealing ring 65, rear cover screw 66；
Active spur gear 7, driven spur gear 8.
Specific embodiment
Below in conjunction with the accompanying drawings, the present invention is further described by embodiment.
Embodiment
Referring to Fig. 9, existing external gear-type hydraulic pump all uses evolvent type straight-tooth gear, in the He of active spur gear 7
During driven spur gear 8 is engaged, a closing space K can be therebetween formed, closing space K volume sizes are with straight
The rotation of gear changes, and because the hydraulic oil for conveying has Incoercibility, forms pocketed oil phenomenon, therefore the closing space
The change of K volumes can produce shock loading, increase power loss, and cause vibration and noise, flow and pressure fluctuation, reduce
The stationarity and service life of work, and these are very unfavorable for hydraulic system.
Referring to Fig. 1~Fig. 5, a kind of high-pressure spiral gear pump with gapless external toothing tooth form, mainly by driving gear
Axle 1, driven gear shaft 2, the pump housing 3, bearing assembly 4, front cover component 5 and rear case component 6 are constituted.Section is provided with the cavity of the pump housing 3
Just as the hollow structure in 8 word holes, for installing active helical gear shaft 1, driven helical gear axle 2 and bearing assembly 4, the pump housing 3
One end connection front cover component 5, the other end connection rear case component 6；The side of the pump housing 3 is provided with snout cavity 31, opposite side and is provided with out
Oral cavity 32.
The structure of the driving gear shaft 1 includes active helical gear 11, actively the first axle journal 12, actively the second axle journal 13
With spindle nose 14；The active helical gear 11, actively the first axle journal 12, actively the second axle journal 13, spindle nose 14 are concentric shafts；Actively
First axle journal 12 and actively the second axle journal 13 is located at the both sides of active helical gear 11, for coordinating with bearing assembly 4, actively the
One axle journal 12 and the actively equal diameters of the second axle journal 13；The spindle nose 14 is connected with actively the first axle journal 12, on spindle nose 14
Keyway 141 is provided with, for being connected with prime mover.
The structure of the driven gear shaft 2 includes driven helical gear 21, driven first axle journal 22 and driven second axle journal
23；The driven helical gear 21, driven first axle journal 22 and driven second axle journal 23 are concentric shafts；The driven He of first axle journal 22
Driven second axle journal 23 is located at the both sides of driven helical gear 21, for coordinating with bearing assembly 4；Driven first axle journal 22 and from
The equal diameters of dynamic second axle journal 23.
The first axle journal of the active 12, actively the second axle journal 13, driven first axle journal 22, driven second axle journal 23 coordinate
Sliding bearing 42 is installed, axle sleeve 41 is provided between the sliding bearing 42 and the pump housing 3.
The active helical gear 11 is dextrorotation, and the driven helical gear 21 is left-handed, both diameter parallels arrangement, two
Person's rotation direction is conversely, tight mesh, constitutes the screw pair of parallel axes external toothing, formation conjugate relation.
Referring to Fig. 8, the rear case component 6 includes that bonnet 61, alignment pin 62, driving gear balance weight 63, driven gear are put down
Weighing apparatus block 64, sealing ring 65 and rear cover screw 66；The structure of the bonnet 61 includes two pin-and-holes, 611, eight mounting holes 612, height
Force feed hole 613, driving gear balance pipe 614, driven gear balance pipe 615, trapezoidal oil-way 616, seal groove 617；Institute
The correspondence driving gear shaft 1 of driving gear balance pipe 614 is stated, hole is built with driving gear balance weight 63；The driven gear balance
The correspondence driven gear shaft 2 of hole 615, hole is built with driven gear balance weight 64；Described high pressure oilhole 613 balances driving gear
Hole 614 and driven gear balance pipe 615 are connected with the outlet plenum 32 of pump；Trapezoidal oil-way 616 connects the snout cavity 31 of pump.
The driving gear balance weight 63 is acted on the afterbody for promoting driving gear shaft 1 then by the hydraulic oil of outlet plenum 32
Axial force on balance driving gear shaft 1；The driven gear balance weight 64 be subject to the hydraulic oil of outlet plenum 32 effect promote from
The afterbody of movable gear shaft 2 axial force then on balance driven gear axle 2.
Trapezoidal oil-way 616 lubricates for storing hydraulic oil to sliding bearing 42；Seal groove 617 is used to install rubber
Sealing ring, plays sealing function.
Referring to Fig. 5, single tooth form schematic diagram of the invention is shown.Active helical gear 11 and the end face of driven helical gear 21
The outside circle da of tooth form, root circle df, reference circle dj and the basic circle db of involute is concentric circles in tooth form, and addendum circle arc half
Footpath and fillet radius are equal, are ro.Active helical gear 11 is identical with the contrate tooth profile of driven helical gear 21, all by
Z tooth is circumferentially uniformly distributed, and single tooth form is connected by following five sections of curves and formed on vertical axis：
c'b'：Tooth root circular arc； b'a'：Involute； a'a：Addendum circle arc； ab：Involute； bc：Tooth root circular arc；
Above-mentioned each section of curve is tangent in junction.In engagement process, addendum circle arc and tooth root circular arc gapless in tooth form
Engagement；Involute conjugate curves each other in tooth form, play a part of to transmit torque, active helical gear 11 transmit torque to from
On dynamic helical gear 21, so as to drive driven helical gear 21 to rotate together.The end face overlap coefficient of the contrate tooth profile is εα=
0.5, axially coincident coefficient is εβ=1.0, total overlap coefficient 1.5.The active helical gear 11, the tooth of driven helical gear 21
B wide is equal, and helical pitch T is also equal, and helical pitch T is multiplied by tooth number Z, i.e. T=B × Z equal to facewidth B.
Referring to Fig. 6（a）, Fig. 6（b）And Fig. 6（c）, it show the engagement process figure of master and slave screw serrated form of the invention.Actively
Helical gear 11 turns clockwise, the rotate counterclockwise of driven helical gear 21, in Fig. 6（a）State when, active helical gear 11
The first monodentate of active 111 and actively the tooth root circular arc between the second monodentate 112 just with driven the of driven helical gear 21
The addendum circle arc of one monodentate 211 coincides, and realizes tight mesh；Master and slave helical gear is further rotated to Fig. 6（b）State, it is main
Tooth root circular arc and driven helical gear 21 between first monodentate of active 111 of dynamic helical gear 11 and actively the second monodentate 112
The driven addendum circle arc of first monodentate 211 disengage, the involute of second monodentate of active 112 of active helical gear 11 promote from
The involute of driven first monodentate 211 of dynamic helical gear 21 is rotated, and both are mutually conjugated involute；When active helical gear 11
The involute of the second monodentate of active 112 complete engagement when, be exactly in Fig. 6（c）State, the active second of active helical gear 11
The addendum circle arc of monodentate 112 is just and driven first monodentate 211 and driven second monodentate 212 of driven helical gear 21 between
Tooth root circular arc coincides, and realizes tight mesh；So master and slave helical gear contrate tooth profile completes one group of engagement of monodentate,
Due to being screw serrated form, the engagement process is also constantly realized repeating, so as to ensure the continuity of master and slave helical gear engagement.
The engagement process smooth-going of master and slave screw serrated form, does not exist closing space between tooth top and tooth root, realize tight mesh, so
Pocketed oil phenomenon, therefore stable working are inherently eliminated, noise is low, pulse free, and efficiency high, long service life.In addition,
Because all adjacent curves of whole tooth form are tangent in junction, therefore in process, form cutter or abrasive grinding wheel
Wearability is significantly improved, service life extension.
Referring to Fig. 7（a）, Fig. 7（b）, Fig. 7（c）, under the conditions of identical basic circle db and reference circle dj, tooth number Z is respectively equal to 7,
Helical gear contrate tooth profile engagement comparison diagram when 8 and 9.The tooth form of helical gear is uniformly distributed along the circumference by Z tooth in the present invention, theoretical
Upper tooth number Z can be 2 to infinite multiple, and tooth number Z of preferentially selecting in actual applications is 5 ~ 19.In actual engineer applied
In, the number of teeth can be chosen according to different operating modes.In the case where reference circle, involute basic circle, the facewidth and rotating speed are fixed, the number of teeth is got over
Many, the annular seal space of formation is more, and boost in pressure performance is also stronger；The number of teeth is fewer, and cavity volume is bigger, and the volume for discharging fluid is got over
It is many.
When using, referring to Fig. 3, driving gear shaft 1 and driven gear shaft 2 continuously engage operating, transported medium
Enter from snout cavity 31, by 8 word holes of active helical gear 11, the teeth groove of driven helical gear 21 and the pump housing 3 formed it is close
Close space and be transported to outlet plenum 32.
Above content not makees any formal limitation to structure of the invention, shape.It is every according to skill of the invention
Any simple modification, equivalent variations and modification that art is substantially made to above example, still fall within technical solution of the present invention
In the range of.
Claims (9)
1. a kind of high-pressure spiral gear pump with gapless external toothing tooth form, including driving gear shaft（1）, driven gear shaft
（2）, the pump housing（3）, bearing assembly（4）, front cover component（5）And rear case component（6）；The pump housing（3）Section shape is provided with cavity
With the hollow structure in 8 word holes, for installing driving gear shaft（1）, driven gear shaft（2）And bearing assembly（4）, the pump housing（3）'s
One end connects front cover component（5）, other end connection rear case component（6）；The pump housing（3）Side be provided with snout cavity（31）, opposite side
It is provided with outlet plenum（32）；It is characterized in that：
The driving gear shaft（1）It is provided with active helical gear（11）, the driven gear shaft（2）It is provided with driven helical tooth
Wheel（21）, the active helical gear（11）It is dextrorotation, the driven helical gear（21）It is left-handed, both diameter parallel cloth
Put, both rotation directions are conversely, be intermeshed, both contrate tooth profiles are identical, and the contrate tooth profile curve of each tooth is by outside circle
Arc aa', involute ab and a'b', tooth root circular arc bc and b'c' composition, each section of curve are tangent connection, are formed in junction
Gapless external toothing tooth form, involute ab and a'b' transmit torque in engagement process；
When using, transported medium is from snout cavity（31）Into by active helical gear（11）, driven helical gear（21）'s
Teeth groove and the pump housing（3）8 word holes formed confined space be transported to outlet plenum（32）.
2. a kind of high-pressure spiral gear pump with gapless external toothing tooth form according to claim 1, it is characterised in that：
The active helical gear（11）And driven helical gear（21）The outside circle da of contrate tooth profile, root circle df, reference circle dj with
And the basic circle db of involute is concentric circles in tooth form, and addendum circle arc radius and fillet radius are equal, are ro。
3. a kind of high-pressure spiral gear pump with gapless external toothing tooth form according to claim 1, it is characterised in that：
The active helical gear（11）And driven helical gear（21）Contrate tooth profile be uniformly distributed along the circumference by Z tooth, preferentially from tooth
Number Z is 5~19；The end face overlap coefficient of the contrate tooth profile is εα=0.5, axially coincident coefficient is εβ=1.0, total overlap coefficient
1.5。
4. a kind of high-pressure spiral gear pump with gapless external toothing tooth form according to claim 1, it is characterised in that：
The active helical gear（11）And driven helical gear（21）Facewidth B it is equal, helical pitch T is also equal, and helical pitch T be equal to tooth
B wide is multiplied by tooth number Z, i.e. T=B × Z.
5. a kind of high-pressure spiral gear pump with gapless external toothing tooth form according to claim 1, it is characterised in that：
The driving gear shaft（1）Structure include active helical gear（11）, actively the first axle journal（12）, actively the second axle journal（13）
And spindle nose（14）；The active helical gear（11）, actively the first axle journal（12）, actively the second axle journal（13）, spindle nose（14）For
Concentric shafts；Actively the first axle journal（12）With actively the second axle journal（13）Positioned at active helical gear（11）Both sides, for and axle
Bearing assembly（4）Coordinate, actively the first axle journal（12）With actively the second axle journal（13）Equal diameters；The spindle nose（14）And actively
First axle journal（12）It is connected, spindle nose（14）It is provided with keyway（141）, for being connected with prime mover.
6. a kind of high-pressure spiral gear pump with gapless external toothing tooth form according to claim 1, it is characterised in that：
The driven gear shaft（2）Structure include driven helical gear（21）, driven first axle journal（22）With driven second axle journal
（23）；The driven helical gear（21）, driven first axle journal（22）With driven second axle journal（23）It is concentric shafts；Driven first
Axle journal（22）With driven second axle journal（23）Positioned at driven helical gear（21）Both sides, for and bearing assembly（4）Coordinate；From
Dynamic first axle journal（22）With driven second axle journal（23）Equal diameters.
7. a kind of high-pressure spiral gear pump with gapless external toothing tooth form according to claim 5 or 6, its feature exists
In：The axle journal of the active first（12）, actively the second axle journal（13）, driven first axle journal（22）, driven second axle journal（23）
Cooperation is provided with sliding bearing（42）, the sliding bearing（42）With the pump housing（3）Between be provided with axle sleeve（41）.
8. a kind of high-pressure spiral gear pump with gapless external toothing tooth form according to claim 1, it is characterised in that：
The rear case component（6）Including bonnet（61）, alignment pin（62）, driving gear balance weight（63）, driven gear balance weight（64）、
Sealing ring（65）And rear cover screw（66）；The bonnet（61）Structure include two pin-and-holes（611）, eight mounting holes（612）、
High pressure oilhole（613）, driving gear balance pipe（614）, driven gear balance pipe（615）, trapezoidal oil-way（616）, sealing
Ring recess（617）；The driving gear balance pipe（614）Correspondence driving gear shaft（1）, hole is built with driving gear balance weight
（63）；The driven gear balance pipe（615）Correspondence driven gear shaft（2）, hole is built with driven gear balance weight（64）；It is described
High pressure oilhole（613）By driving gear balance pipe（614）With driven gear balance pipe（615）With the outlet plenum of pump（32）Even
It is logical；Trapezoidal oil-way（616）Connect the snout cavity of pump（31）.
9. a kind of high-pressure spiral gear pump with gapless external toothing tooth form according to claim 8, it is characterised in that：
The driving gear balance weight（63）By outlet plenum（32）The effect of hydraulic oil promotes driving gear shaft（1）Afterbody then put down
Weighing apparatus driving gear shaft（1）On axial force；The driven gear balance weight（64）By outlet plenum（32）The effect of hydraulic oil is pushed away
Dynamic driven gear shaft（2）Afterbody then balance driven gear axle（2）On axial force.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710015789.1A CN106762612A (en) | 2017-01-10 | 2017-01-10 | A kind of high-pressure spiral gear pump with gapless external toothing tooth form |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710015789.1A CN106762612A (en) | 2017-01-10 | 2017-01-10 | A kind of high-pressure spiral gear pump with gapless external toothing tooth form |
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| CN106762612A true CN106762612A (en) | 2017-05-31 |
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|---|---|---|---|
| CN201710015789.1A Pending CN106762612A (en) | 2017-01-10 | 2017-01-10 | A kind of high-pressure spiral gear pump with gapless external toothing tooth form |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108286517A (en) * | 2018-04-10 | 2018-07-17 | 山西平阳重工机械有限责任公司 | Coupling wheel spiral rotor pump |
| CN109505960A (en) * | 2019-01-23 | 2019-03-22 | 福建江夏学院 | A kind of low noise traveling pump of engineering machinery |
| US20190376557A1 (en) * | 2018-06-11 | 2019-12-12 | Eaton Intelligent Power Limited | Bi-metallic journal bearing with additive manufactured sleeve |
| CN110617213A (en) * | 2019-10-24 | 2019-12-27 | 山东大学 | Spiral tooth double-arc tooth-shaped hydraulic gear pump with dynamic and static pressure floating support at shaft end |
| RU195413U1 (en) * | 2019-09-18 | 2020-01-28 | Сергей Иванович Никитин | GEAR PUMP |
| CN115681147A (en) * | 2022-12-30 | 2023-02-03 | 江苏罗茨泵业科技有限公司 | Full-time leakage-free backflow-free lobe pump impeller structure and heat treatment process |
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| CN108286517A (en) * | 2018-04-10 | 2018-07-17 | 山西平阳重工机械有限责任公司 | Coupling wheel spiral rotor pump |
| US20190376557A1 (en) * | 2018-06-11 | 2019-12-12 | Eaton Intelligent Power Limited | Bi-metallic journal bearing with additive manufactured sleeve |
| US11060559B2 (en) * | 2018-06-11 | 2021-07-13 | Eaton Intelligent Power Limited | Bi-metallic journal bearing with additive manufactured sleeve |
| CN109505960A (en) * | 2019-01-23 | 2019-03-22 | 福建江夏学院 | A kind of low noise traveling pump of engineering machinery |
| RU195413U1 (en) * | 2019-09-18 | 2020-01-28 | Сергей Иванович Никитин | GEAR PUMP |
| CN110617213A (en) * | 2019-10-24 | 2019-12-27 | 山东大学 | Spiral tooth double-arc tooth-shaped hydraulic gear pump with dynamic and static pressure floating support at shaft end |
| CN110617213B (en) * | 2019-10-24 | 2021-06-04 | 山东大学 | Spiral tooth double-arc tooth-shaped hydraulic gear pump with dynamic and static pressure floating support at shaft end |
| CN115681147A (en) * | 2022-12-30 | 2023-02-03 | 江苏罗茨泵业科技有限公司 | Full-time leakage-free backflow-free lobe pump impeller structure and heat treatment process |
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Application publication date: 20170531 |