CN2118181U - Planetary gear pump - Google Patents
Planetary gear pump Download PDFInfo
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- CN2118181U CN2118181U CN 92215003 CN92215003U CN2118181U CN 2118181 U CN2118181 U CN 2118181U CN 92215003 CN92215003 CN 92215003 CN 92215003 U CN92215003 U CN 92215003U CN 2118181 U CN2118181 U CN 2118181U
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- gear
- voussoir
- planetary pinion
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Abstract
The utility model discloses a planetary gear pump in a hydraulic system. The center of the planetary gear pump is provided with a drive gear (11), a plurality of planetary gears (12) is arranged in a mode that the center positions of the planetary gears are fixed and symmetric, and the output of 2 NG is formed. The change of radial forces on the planetary gears is adjusted to be synchronous, and most radial forces are counteracted with each other. When the tooth number of the drive gear (11) equals to the integral multiple of N, the radial force on the drive gear equals to 0. Hydraulic balance exists on a wedge block (16), an internal gear (6) and a tile block bearing (8), and most radial forces on the parts are mutually counteracted. An assembly clearance can be kept easily. The output pressure of the pump is limited only by the torsion strength of a drive shaft and the mechanical strength of the tooth form of each gear.
Description
The utility model relates to the gear pump in a kind of hydraulic system, and this gear pump is an actuation gear by the center specifically, and the outer ring is an internal gear, is that planetary planetary gear train is formed between actuation gear and internal gear.
At known document " hydraulic pressure handbook " (Hyd raulic Handbook, P72～73, R.H.WARRING.Trade ﹠amp; Thcnical press Limited.1983.) 72 to 73 page, and (2) 240 pages of " mechanical engineering manual " supplementary copies, the internal gear pump that a crescent shape voussoir is arranged shown in (China Machine Press's version in 1988), can partial offset in the radial force of two gear center on line directions, but sucking and discharge radial force that two sides form by hydraulic pressure can't balance, and have an external gear pump of shunting side plate, part radial force on yet can only balance gear, other existing gear pumps still do not have significantly effectively balanced radial force measure.Concerning gear pump, the radial force that is formed by hydraulic pressure and driving force on the gear causes gear shaft bending deflection, and each gap increases volumetric efficiency and reduces; The very big easy wearing and tearing of the specific pressure of bearing, especially under high discharge pressure, above-mentioned shortcoming is just more outstanding, has placed restrictions on the further raising of the discharge pressure of existing gear pump.In addition aspect the gear meshing form, the gear pump that does not yet have interior outer gearing to combine.
The purpose of this utility model provides a kind of radial load influence that can overcome on the gear, thereby improves the gear pump of discharge pressure and flow significantly.
The purpose of this utility model is to solve like this: a kind of planetary gear pump, it comprises inside and outside gear, the segmental bearing of voussoir, side plate and supporting internal gear.It has an actuation gear at the center, internal gear is in the outer ring, the planetary gear train of planetary pinion between actuation gear and internal gear, wherein planetary pinion has the symmetric arrangement of its center fixed-site, planetary pinion is counted N 〉=2, N is a positive integer, each planetary pinion and internal gear and actuation gear form 2 engagement inlet ends on its sense of rotation, thereby planetary gear pump has 2N engagement inlet end, discharge capacity with 2Nq, the discharge capacity of each engagement inlet end of q-, any with the structure that enters the sealing arc of voussoir in a flash what stipulate with the sealing arc that leaves voussoir in a flash and this planetary tooth top edge by the tooth top edge that makes two engagement inlet ends on the planetary pinion, the variation that reaches the radial force on the planetary pinion is synchronous.Planetary pinion no matter its parameter and size has muchly, has only two kinds of fundamental types, and promptly the number of teeth is that the even numbers or the number of teeth are odd numbers.Also no matter the planetary number of teeth is even numbers or odd number, and at its interior end of engagement and outer gearing end, the making a concerted effort of radial force that is formed by hydraulic pressure and driving force, the fluctuation of the swing of their line of action direction and size must be adjusted to synchronously as stated above.Have only the synchronous variation of above-mentioned these power could offset most radial forces, make planetary pinion be in minimum stress.
When the number of teeth of actuation gear is that planetary pinion is when counting the integral multiple of N, because the symmetric arrangement of planetary pinion position.Radial hydraulic pressure that is subjected on the actuation gear and driving force are in radially component symmetry fully, and the fluctuation of their direction swing and amount is synchronous fully, thus they make a concerted effort to equal 0.Gear shaft only is subjected to torsional interaction, and this bearing does not have radial load in theory and only plays the role of positioning, and irrelevant with the size of the discharge pressure of pump.In this case, the discharge pressure of planetary gear pump only is subjected to the placing restrictions on of mechanical strength of the torsional strength of live axle and each form of gear tooth.When the number of teeth of actuation gear is not a planetary pinion when counting the integral multiple of N, the direction swing of the radial force on the actuation gear and the fluctuation of amount can not be synchronous, they make a concerted effort to be not equal to 0.But the variation of this resultant radial force is at (t
1'-b
1) in the PB scope, still far below the radial force of existing gear pump, t in the formula
1'-actuation gear tooth top garden pitch, b
1-actuation gear addendum thickness, the discharge pressure of P-pump, the B-facewidth.So actuation gear can be an optional tooth number, the wherein best number of teeth equals the integral multiple of N.
Internal gear is supported on the N piece segmental bearing, the aperture of internal gear tooth root, position, hydro-cushion chamber and interior end of engagement constant cabin altitude state position at voussoir, the relief liquor that pressure is arranged is introduced between interior garden cylinder of segmental bearing and the outer garden of the internal gear cylinder, be formed with the lubricating liquid film of pressure, and by garden cylinder in the segmental bearing at above-mentioned two locational elongate slots and bottom land aperture, relief liquor is introduced on the cylinder of the outer garden of segmental bearing in corresponding two balance cylinders of pressure gradient by the shape of seal with O ring and this position.Make segmental bearing in the suffered radial force that is formed by hydraulic pressure of the inside and outside garden of this position cylinder about equally, its direction is opposite, the most of counteracting.This structure is fallen on the interior garden cylinder of pump case radial force at last.
The enclosed space of each engagement inlet end is made up of the planar surface encloses of gear two end respective length the garden cylinder and the side plate of the certain arc length in tooth top garden voussoir.The sealing arc length degree of voussoir enters the sealing arc to begin only to leave the sealing arc to the tooth top edge from the tooth top edge.The fluid pressure that is full of interdental spaces in this section arc length is linear and raises, and is decided to be press area; Leave the sealing arc from the tooth top edge and end to the tired liquid compensating groove terminal point on the side plate, it is that drainage region is decided to be constant cabin altitude state that fluid pressure reaches discharge pressure.When the tooth top edge leaves moment of sealing arc, the arc length of constant cabin altitude state will have a unexpected elongation (t on the planetary pinion and on the voussoir, side plate
2'-b
2), t in the formula
2'-planetary pinion tooth top garden pitch, b
2-planetary pinion addendum thickness, the sealing arc length degree 1 and 1 of the inside and outside end of engagement press area of a planetary pinion ' onesize unexpected decrease will be arranged in other words.When the tooth top edge enter the sealing arc moment, the sealing arc 1 and 1 ' length will be increased to its starting point suddenly, increasing amount is (t equally
2'-b
2).The unexpected variation of this sealing arc length degree makes and the swing of direction and the fluctuation of amount takes place the radial force that is formed by hydraulic pressure on gear and the voussoir that revolution is crossed a tooth and changed one-period.Radial force on voussoir on end of engagement and the outer gearing end position forms the R that makes a concerted effort of a direction swing and big minor swing.Voussoir is by two garden pins location, and wherein the bigger garden pin of diameter is used for the above-mentioned R that makes a concerted effort of balance, and its position is on the mean place of R line of action swing, simultaneously also as the bolt of balance pump cover axial force.The less straight pin of another root diameter is used for balance because the moment that the R swing produces.When voussoir in R line of action direction when the internal gear side has hydro-cushion, the radial force of above-mentioned garden pin is with minimum.
Under the higher discharge pressure for the R on the balance voussoir, on the position that the R line of action is on average swung, a counter balance pocket is set between each voussoir and internal gear, this counter balance pocket is made of the side plate of the interdental spaces of internal gear certain-length and voussoir, two side planes, and by the relief liquor of two apertures on the side plate from ring discharge liquid passage introducing pump, build-up pressure field balance R.
At the outer gearing end of voussoir, be parallel to the Gear center on line and cut a C width, C determines that by the balanced radial force state on the planetary pinion a microscler outage is arranged in the C width.This hole links to each other with another larger-diameter hole on the voussoir, and the discharge opeing of outer gearing end flows into the ring discharge liquid passage by these aperture side plates and front pump cover.Voussoir for the purpose that the radial force that reaches on the planetary pinion changes synchronously, cuts a wedge angle at interior end of engagement if necessary, and the width after cutting is e or e
1The tooth top garden of this width and planetary pinion and internal gear forms 2 intersection points, and the position of this intersection point is determined by above-mentioned synchronous requirement on planetary pinion, and the position of intersecting point on internal gear is determined by the stress of voussoir.When being not enough to perforate in the C width, the discharge opeing of outer gearing end is gone into the ring discharge liquid passage by the orifice flow on the side plate.
Front pump cover and gland are formed a ring discharge liquid passage, and the interior garden cylinder of this annular pass is the equal diameter garden cylinder of gland.This structure be make be subjected on the gland cut down output the axial force minimum living by relief liquor.Have 2N hole to be communicated with the annular pass in the relief liquor position of inside and outside end of engagement, discharge opeing is concentrated in the annular pass, is discharged by the top mouth of pipe.
Side plate has breach at liquid feeding end, in a side milling of pump cover the balance groove is arranged, and introduces relief liquor, the sealing arc shape basically identical of the shape of groove and engagement inlet end, also can around groove, add-O shape circle reduces to leak.End of engagement is milled with tired liquid compensating groove with the position that paste mutually on the gear plane outside.Have outage with the side plate that front pump cover pastes mutually at interior end of engagement constant cabin altitude state, and the balance groove of outer gearing end is connected with outage on the front pump cover.
Working solution is entered by pump back cover central nozzle, sucks 2N the hole that the position has corresponding to gear on the rear pump cover of flowing through, and is engaged end and sucks.Have groove at the front and back pump cover corresponding to the planetary gear bearing position, be communicated with that above-mentioned perforate increases circulation area and bearing lubrication.
The less planetary pinion of diameter is supported on the rolling bearing in the side plate hole.The planetary pinion that diameter is bigger, rolling bearing are contained in the planetary pinion endoporus, and axle is the garden pin, the bolt of double as balance pump cover axial force.
Gear shaft is bearing on two rolling bearings, and axle head has a fluid-tight circle.
Two ends at segmental bearing have key spacing to segmental bearing garden Zhou Fangxiang.
By above-mentioned solution, the advantage that planetary gear pump of the present utility model has is: owing to adopted hydro-cushion, can ignore in radial and axial distortion in the inside of pump part in addition, thereby can keep the fit up gap to guarantee volumetric efficiency and duplex geared pump relatively easily, flow is approximately 2N doubly, and the fluctuation of flow is more level and smooth; Discharge pressure only is subjected to the torsional strength of live axle and placing restrictions on of each tooth-formation of gear mechanical strength, can break through the maximum emission pressure of existing gear pump; There is not the bearing wear problem that causes because of load.
Fig. 1 is the front view after planetary gear pump is thrown off front pump cover;
Fig. 2 is the sectional view of Fig. 1 along A-B-C-D-E;
Fig. 3 is the stressed and shape of voussoir.
Fig. 4 is that the liquid path partially that unloads on the outer gearing end voussoir is analysed and observe;
Fig. 5 is that the F-G of Fig. 4 analyses and observe;
Fig. 6 is that the planetary pinion number of teeth is the same geometrical relationship figure that leaves the sealing arc in a flash in tooth top edge of even numbers;
Fig. 7 is that the planetary pinion number of teeth is the same geometrical relationship figure that enters the sealing arc in a flash in tooth top edge of even numbers;
Fig. 8 is that the planetary pinion number of teeth is the same geometrical relationship figure that leaves the sealing arc in a flash in tooth top edge of odd number;
Fig. 9 is that the planetary pinion number of teeth is the same geometrical relationship figure that enters the sealing arc in a flash in tooth top edge of odd number;
Figure 10 is that the outer gearing end unloads the liquid path partially and analyses and observe when the perforate of the width deficiency of C;
Figure 11 is that the H-I of Figure 10 analyses and observe.
Below in conjunction with these accompanying drawings specific embodiments of the present utility model is described in detail.
Count the planetary gear pump of N=3 at planetary pinion shown in Fig. 1 and Fig. 2, the planetary gear train of this planetary gear pump be actuation gear (11) at the pump center, planetary pinion (12) is 120 ° of symmetric arrangement each other.Its center fixed-site is motionless, and the outer ring of planetary pinion (12) is internal gear (16).Actuation gear (11) rotates counterclockwise by Fig. 1 line of vision, forms 2N=6 engagement inlet end, and this pump has the discharge capacity of a 6q.The number of teeth of actuation gear equals the integral multiple that planetary pinion is counted N, so the radial force on the actuation gear (11) makes a concerted effort to equal 0.Any what stipulate by two tooth top edges that mesh inlet ends that make planetary pinion (12) with the structure that enters the sealing arc in a flash with the sealing arc that leaves voussoir (16) in a flash and this planetary tooth top edge, the variation of the radial force on the planetary pinion is adjusted to synchronously, and the maximum value that reaches the resultant radial force fluctuation on the planetary pinion is minimum.For example facewidth 2cm is at 320kgf/cm
2Be lower than 50kgf under the discharge pressure, the radial force on the planetary pinion is proportional to discharge pressure, in the Intermediate High Pressure of NBS and following, the planetary stressed quick condition that approaches.
Fig. 3 illustrates the distribution of force in radial on the voussoir and their R that makes a concerted effort.Tooth-formation of gear is when diverse location, and vibration and oscillation takes place for the line of action direction of R and size.On the mean place of R line of action swing, a garden pin (7) is set is used for offsetting R, and garden pin (5) is used for offsetting because the swing of R, its line of action departs from the moment that the center of garden pin (7) causes.
Requiring planetary gear pump to have under the situation of higher discharge pressure,, the counter balance pocket that an interdental spaces by internal gear (6), voussoir (16) and side plate (4), (19) form is set in the average swing position of each R line of action.
The enclosed space of each engagement inlet end is sealed gear two Transverse planes tooth top garden cylinder and side plate (4) and (19) by voussoir (16) to be formed.
The outer garden cylinder of segmental bearing (8) is respectively having a balance cylinder corresponding to the position, hydro-cushion chamber of voussoir (16) and corresponding to interior engagement inlet end position, the shape of above-mentioned balance cylinder is a rectangle at the constant cabin altitude state of correspondence, press area in correspondence is an isosceles triangle, and O shape circle (9) and O shape circle (10) is respectively arranged around the above-mentioned balance cylinder.In position, hydro-cushion chamber and interior engagement inlet end constant cabin altitude state position, on the cylinder of interior garden an elongate slot is arranged respectively, bottom land respectively has the balance cylinder on the cylinder of the outer garden of aperture connection, and the length of groove makes has at least an internal gear root aperture to be communicated with it.Two ends of segmental bearing (8) have key (2) to be embedded in building in the groove of pump case (3), and Zhou Fangxiang is spacing to the segmental bearing garden.
Side plate (4), (19) lean on a side milling of pump cover that the hydro-cushion groove is arranged in the position of gear engagement inlet end and hydro-cushion chamber correspondence, and O shape circle is arranged around the groove.Side plate (19) has an aperture to be communicated with the hydro-cushion groove in end of engagement discharge opeing position.Side plate (19) and (4) have two apertures to be communicated with the hydro-cushion groove in position, hydro-cushion chamber, and the distance between two apertures makes has at least the interdental spaces of an internal gear to be communicated with it.The end of engagement side plate has tired liquid compensating groove with the side milling that paste mutually on the gear plane outside.Side plate (4) has an elongated hole to be communicated with the hydro-cushion groove at this place and the outage on the front pump cover (21) in interior end of engagement discharge opeing position, the outage on this hydro-cushion groove of end of engagement and the front pump cover (21) is communicated with outside.Side plate (4) and (19) have shape and the corresponding breach of voussoir (16) at liquid feeding end.
Liquid is flowed into by rear pump shell (13) central nozzle, go up 2N the hole and the side plate (4) that suck corresponding to gear that the position has through rear pump cover (17) and have shape and the corresponding breach of voussoir (16) at liquid feeding end, sucked by gear between inflow voussoir and the gear with (19).Rear pump cover (17) is gone up the position corresponding to planetary gear bearing, has N bar groove to be communicated with above-mentioned perforate, lubricates with the inhalant liquid circulation sectional area of increase outer gearing end with to planetary gear bearing.Front pump cover (21) with the corresponding position of planetary gear bearing, also have N bar groove with the inhalant liquid circulation sectional area that increases the outer gearing end and lubricated to planetary gear bearing.
Front pump cover is formed a ring discharge liquid passage with gland (24), the interior garden cylinder of ring discharge liquid passage is the equal diameter garden cylinder of gland (24), by O shape circle (23) sealing, make the axial force minimum that is subjected on the gland, the top of front pump cover (21) has a discharge opeing mouth of pipe to be connected with the annular pass.Being milled with Chang Yuan hole or hole, garden with the corresponding position of interior engagement and outer gearing discharge opeing position, be communicated with the annular pass on the front pump cover, the hole of engaging position is sealed by O shape circle (22) between front pump cover and gland outside; Pump cover and pump case are connected by bolt (1), and gland is connected by garden pin (7).
The less planetary pinion of diameter is supported on the rolling bearing (18) in the side plate hole; The planetary pinion that diameter is bigger, rolling bearing are installed in the planetary pinion endoporus, and axle is the bolt of garden pin (7) double as balance pump cover.
Live axle (11) is supported on rolling bearing (15) and (26), and the external part of axle has a fluid-tight circle (25).
It is that the planetary pinion of even numbers leaves moment of sealing arc by the tooth top edge of diagram sense of rotation that Fig. 6 illustrates the number of teeth, and being voussoir (16) moves on to a M1 and M2 at the outer gearing inlet end by the crossing naturally intersection point M in tooth top garden.They are that the center on line that is parallel to planetary pinion (12) and actuation gear (11) on voussoir (16) cuts part formation, and the width of some M1 to M2 is C, C=A
1-((D
2COS θ
5)/2+(D
2COS θ
4)/2), sin θ
4=(D
2/ D
1) sin θ
5C is determined by the balanced radial force state on the planetary pinion, is one and adjusts the factor.In the C width, have an elongated hole.When being not enough to perforate in the C width, the discharge opeing of outer gearing end flows into the ring discharge liquid passage by the perforate that side plate (4) is gone up and C is tangent.The angular orientation that M1 is ordered is θ
5, the tooth top edge of end of engagement and interior end of engagement is characterized in that voussoir (16) moves on to width e or e after cutting a part by voussoir at the tooth top garden of interior engagement inlet end nature intersection point M3 when leaving the sealing arc in a flash outside
1The point M4 that on planetary pinion, forms, the angular position of some M4
2'=θ
5+ 360 °/Z
2, Z
2-planetary pinion the number of teeth.
Fig. 7 illustrates the planetary pinion that the number of teeth is even numbers.Enter the moment of voussoir sealing arc by the tooth top edge of diagram sense of rotation.The position of this starting point on planetary pinion of voussoir sealing arc is that inside and outside two end of engagements differ 180 ° ± nt
2'/(D
2/ 2), wherein n comprises 0 positive integer.N is one and adjusts the factor that the size of n is as the criterion with the maximum value minimum that reaches the resultant radial force fluctuation on the planetary pinion.
It is that the planetary pinion of odd number leaves moment of sealing arc by the tooth top edge of diagram sense of rotation that Fig. 8 illustrates the number of teeth, and voussoir (16) feature and the number of teeth of end of engagement outside is that the planetary voussoir of even numbers is identical.
The tooth top edge of end of engagement and interior end of engagement is when leaving voussoir sealing arc in a flash outside, moves on to width e or e after cutting a part by voussoir at interior engagement inlet end tooth top garden nature intersection point M8
1The point M9 that on planetary pinion, forms, the angular position of some M9
2"=θ
5+ 180 °/Z
2
It is the planetary pinion of odd number enters voussoir sealing arc by the tooth top edge of diagram sense of rotation moment that Fig. 9 illustrates the number of teeth.The position of this starting point on planetary pinion of voussoir sealing arc is that inside and outside two end of engagements differ 180 ° ± (n+1/2) t
2'/(D
2/ 2), wherein n comprises 0 positive integer.N is one and adjusts the factor that the size of n is as the criterion with the maximum value minimum that reaches the resultant radial force fluctuation on the planetary pinion equally.
Claims (10)
1, a kind of planetary gear pump, it comprises inside and outside gear, the segmental bearing of voussoir, side plate and supporting internal gear, it is characterized in that: it has an actuation gear (11) at the center, internal gear (6) is in the outer ring, the planetary gear train of planetary pinion (12) between actuation gear and internal gear, wherein planetary pinion (12) has the symmetric arrangement of its center fixed-site; Planetary pinion is counted N 〉=2; Each planetary pinion and internal gear (6) actuation gear (11) forms 2N engagement inlet end on its sense of rotation; The tooth top edge of two engagement inlet ends on the planetary pinion (12) is any with the sealing arc that enters voussoir (16) in a flash what stipulate with the sealing arc that leaves voussoir (16) in a flash and this planetary tooth top edge; The enclosed space of each engagement inlet end is made up of the planar surface encloses of gear two end respective length the garden cylinder of the certain arc length in tooth top garden and side plate (4) and (19) voussoir (16); Each hydro-cushion chamber is made of side plate (4) and (19) of the interdental spaces of internal gear certain-length and voussoir (16), two side planes; On the mean place of R line of action swing, a garden pin (7) is set and is used for offsetting the garden pin of swinging owing to R (5); Internal gear (6) is supported on the N piece segmental bearing (8); The outer garden cylinder of segmental bearing (8) respectively has a balance cylinder in position, hydro-cushion chamber and interior engagement inlet end position corresponding to voussoir (16); Front pump cover (21) is formed annular apocenosis passage and is communicated with a discharge opeing mouth of pipe with gland (24); Rear pump cover (17) is gone up corresponding to gear suction position and is had 2N hole, and rear pump cover (17), front pump cover (21) have N bar groove corresponding to the planetary gear bearing position and be communicated with above-mentioned perforate; Rear pump shell (13) has a feed liquor mouth of pipe; Planetary pinion (12) be supported on that bearing (18) in side plate (4) and (19) hole is gone up or Bearing Installation at the planet bore.
2, gear pump according to claim 1, it is characterized in that voussoir (16) moves on to a M1 and M2 at the intersection point M that the outer gearing inlet end is intersected naturally by the tooth top garden, they are that the center on line that is parallel to planetary pinion (12) and actuation gear (11) on voussoir (16) cuts part formation, the width of point M1 to M2 is C
C＝A
1－〔（D
2cosθ
5）／2＋（D
1cosθ
4）／2〕，sinθ
4＝（D
2／D
1）sinθ
5。
3, gear pump according to claim 1 is characterized in that the planetary pinion number of teeth is the voussoir (16) of even numbers, moves on to width e or e after cutting a part by voussoir at the tooth top garden of interior engagement inlet end nature intersection point M3
1The point M4 that on planetary pinion, forms, the angular position of some M4
2'=θ
5+ 360 °/Z
2
4, gear pump according to claim 1 is characterized in that the planetary pinion number of teeth is the voussoir (16) of even numbers, and the tooth top edge enters the position of starting point on planetary pinion (12) of sealing arc, is that inside and outside two end of engagements differ 180 ° ± nt
2'/(D
2/ 2), wherein n comprises 0 positive integer.
5, gear pump according to claim 1 is characterized in that the planetary pinion number of teeth is the voussoir (16) of odd number, moves on to width e or e after cutting a part by voussoir at interior engagement inlet end tooth top garden nature intersection point M8
1The point M9 that on planetary pinion, forms, the angular position of some M9
2"=θ
5+ 180 °/Z
2
6, gear pump according to claim 1 is characterized in that the planetary pinion number of teeth is the voussoir (16) of odd number, and the tooth top edge enters the position of starting point on planetary pinion (12) of sealing arc, is that inside and outside two end of engagements differ 180 ° ± (n+1/2) t
2'/(D
2/ 2), wherein n comprises 0 positive integer.
7, gear pump according to claim 1, it is characterized in that on the outer garden cylinder of segmental bearing (8), corresponding to the position, hydro-cushion chamber of voussoir (16) and corresponding to interior engagement inlet end position a balance cylinder is being arranged respectively, the shape of above-mentioned balance cylinder is a rectangle at the constant cabin altitude state of correspondence, press area in correspondence is an isosceles triangle, and O shape circle (9) and O shape circle (10) is respectively arranged around the above-mentioned balance cylinder; In position, hydro-cushion chamber and interior engagement inlet end constant cabin altitude state position, on the cylinder of interior garden an elongate slot is arranged respectively, bottom land respectively has the balance cylinder on the cylinder of the outer garden of aperture connection, the length of groove makes has at least an internal gear root aperture to be communicated with it, and two ends of segmental bearing (8) have key (2) to be embedded in the keyway of pump case (3).
8, gear pump according to claim 1 is characterized in that the side milling by pump cover has the hydro-cushion groove in the position of gear engagement inlet end and hydro-cushion chamber correspondence for side plate (4), (19), has O shape circle around the groove; Side plate (19) has an aperture to be communicated with the hydro-cushion groove in end of engagement discharge opeing position; Side plate (19) and (4) have two apertures to be communicated with the hydro-cushion groove in position, hydro-cushion chamber, and the spacing of two apertures makes has at least the interdental spaces of an internal gear to be communicated with it; The end of engagement side plate has tired liquid compensating groove with the side milling that paste mutually on the gear plane outside; Side plate (4) has an elongated hole to be communicated with the hydro-cushion groove at this place and the outage on the front pump cover (21) in interior end of engagement discharge opeing position; End of engagement is communicated with outage on this hydro-cushion groove and the front pump cover (21) outside; Side plate (4) and (19) have shape and the corresponding breach of voussoir (16) at liquid feeding end.
9, gear pump according to claim 1, the interior garden cylinder that it is characterized in that the ring discharge liquid passage are the equal diameter garden cylinders of gland (24), and by O shape circle (23) sealing.
10, gear pump according to claim 1 is characterized in that rear pump cover (17) upward sucks the position corresponding to gear and has 2N hole, goes up corresponding to the planetary gear bearing position at rear pump cover (17), has N bar groove to be communicated with above-mentioned perforate; Front pump cover (21) with the corresponding position of planetary pinion, also have N bar groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92215003 CN2118181U (en) | 1992-01-04 | 1992-01-04 | Planetary gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 92215003 CN2118181U (en) | 1992-01-04 | 1992-01-04 | Planetary gear pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2118181U true CN2118181U (en) | 1992-10-07 |
Family
ID=4959462
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 92215003 Granted CN2118181U (en) | 1992-01-04 | 1992-01-04 | Planetary gear pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2118181U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1320276C (en) * | 2001-08-16 | 2007-06-06 | 米其林技术公司 | Gear pump |
| CN101797887B (en) * | 2009-08-10 | 2013-03-06 | 宁波高新协力机电液有限公司 | Multi-functional drive element used for oil-liquid hybrid electric vehicle |
| CN111164310A (en) * | 2017-10-05 | 2020-05-15 | 株式会社Tbk | Gear pump |
-
1992
- 1992-01-04 CN CN 92215003 patent/CN2118181U/en active Granted
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1320276C (en) * | 2001-08-16 | 2007-06-06 | 米其林技术公司 | Gear pump |
| CN101797887B (en) * | 2009-08-10 | 2013-03-06 | 宁波高新协力机电液有限公司 | Multi-functional drive element used for oil-liquid hybrid electric vehicle |
| CN111164310A (en) * | 2017-10-05 | 2020-05-15 | 株式会社Tbk | Gear pump |
| CN111164310B (en) * | 2017-10-05 | 2022-06-14 | 株式会社Tbk | Gear pump |
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