CN106194722B - Internal gear pump - Google Patents
Internal gear pump Download PDFInfo
- Publication number
- CN106194722B CN106194722B CN201610330614.5A CN201610330614A CN106194722B CN 106194722 B CN106194722 B CN 106194722B CN 201610330614 A CN201610330614 A CN 201610330614A CN 106194722 B CN106194722 B CN 106194722B
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- China
- Prior art keywords
- gear ring
- gear pump
- internal gear
- gear
- covering part
- Prior art date
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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
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
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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
- F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
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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
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/101—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The present invention relates to internal gear pump (1), the gear ring (5) that the internal gear pump (1) has the conveying pinion gear (2) with external toothing portion (4) and prejudicially supports in a rotatable way and relative to conveying pinion gear (2) around gear ring rotation axis (6), there is the gear ring (5) the internal messing portion (7) locally engaged with external toothing portion (4) and radial indentation (9,40), the radial indentation (9,40) to engage the inner peripheral surface and outer peripheral surface (16) of gear ring (5).Suggest providing covering part (28) in the suction room (19) of internal gear pump (1) herein, the covering part (28) covers at least one of radial indentation (9,40) at least one spin angular position of gear ring (5).
Description
Technical field
The present invention relates to internal gear pump, the internal gear pump has the conveying pinion gear with external toothing portion and surrounds tooth
Circle rotation axis rotatably and relative to the gear ring that prejudicially supports of conveying pinion gear, the gear ring have locally with nibble outside
The internal messing portion of conjunction portion engagement and radial indentation, the radial indentation penetratingly engage the inner peripheral surface and outer peripheral surface of gear ring.
Background technique
Internal gear pump is used for trandfer fluid, especially conveying liquid.As crucial component part, internal gear pump has defeated
Send pinion gear and gear ring.For example, conveying pinion gear and gear ring are arranged in the shell of internal gear pump, particularly with rotatable
Mode be supported in the shell.Conveying pinion gear supports in a rotatable way around conveying pinion gear rotation axis, tooth
Circle supports in a rotatable way around gear ring rotation axis.To realize eccentric support of the gear ring relative to conveying pinion gear, tooth
It encloses rotation axis and conveying pinion gear rotation axis is arranged spaced apart in parallel.
Conveying pinion gear is arranged in gear ring herein and has corresponding outer diameter, and the outer diameter is less than the internal diameter of gear ring.It is defeated
It is basically round when sending pinion gear and gear ring in cross section relative to the observation of each rotation axis.Convey the outer diameter of pinion gear
And the internal diameter of gear ring is chosen to a region of the external toothing portion of conveying pinion gear only with the internal messing portion of gear ring and connects
It closes.
Gear ring is for example arranged in the drive shaft of internal gear pump, is particularly connected in a rotatable way with the drive shaft
It connects.Conveying pinion gear can be driven with regard to this by drive shaft and make the conveying pinion gear around conveying pinion gear rotation axis rotation
Movement.Due to the external toothing portion engaged with internal messing portion, gear ring is correspondingly also driven.That is conveying pinion gear directly passes through driving
Axis driving, and gear ring is only driven indirectly by conveying pinion gear by drive shaft.
The backlash that external toothing portion and internal messing portion are respectively provided with multiple teeth and are between tooth.The conveying of internal gear pump
Act through the realization that is interconnected in external toothing portion and internal messing portion.Radial indentation is provided in gear ring, fluid can pass through institute
Radial indentation is stated to escape from backlash.Preferably, such radial indentation is arranged for each backlash is corresponding.Radial indentation therefore at which
In radial directions in internally positioned side upper opening a to backlash, and penetratingly engage the inner peripheral surface of gear ring.In its radial direction
It is located on external side on direction, radial indentation penetratingly engages the outer peripheral surface of gear ring.
During conveying pinion gear rotation and turning around when any tooth in observation external toothing portion, this tooth is temporarily bonded on internal messing
In the backlash in portion.Before indented joint is in backlash, fluid is present in the backlash.By engagement by fluid from backlash pressure
Out, so that fluid is by being the corresponding radial indentation being arranged of backlash on the direction of the outer peripheral surface of gear ring and preferably in internal gear
It is conveyed on the direction of the pressure chamber of pump.Pressure chamber is for example formed in the shell of internal gear pump.Radial indentation preferably constructs
To intersect its longitudinal center axis mutually, particularly intersect on gear ring rotation axis.Certainly, it also can provide radial indentation
Following orientation, the i.e. longitudinal center axis of the radial indentation described in the orientation are partly not with gear ring rotation axis coincident
It arranges and/or is obliquely arranged with the gear ring rotation axis.
Such as known references DE 1 403 899 from the prior art.This describe gear pump, the gear pump band
There are gear ring and the external toothing, the pinion gear that engages with gear ring of internal messing, and be arranged between two gears sickle-shaped fill out
Fill block, wherein gear ring outer peripheral surface and enclose the outer peripheral surface shell hole wall between arrange one or more bearings
Disk, at least one on the pressure side supporting disk, wherein the on the pressure side supporting disk is at it back to having on the outside of gear ring outer peripheral surface
The external pressure area being connect with pump pressure side extend in circumferential direction, long, and the on the pressure side supporting disk at it towards gear ring
Inside on have that smaller pressure discharges area with external pressure area compared with about its radial significant surface, the pressure, which discharges area, to be had
The form in the gap of supporting disk extended in circumferential direction.Here, pressure area pressure release area on the outside of control panel
On the inside of control panel and in axial direction stretch out.
Summary of the invention
The technical problems to be solved by the invention are suggestion internal gear pump now, and the internal gear pump is relative to known interior
Gear pump has the advantage that, achieves particularly higher revolving speed and it is achieved that higher transmission power.
This technical problem is realized by internal gear pump according to the present invention.Suggest mentioning in the suction room of internal gear pump herein
For covering part, the covering part covers at least one radial indentation at least one spin angular position of gear ring.In internal gear
Fluid to be conveyed is provided in the suction room of pump, and then directs fluid into the internal messing portion of the interior gear ring in other words of gear ring
Between the external toothing portion of conveying pinion gear.For example, being used herein to supply or provided in fluid to be conveyed for internal gear pump
The suction connector of gear pump opens directly into suction room.Connector is aspirated herein at least one intracorporal pumping of the shell of internal gear pump
The form of suction head receiving portion exists.Fluid to be conveyed can be provided or supplied by aspirating connector for internal gear pump.
In known internal gear pump, fluid can be flowed into gear ring by radial indentation.By radial indentation with regard to this
Suction room and being formed between the conveying space in gear ring forms flowing connection, and wherein conveying space alternatively can be described as aspirating
Space.By this method, the effective inflow in conveying space is usually realized.But it is higher in the revolving speed of internal gear pump and therefore
When the revolving speed of gear ring is higher, may by raised revolving speed more more strongly act on the centrifugal force on fluid occur for flow into
Influence, and/or in radial indentation formed cavitation erosion.Due to high revolving speed, occurs part in radial indentation in latter instance
Pressure reduction.
If the pressure of fluid depends on terminal pressure pressure reduction below, the steam of the terminal pressure such as fluid
Pressure, then form the phase transition of fluid.If fluid is liquid, this fluid locally evaporates, so that forming bubble or multiple gas
Bubble.This bubble reduces or hinders the flow cross of radial indentation, therefore prevents the inflow in fluid to conveying space, or
Even fully interrupt the inflow.It (cavitates at the boundary value) when exceeding the boundary value of internal gear pump revolution, it is interior
The transmission power of gear pump reduces suddenly.Furthermore, it is possible to since there is undesirable the formation of noise in cavitation erosion.
Due to this, covering part is provided in present suction room.This covering part is arranged as making it at least one of gear ring
Ground is covered or covered at spin angular position engages at least one radial indentation.Hereinafter it should be understood that by means of covering part extremely
Prevent the apparent mass flow of at least one of fluid or fluid from passing through capped radial indentation in a few spin angular position
It is flowed into conveying chamber or vice versa from suction room and is flowed up from conveying chamber in the side of suction room.Particularly suggest keeping covering part close
Feud covers radial indentation.But it hereinafter preferably should not be construed as realizing in the spin angular position of gear ring and be lacked for radial
The covering of the absolute Fluid Sealing of mouth.But only prevent radial indentation from significantly being flowed through by fluid.
With regard to this, covering part can be alap by being placed on gear ring, or for holding for the particularly preferred sealing effect of realization
Friction is slightly arranged with gear ring at interval.In latter instance, gap is formd between covering part and gear ring, in the seam
Fluid may be present in gap.Gap can particularly preferably be configured to form the fluid dynamic bearing of gear ring.
Radial indentation is covered at least one spin angular position by means of covering part.This means that radial indentation is in tooth
Cover is coated in every turn of circle at least once and fully covers or surround engagement.Preferably, covering part is arranged so that for tooth
Circle every turn make at least once respectively radial indentation it is multiple particularly by all radial indentations be coated cover fully cover or
The engagement of covering ground.For this purpose, the size of covering part is on the circumferential direction relative to gear ring rotation axis and/or in axial side
Correspond to size of the radial indentation in all directions upwards.
In addition, covering part is certainly and at least one radial indentation arrangement in the axial direction identical position.For example, can
It is recommended that so that radial indentation it is each it is multiple in circumferential direction observe when be arranged in line.Ground is particularly preferred, multiple this journeys are in axis
It provides with being spaced from each other on direction.Covering part can be now arranged as so that the covering part only covers is arranged in a line
Radial indentation, particularly gear ring is every turn when covering it is primary.But it is radially lacked it is particularly preferred that covering part is configured to covering multirow
Mouthful, it is specially configured to the whole row of covering.
As explained before, internal gear pump has suction room, and fluid to be conveyed is provided in the suction room.Then
Fluid can reach in conveying space from suction room.But if providing covering part, then the inflow in fluid to conveying space cannot
By or only restrictively pass through radial indentation realize.Alternatively, preferably suggesting in the axial direction by gear ring in tooth
At least side of circle preferably exists in conveying space in the two sides of gear ring to be connected from the flowing of suction room.Connect along the flowing
It connects, fluid can enter in gear ring by-pass flow and then be flowed into gear ring when observing in longitudinal section, that is, be flowed into conveying space, excellent
Selection of land flows into a substantially axial direction.
Preferably suggest so that each radial gap is overlapped at least one spin angular position of gear ring with pressure chamber.?
With regard to this there are pressure chamber by suction room, the pressure chamber is for example formed in the shell of internal gear pump.Pressure chamber is preferably in week
Gear ring is engaged partially around ground on direction, i.e., is arranged as more leaning on than gear ring in radial directions relative to gear ring rotation axis
Outside.Pressure chamber be arranged so that at least one of radial gap but be preferably so that whole radial gaps respectively gear ring extremely
It is overlapped in a few spin angular position with the pressure chamber.Preferably, in every turn of gear ring, radial gap be especially it is multiple or
Whole radial gaps are overlapped with pressure chamber once respectively, are preferably flowed and are connected with pressure chamber.
Chamber arrangement is so that when carrying out fluid conveying by the engagement in tooth to backlash according to previous constructions and making
It obtains fluid and passes through radial indentation when being conveyed on the direction of pressure chamber or multiple pressure chambers from backlash, in a rotation of gear ring
There are the coincidence between each radial indentation and pressure chamber and therefore in the presence of flowing connection in Angle Position.Pressure chamber for example with internal gear
Connection is flowed in the press-in connection portion of pump, particularly for good and all flowing connection.By press-in connection portion, can obtain defeated by internal gear pump
The fluid sent.
Radial indentation can have arbitrary cross-sectional flow substantially in the cross section relative to its each longitudinal center axis
Face.But it is particularly preferred that radial indentation has round flow cross.Preferably, radial indentation exists in this as radial hole,
Exist especially as the radial hole with constant diameter, so that simple and cost advantages gear ring manufactures can be realized.
Suggest in preferable configuration of the invention so that suction room extends from the first bearing position in circumferential direction
Until the second bearing position, wherein gear ring herein the first bearing position and the second bearing position in radial directions and/or in axis
It is abutted up to side on the support region for being placed on the shell of internal gear pump and/or by putting on supporting member.First bearing position with
And second bearing position be used in gear ring being supported in the radial direction and/or in the axial direction relative to gear ring rotation axis
In the shell of internal gear pump.For example, the bearing position for supporting gear ring in radial directions is formed as sliding bearing or stream
The form of body bearing is uniquely formed as the form of hydrodynamic bearing.
This means that gear ring is on the first bearing position and the second bearing position in radial directions by being placed on the branch of shell
It holds on region or on each support region, or at least only there is away from the support region low distance, so that gear ring is in radial direction
It is reliably supported on direction.For example, at least one of bearing position, i.e. the first bearing position or the second bearing position can arrange
To make gear ring upward or be expressed to the support region in the side of the corresponding support region of shell by conveying pinion gear
On.Therefore, gear ring is maintained between conveying pinion gear and corresponding support region.
First bearing position and the second bearing position or corresponding support region are respectively provided with when observing in circumferential direction
At most 45 degree of extension, at most 30 degree of extension, at most 25 degree of extension, at most 20 degree of extension, at most 15 degree of extension or
At most 10 degree of extension.Thus, it is only required to the relatively low reliable bearing extended to realize gear ring in circumferential direction.Two branch
Position is held to be spaced from each other in circumferential direction.It is particularly preferred that only providing the first bearing position and the second bearing position.In week
On the one hand there is suction room now between bearing position on direction and on the other hand there is pressure chamber.Suction room and pressure
Room engages each gear ring partially around ground in circumferential direction with regard to this, i.e., straight in the opposite direction from the first bearing position
To the second bearing position.
It alternatively or additionally can provide supporting member.Supporting member is for example arranged in shell and gear ring in the axial direction
Between.Ground is particularly preferred, supporting member presses off gear ring from shell.For this purpose, supporting member for example with spring element phase
It closes, the spring element applies spring force on the direction of gear ring on supporting member.Supporting member can for example be known as axial disk
Or axial supporting disk.To realize the reliable bearing of gear ring in the axial direction, preferably on the opposed side of gear ring respectively
Arrange at least one such supporting member.For example, one of supporting member is rigidly arranged, and supporting member another
Gear ring is pressed on first supporting member by the direction upper pressing tooth circle of first supporting member.But preferably two branch
It holds element and respectively corresponds one spring element of arranging, so that the spring element is in the opposite direction and therefore respectively opposed
Supporting member direction on press the gear ring or the gear ring be pressed on the supporting member.With such arrangement, except good
Bearing outside, reliable backlash compensation is realized in the service life of internal gear pump.
Suggest being configured to covering part to dash forward from the shell that the shell of internal gear pump issues in preferred construction of the invention
Portion out, or be configured as the covering part to be embedded into the intracorporal insert of shell and exist.Substantially covering part can be constructed arbitrarily,
As long as the covering part meets aforementioned condition, i.e., at least the one of radial indentation is covered at least one spin angular position of gear ring
It is a.For example, covering part exists as housing protrusion, the housing protrusion is configured to shell into single-piece and/or and shell
Material one.Shell be expressly understood that herein in circumferential direction at least partly, particularly completely about ground soldered tooth
The housing parts of circle.Housing protrusion extends to be formed cover upwardly through suction room to the side of inherent gear ring in radial directions
Portion.Here, the housing protrusion is arranged as covering at least one radial indentation at least one spin angular position.
Preferably, covering part and thus housing protrusion there is extension in the axial direction, it is described to extend less than suction
The extension of room in a same direction.Covering part only blocks a region of suction room with regard to this, and the especially described covering part will
Suction room is divided into multiple suction seed cells being spaced apart in the axial direction.On the side towards gear ring of covering part, covering part can
It is provided with antifriction coating, such as the coating being formed by polyme, the coating preferably formed by polytetrafluoroethylene (PTFE) (PTFE).
As the substitution that covering part is configured to housing protrusion, covering part can be configured to insert certainly.Insert
Such as it is embedded into shell during internal gear pump installation or is embedded into suction room.Ground is particularly preferred, insert is configured to
It is shape-ordinatedly maintained in suction room, wherein the insert is particularly on the one hand by being placed on shell and on the other hand by putting
On gear ring, so that the insert is securely held between shell and gear ring.Insert can be made of any materials, special
The not described insert and shell are not integrally formed on material and are separately formed with the shell.For example, insert
It is made of antifriction material, such as polymer, especially thermoplastic.Preferably, insert polytetrafluoroethylene (PTFE) (PTFE) is made.
Suggest arranging sickle-shaped filling between conveying pinion gear and gear ring in of the invention another preferably constructs
Block.Filling block provides in conveying space with regard to this.Filling block is preferably on the one hand by being placed on gear ring and on the other hand by being placed on
It conveys in pinion gear.Filling block can be configured to single-piece and/or multi-piece type herein.Filling block is particularly used for preventing fluid defeated
Send the reflux on the direction in space.
Extension suggestion of the invention makes covering have sealing surface, and the sealing surface is parallel to when observing in circumferential direction
Outer peripheral surface trend, wherein sealing surface is spaced apart on the outer peripheral surface for be placed on gear ring or to form gap with the outer peripheral surface.It is covering
Sealing surface is formd with regard to this in cover.This sealing surface is formed as covering at least one diameter at least one spin angular position
To notch.With regard to this, sealing surface is configured to match with the outer peripheral surface shape of gear ring.Particularly, sealing surface in circumferential direction and/or
It is parallel to outer peripheral surface trend when observing in the axial direction, therefore has away from outer peripheral surface constant distance.It is existing in the first construction
It is reliably placed on outer peripheral surface in sealing surface, so that ensure that the particularly reliable sealing of radial indentation.
But alternatively sealing surface can move towards at interval with outer peripheral surface, so that depositing between sealing surface and the outer peripheral surface of gear ring
In gap.Gap can substantially have an arbitrary size, such as distance of the sealing surface away from outer peripheral surface and therefore the thickness in gap is extremely
Mostly 0.5mm is at most 0.25mm, is at most 0.1mm, is at most 0.075mm, is at most 0.05mm, is at most 0.025mm,
It or is at most 0.01mm.The thickness in gap is preferably located in the magnitude of 1/10mm, i.e., from 0.1mm to less than 1mm, or is in 1/
In the magnitude of 100mm, i.e., at least 0.01mm and be less than 0.1mm.
According to previous constructions, the size in gap is constant in circumferential direction.It can alternatively suggest the ruler so that gap
It is very little to change in circumferential direction, particularly continuously change.Following situation is considered by this method, i.e., observes in circumferential direction
When flowed into without the different mass flow of covering part by radial indentation at different positions and therefore different sealing effect can
To be enough.Ground is particularly preferred herein is the consecutive variations of gap scale, wherein not providing transition or interruption.With this side
Furthermore formula can realize that the fluid dynamic of gear ring is supported by means of covering part.
Suggest in another advantageous construction of the invention so that radial indentation engagement is accurately wrapped in the axial direction
The flow area of the annular of the outer peripheral surface of radial indentation, quilt when wherein the sealing surface of flow area is observed in the axial direction are enclosed
It engages with being completely covered.Flow area is the imaginary region of the outer peripheral surface of gear ring, especially imaginary partial region with regard to this.It is logical
Stream region is selected as that it is made accurately to surround the radial indentation being present on gear ring in the axial direction, i.e., in the axial direction
Being located in second side back to the first side is extended up to from the external farthest position that is located on the first side of radial indentation
External farthest position.
When observing in circumferential direction, flow area is completely about engagement gear ring.Flow area is ring-shaped with regard to this.It is close
Cover is dimensioned so that when the sealing surface is observed in the axial direction now and engages flow area or cover with fully covering
Lid flow area.The size of sealing surface is then preferably selected such that the sealing surface corresponds to diameter when observing in circumferential direction
To the size of at least one of notch, or engage the radial indentation of multiple direct neighbors with covering simultaneously.It is particularly preferred that herein
Arrangement is embarked on journey when radial indentation is observed in circumferential direction, that is, is on identical axial position.
Of the invention another preferably constructs suggestion so that having the following size when covering part is observed in circumferential direction,
At least the 25% of the i.e. described distance between the first bearing position and the second bearing position of gear ring having a size of suction room side,
At least 50%, at least 75%, at least 90%, at least 95% or 100%.For for by gear ring in radial directions and/or axis
The bearing position supported on direction, with reference to above.Furthermore what should be explained is that bearing position will be taken out when observing in circumferential direction
Suction-chamber surrounds between the bearing position.The size of suction room in circumferential direction corresponds to the first bearing position and the with regard to this
The distance between two bearing positions.
Covering part is constructed so that covering part penetratingly engages at least one portion of suction room in circumferential direction now,
There is at least described size.Can suggest herein so that covering part in circumferential direction completely through ground engage suction room,
So that covering part directly extends directly into the second bearing position from the first bearing position.When smaller, covering part is in week
It is spaced apart on direction with the first bearing position, with the second bearing position or with two bearing positions.
Preferably, suggest in other construction of the invention so that gear ring has other radial indentation, the radial direction
Notch penetratingly engages inner peripheral surface and outer peripheral surface, wherein other radial indentation penetratingly engages in the axial direction accurately
Enclose the other flow area of the imaginary annular of the outer peripheral surface of radial indentation.Other radial indentation is similar to hereinbefore
The radial indentation of explanation constructs.It is particularly preferred that other radial indentation is of the same size and in circumferential direction
Mutual identical distance.Other radial indentation penetratingly engages the other flow area of circumferential surface, described other through-flow
Region is for example directly connected on flow area or in the axial direction with the flow area in the axial direction and is spaced apart.
Other radial indentation is preferably arranged to go when observing in circumferential direction.With regard to this, such as there are radial indentations
A line and radial indentation another row, wherein the first row is accurately surrounded by flow area and another row is by other
Flow area accurately surrounds.Covering part is configured to now by least flow area but preferably additionally by other through-flow area
Domain covering or the in the axial direction engagement of covering ground.
Certainly it can be similar at least one additional row that previous constructions suggest radial indentation, the row is preferably also coated
Cover covers in the axial direction.Substantially, radial indentation can arrange in circumferential direction, that is, be arranged in any number of row
It is interior, such as be arranged in a unique row or be arranged in multiple rows, particularly at least two, at least three, at least four
Or at least five in row.Preferably, here, each of radial indentation is always respectively at least one spin angular position of gear ring
It is capped by covering part.
Other construction of the invention is suggested so that other radial indentation is in the axial direction by sealing surface or other
Sealing surface covering ground engagement.Sealing surface can with regard to this in addition to flow area it is also related to other flow area so that sealing surface covers
Cover multiple flow areas.Preferably, perforation ground is by being placed on gear ring or gear ring when sealing surface is observed in the axial direction herein
On outer peripheral surface, or there is at least one to keep identical distance away from outer peripheral surface.But can also alternatively suggest so that sealing surface only with
Flow area is related.To engage other flow area with covering or cover, other sealing surface is provided in this case.Covering
Portion correspondingly has other sealing surface in addition to sealing surface.Sealing surface and other sealing surface are preferably mutual in the axial direction
It arranges at interval.
Can particularly preferably it suggest herein so that sealing surface and other sealing surface are by being placed on being spaced from each other for covering part
Sealing protruding portion on.Therefore covering part has multiple sealing protruding portions, wherein sealing one of protruding portion have sealing surface and
Another of sealing protruding portion is with other sealing surface.Sealing protruding portion is spaced from each other in the axial direction, so that at it
Between there are free spaces.When radial indentation and other radial indentation are mutually relatively remote in the axial direction, covering part
Such construct particularly has the advantage that.It is covered with wherein flow area and other flow area by unique sealing surface
Construction is compared, therefore the friction of covering part can be reduced by the construction with spaced sealing protruding portion.
Preferred extension of the invention is suggested so that sealing surface and/or other sealing surface have in the axial direction than tooth
Enclose smaller extension.In general, radial indentation is closely constructed in gear ring inside edge.Correspondingly, the short side of radial indentation and gear ring
The outer peripheral surface of gear ring is penetratingly engaged at interval.Although it also means that sealing surface or other sealing surface are in the axial direction not
Entire gear ring must be engaged with covering, but there can be smaller extension.Provided that sealing surface and other sealing surface, especially
It is to provide sealing surface and other sealing surface on spaced sealing protruding portion, then sealing surface generally has at it
It is more smaller than gear ring to extend and/or arranged at interval with each next end side of gear ring in the axial direction respectively.
It can suggest in preferred extension of the invention so that covering part is at least partially disposed in the suction of internal gear pump
In connector.It aspirates connector and suction room flowing connects, preferably for good and all flowing connection.Connector is aspirated for example by shell
Interior notch is formed.For example, notch exists as hole, that is, there is circular cross section.But suction connector can also have separately certainly
The cross section of outer cross section, such as polygonal crosssection, especially substantial rectangular.Covering part at least partially engages now
It is moved towards in suction connector or in suction connector.Particularly, covering part is present in two of suction connector in the axial direction
It aspirates between connector receiving portion.
Suggest forming flow path by gear ring in the axial direction in suction room in preferred construction of the invention,
Especially each flow path is respectively formed in gear ring two sides.The stream between suction room and conveying space is hereinbefore discussed
Dynamic connection does not re-form or at least only secondary ground is formed by radial indentation.Due to this, exist at least by gear ring now
One flow path.Flow path is extended up to from suction room in conveying space or up to conveying space on axial direction
Side, so that fluid is reached in conveying space from suction room by flow path.To form flow path, gear ring is in the axial direction
It is upper to be arranged at interval with shell.It is particularly preferred that fluid can certainly reached in conveying space in gear ring two sides from suction room.
For this purpose, providing flow path on the opposed side of gear ring.
Finally, suggesting in other construction of the invention so that the distance between gear ring and housing wall is that radial indentation exists
At least the 75%, at least 80%, at least 85%, at least 90% of at least unilateral particularly size of bilateral on axial direction, at least
95% or 100%.Radial indentation is bigger, then the fluid throughput of internal gear pump can be bigger.Accordingly, it is necessary to guarantee fluid foot
It can reach in conveying space from suction room fast enough.For this purpose, the distance root between gear ring and housing wall in the axial direction
It is given according to the size of radial indentation in the axial direction.
It is particularly preferred that the distance between gear ring and housing wall are at least as radial indentation size in the axial direction
Greatly.But the distance is at least 75%.But certainly in the other construction of internal gear pump, can also realize it is smaller or larger away from
From for example, at least 150%, at least 200% or at least 250%.
The present invention additionally relates to internal gear pump, and in particular according to the internal gear pump of previous constructions, the internal gear pump is had
Conveying pinion gear with external toothing portion and around gear ring rotation axis in a rotatable way and relative to conveying pinion gear
The gear ring prejudicially supported, the gear ring has the internal messing portion locally engaged with external toothing portion and radial indentation, described
Radial indentation penetratingly engages the inner peripheral surface and outer peripheral surface of gear ring, wherein arranging filling between conveying pinion gear and gear ring
Block, the filling block are supported or are fixed by retaining pin.
Here, conveying cloth between pinion gear and gear ring on the side back to filling block of retaining pin according to the invention
Set flowing induction element.
Flowing induction element, the flowing guidance are provided as the supplement or substitution of covering part, therefore for flow optimized
Element is present between conveying pinion gear and gear ring.Certainly, internal gear pump described herein removes flowing induction element shell and has
Furthermore the covering part explained, the covering part can be extended according to aforementioned discussion.The flow optimized of internal gear pump can be only by means of
Covering part is realized only by means of flowing induction element or by using covering part and flowing induction element.
Supplement of the flowing induction element as the filling block being arranged between conveying pinion gear on gear ring.Filling block is special
Ground is for covering backlash, so that being effectively prevented fluid when even if in indented joint to each backlash on the direction of conveying space
Reflux.For this purpose, when being observed in cross section, filling block be preferably on gear ring or in the internal messing portion of gear ring or
It exists in conveying pinion gear or in the external toothing portion of conveying pinion gear.Filling block is fixed particularly rigidly by retaining pin
It is fixed between conveying pinion gear and gear ring, or is supported between conveying pinion gear and gear ring, such as prop up in a rotatable way
It holds, supports especially about axis, supported in a rotatable way preferably about the longitudinal center axis of retaining pin.
Filling block is opened from retaining pin extension in circumferential direction and is extended in a first direction with regard to this.It is existing to flow induction element
It is also opening from retaining pin extension, but is being upwardly extended in the second party opposite with first direction in circumferential direction.Preferably, it flows
Induction element is fixed and/or is supported also by way of retaining pin.Here, can suggest forming list with retaining pin so that flowing induction element
It part and/or is integrally formed with retaining pin material.The flowing induction element of the task is will be present during the operation of internal gear pump
In conveying in indoor fluid compression to backlash, and this is realized to the good filling of backlash.
Suggest in another construction of the invention so that flowing induction element its extension in circumferential direction extremely
It is above arranged at interval with conveying pinion gear and/or gear ring on a few part, particularly in its entire extends.Filling block is in cross
Preferably by being placed on gear ring and conveying in pinion gear when being observed in section, and for flowing induction element at least partly simultaneously
It is far from it.Therefore can suggest so that flow induction element particularly on its side towards retaining pin for example also by be placed on convey it is small
On gear and/or gear ring.But on the side back to retaining pin of flowing induction element, flowing induction element is observed in cross section
When with conveying pinion gear and/or gear ring be spaced apart.Particularly, entirely between flowing induction element and conveying pinion gear and/or gear ring
It separates；Flow induction element therefore in its entire extension in circumferential direction not by being put into conveying pinion gear and/or gear ring
On.
In another preferable configuration of the invention suggest so that flowing induction element and conveying pinion gear and/or gear ring it
Between distance in circumferential direction back to increasing on the direction of retaining pin.Flow induction element and conveying pinion gear or gear ring it
Between distance it is inconstant when this is observed in circumferential direction, it is increased.Here, flowing induction element and defeated certainly
The distance between pinion gear or gear ring is sent independently to be defined with conveying pinion gear or engaging for gear ring.For example, distance is interpreted as
It flows the distance between tip diameter, root diameter or the pitch diameter in induction element and external toothing portion and (is conveying small tooth
In the case where wheel), or between flowing induction element and the tip diameter in internal messing portion, root diameter or pitch diameter away from
From (in the case where gear ring).Due to distance increased on the direction back to retaining pin, occur between the internal gear pump runtime
Fluid is pressed onto backlash by conveying effect, the conveying effect.
In addition, can suggest in particularly preferred construction of the invention so that flowing the ruler of induction element in the axial direction
The very little size at least corresponding to gear ring.Certainly substantially flowing induction element can have arbitrary dimension in the axial direction, that is, exist
This side up might be less that or be greater than gear ring.For example, the size of flowing induction element in the axial direction corresponds to gear ring and exists
At least 50% of size on the same direction, at least 75%, at least 100%, at least 110%, at least 120%, or at least
125%.Induction element particularly greater than gear ring when being configured to single-piece with retaining pin is flowed, the retaining pin is in the axial direction
Gear ring is extended over for fixing or being supported on shell.
Finally, can suggest in another preferable configuration so that flowing induction element is configured to bearing planar.Flowing guidance
Element is at least partially used as the profile of flow technique to exist with regard to this.For example, the side shape back to retaining pin of flowing induction element
Profile nose as profile.Preferably, flowing induction element forms the only one part of bearing surface.
Detailed description of the invention
The present invention is hereinafter explained in detail according to the embodiment illustrated in the accompanying drawings, without limiting the present invention.Each figure are as follows:
Fig. 1 shows the cross section diagram of internal gear pump, and the internal gear pump, which has, to be arranged in the shell of internal gear pump
Conveying pinion gear and gear ring,
Fig. 2 shows the longitudinal section of the first form of implementation of internal gear pump diagram,
Fig. 3 shows the longitudinal section diagram of the second form of implementation of internal gear pump,
Fig. 4 shows the longitudinal section diagram of the third form of implementation of internal gear pump,
Fig. 5 shows the cross section in the region of the internal gear pump by the flowing induction element with the first variant, and
Fig. 6 shows the cross section in the region by internal gear pump, wherein flowing induction element exists with the second variant.
Specific embodiment
Fig. 1 shows the cross section by internal gear pump 1.Internal gear pump 1 has conveying pinion gear 2, the small tooth of conveying
Wheel 2 rotatably supports around conveying pinion gear rotation axis 3 and has the external toothing portion 4 with multiple teeth and backlash.In addition,
Internal gear pump 1 has gear ring 5, and the gear ring 5 is rotatably supported around gear ring rotation axis 6.Gear ring rotation axis 6 is parallel to
Conveying pinion gear rotation axis 3 is arranged at interval；Gear ring 5 is supported with regard to this relative to conveying 2 bias of pinion gear.Gear ring 5 is complete
Conveying pinion gear 2 is received entirely and there is the internal messing portion 7 with multiple teeth and backlash.Internal messing portion 7 locally with external toothing
It engages in portion 4.Particularly, external toothing portion 4 is at least partially bonded in internal messing portion 7 in engaging zones 8.As it can be seen that internal messing
Each backlash in portion 7 is related to radial indentation 9, and wherein the only one part of radial indentation 9 is identified.Radial indentation 9 is preferably
Be formed as radial hole and be respectively provided with longitudinal center axis, the longitudinal center axis intersects with gear ring rotation axis 6, particularly
It is normal thereto.
Conveying pinion gear 2 is preferably arranged in drive shaft 10, is particularly torsionally connected with drive shaft 10.Convey small tooth
Furthermore wheel 2 is supported in the shell 11 of internal gear pump 1 by drive shaft 10.The bearing of gear ring 5 then passes through the first bearing position 12
It is realized with the second bearing position 13.To form bearing position 12 and 13, shell 11 has support region 14 and 15.Support region 14
It is preferably matched herein with 16 shape of outer peripheral surface of gear ring 5, i.e., particularly on the circumferential direction relative to gear ring rotation axis 6
Bending having the same.In the region of bearing position 12 and 13, supporting area of the gear ring 5 with its outer peripheral surface 16 by being put into shell 11
On domain 14 and 15, and this is reliably maintained in radial directions.Here, being preferably so that the one of bearing position 12 and 13
It is a, it is herein bearing position 13 by being placed in corner positions, the external toothing portion 4 of pinion gear 2 is fully in the corner positions
It is joined in the internal messing portion 7 of gear ring 5.Correspondingly, gear ring 5 by pinion gear 2 or acts on stream between pinion gear 2 and gear ring 5
Body pressure is upward in the side of bearing position 13 and is reliably held on bearing position 13.
Relative to gear ring rotation axis 6, gear ring 5 is in each folding corner region by being placed on support region 14 and support region
On 15, the support region is less than 30 degree, and particularly less than 15 degree.Corner for bearing position 12 and 13 passes through double-head arrow 17
With 18 instructions.When observing in circumferential direction, there are suction room 19 and pressure chambers 20 between bearing position 12 and 13.Suction
Room 19 is blocked in selected diagram and only indicated by a dotted line here.It aspirates in the opening to suction room 19 of connector 21, institute
Suction connector 21 is stated also to be blocked and therefore only illustrate.In the opening to pressure chamber 20 of press-in connection portion 22.Aspirate connector 21 with
And press-in connection portion 22 is formed in shell 11.For example, the suction connector 21 and press-in connection portion 22 have circular cross-section
Hole exist.Fluid to be conveyed can be provided for internal gear pump by aspirating connector 21, and the fluid quilt conveyed by internal gear pump 1
It provides in press-in connection portion 22, and can be obtained in the press-in connection portion 22 or from the press-in connection portion 22.Suction room
The double-head arrow 23 that extends through in circumferential direction illustrates, and pressure chamber 20 extends through the diagram of double-head arrow 24.
Fluid to be conveyed can reach in the conveying space 25 being in gear ring 5 from suction room 19.In conveying space 25
Filling block 26 is selectively arranged, the filling block 26 is preferably sickle-shaped.Filling block 26 is formed as single-piece or can also
Be formed as multi-piece type.Filling block 26 is particularly in folding corner region, forms on shell 11 in the folding corner region
One bearing position 12.Preferably, filling block extends on this folding corner region.The fluid being in conveying space 25 now reaches outer
In engaging section 4 and the backlash in internal messing portion 7, and carried in a rotational direction by the backlash.Direction of rotation passes through arrow 27
Instruction.
By gradually engagement of the external toothing portion 4 in rotation in interior engaging section 7, fluid is compressed in backlash and from tooth
Gap is forced out by radial indentation 9 from gear ring 5.Here, fluid reaches in pressure chamber 20 and can then pass through press-in connection portion 22
It obtains.Radial indentation 9 correspondingly arranges so that each of radial indentation 9 at least one spin angular position of gear ring 5 with pressure
Power room 20 is overlapped, so that forming direct flowing connection between each radial indentation 9 and pressure chamber 20.
During fluid is flowed out from gear ring 5 outward in radial directions by radial indentation 9, pass through radial direction from suction room 19
Inflow in notch 9 to conveying space 25 be at least in the high revolving speed of interior gear pump 1 it is undesirable, to prevent from acting on fluid
On centrifugal force and/or cavitation erosion influence.Correspondingly, covering part 28 is provided in suction room 19, the covering part 28 is in tooth
At least one of radial indentation 9 is covered at least one spin angular position of circle 5.As it can be seen that covering in the cross section illustrated here
Cover 28 can extend in the entire extension of suction room 19 in circumferential direction, that is, pass through entire angular region indicated by arrow 23
Exist on domain, and therefore extends up to the second bearing position 13 from the first bearing position 12.
Although covering part 28 is filled with the first bearing position 12 in illustrated form of implementation here in circumferential direction
And the second entire distance or angular distance between bearing position 13, as indicated by through arrow 23, but the covering part 28 is certainly
Also it can be provided as so that covering part 28 is only filled with a part of this distance in circumferential direction.Here, covering part 28 can be
From the first bearing position 12 or from the second bearing position 13s and between each other bearing position when being observed in circumferential direction
It separates.Certainly, it can also be spaced apart, that is, be in described with two bearing positions 12 and 13 when covering part 28 is observed in circumferential direction
Between bearing position 12 and 13.Covering part 28 is preferably not only in suction room 19 but also is in suction connector 21, i.e., extremely
Partially particularly extend completely through the suction connector 21.
Preferably, covering part 28 has size more smaller than bearing position 12 and 13 in the axial direction, so that covering part
28 only partially fill suction room 19 in the axial direction.Preferably, covering part 28 exists only in the intermediate region of suction room 19
It is interior, such as covering part 28 is in the axial direction in intermediate arrangement in suction room 19.Correspondingly, when observing in the axial direction,
It can cross and therefore reach in conveying space 25 in 28 by-pass flow of covering part in the bilateral of covering part 28 in the fluid in suction room 19.?
In form of implementation illustrated herein, covering part 28 is formed as housing protrusion, i.e., from shell 11 in radial directions in gear ring 5
Direction on extend internally.Alternatively, covering part 28 also can be used as insert presence certainly.Illustrated form of implementation here
In, covering part 28 or housing protrusion are formed as single-piece with shell 11 or are consistently formed with 11 material of shell.
Covering part 28 has sealing surface 29, and the sealing surface 29 is parallel to gear ring 5 when for example observing in circumferential direction
Outer peripheral surface 16 moves towards.For example, sealing surface 29 is by being placed on outer peripheral surface 16.But preferably sealing surface and outer peripheral surface 16 cloth at interval
It sets, so that forming gap 30 between covering part 28 or sealing surface 29 and outer peripheral surface 16.The size in gap 30 is preferably in circumferential direction
It is constant on direction, but alternatively can also change, particularly continuously changes.Preferably, the size in gap 30 is in axial side
It is constant upwards.
Fig. 2 shows the first form of implementation of internal gear pump 1 in longitudinal section.Affiliated cross-wise direction passes through in Fig. 1
Section marks A mark.The form of implementation illustrated herein corresponds essentially to foregoing embodiments, refers to aforementioned discussion to this.It is aobvious
What is seen is that shell 11 is more than one piece sandwich type element and has casing member 31 and bearing covering part 32 and 33.Casing member 31 is in circumferential direction
Preferably completely around engagement gear ring 5 and in the axial direction relative to gear ring rotation axis 6 with more than gear ring 5 on direction
Big extension.Bearing covering part 32 and 33 is arranged or secured in the axial direction on opposed side on casing member 31, and
The bearing covering part 32 and 33 is closed in end side.Preferably arrange in bearing covering part 32 and 33 for drive shaft 10 and
It is accordingly used in the bearing 34 of conveying pinion gear 2, such as sliding bearing or roller bearing.
The bearing of gear ring 5 in radial directions has been discussed above.The bearing of gear ring 5 in the axial direction passes through two
Supporting member 35 and 36 realize, the supporting member 35 and 36 be arranged on the opposed side of gear ring 5 in the axial direction and
Only extend on a part of gear ring 5 in circumferential direction.Supporting member 35 and 36 is arranged in gear ring 5 in the axial direction herein
Between shell 11, it is arranged in shown embodiment between gear ring 5 and bearing covering part 32 and 33 here.Here,
Each provide spring element 37 between each of shell 11 and supporting member 35 and 36, the spring element 37 is by each bearing
Element 35 and 36 is upward in the side of gear ring 5.
Spring element 37 can have simultaneously sealing function for example with the form of sealing element.In addition, in supporting member 35
Notch 38 is flowed with each of 36 interior may be present, the flowing notch engages each bearing member completely through ground in the axial direction
Part 35 and 36.It can be to the fluid being present in pressure chamber 20 in the axial direction in shell 11 and each bearing by flowing notch 38
Apply pressure between element 35 and 36, the additional support for supporting member 35 or 36 in the axial direction is realized with this.
Since the pressure balance between the opposed side of supporting member 35 and 36 that flowing notch 38 is realized leads to spring element
37 are not compressed by the Fluid pressure being present in pressure chamber 20, so that always realizing 35 He of supporting member by spring element 37
The compression being kept essentially constant on 36 to gear ring 5.
Supporting member 35 and 36 is preferably sized such that is aspirating on every side of gear ring 5 in the axial direction herein
The distance between end side and the shell of gear ring 5 are kept in room 19, the distance passes through l herein3Mark.Gear ring 5 has herein
Extension l in the axial direction1, the extension l1Less than the extension l of suction room 19 in the axial direction2.Therefore, although covering
28 fluid of portion can also reach in conveying space 25 from suction room 19, because in suction room 19 in the axial direction by gear ring 5
It is respectively present flow path 39 on bilateral, there is flowing between suction room 19 and conveying space 25 by the flow path and connect
It connects.
Furthermore obvious, arrange by rows of radial indentation 9 that other radial direction is formd in gear ring 5 to be lacked in circumferential direction
Mouth 40.This other radial indentation 40 is arranged at interval with radial indentation 9 in the axial direction and is observed in circumferential direction
When be preferably also in a line.Radial indentation 9 penetratingly engages gear ring 5 in the imaginary flow area 41 of outer peripheral surface 16
Outer peripheral surface 16.Flow area 41 accurately encloses radial indentation 9 in the axial direction and extends with penetrating through in circumferential direction,
This is ring-shaped.The size of flow area 41 in the axial direction corresponds to the diameter d of radial indentation 9.Similar to this, diameter
Outer peripheral surface 16 is penetratingly engaged in the flow area of outer peripheral surface 16 42 to notch 40.
Covering part 28 is configured to that it is made to engage or cover flow area 41 and flow area with covering in circumferential direction
42.Therefore covering part 28 can cover or seal radial indentation 9 and radial indentation under the corresponding spin angular position of gear ring 5
40.As already explained, covering part 28 and shell 11 are configured to single-piece, construct in shown embodiment with casing member 31 here
For single-piece.Covering part 28 can widen in the axial direction on the direction of gear ring 5 at this, to use the sealing surface 29 of covering part 28
To cover flow area 41 and 42.
Fig. 3 shows the second form of implementation of internal gear pump 1 in the longitudinal section of the label B of the section according to shown in Fig. 1.
This form of implementation is substantially similar to the form of implementation described, therefore refers to aforementioned discussion.Basic difference is radial lack
Mouth 9 and 40 is close together in the axial direction.Accordingly it is not required to which broadening of the covering part 28 on the direction of gear ring 5 comes
Therefore two flow areas 41 and 42 are covered.But covering part 28 only has sealing surface 29, the sealing surface 29 covers two again
A flow area 41 and 42.
Fig. 4 shows the third form of implementation of internal gear pump 1 in the longitudinal section for marking B according to section.Referring again to preceding
Review is stated, and below relates to difference.Obvious radial indentation 9 is spaced apart with radial indentation 40 far relatively in the axial direction.For
The friction caused by covering part 28 is reduced as strongly as possible, keeps flow area 41 related to sealing surface 29 and is made through-flow
Region 42 is related to other sealing surface 43.
Sealing surface 29 is present on the first sealing protruding portion 44 of covering part 28, and sealing surface 43 is formed in the axial direction
On the sealing protruding portion 45 arranged at interval with sealing protruding portion 44.It is mutual in the axial direction to seal protruding portion 44 and 45
It separatedly arranges, so that there is the circumferential gap 46 extended in circumferential direction between.It is close in such form of implementation
Envelope portion 28 reduces by the area that is placed on gear ring 5, so that reducing friction simultaneously.
Aforementioned internal gear pump 1 can be run with considerably higher revolving speed compared with known internal gear pump, such as at least
The operation of 3000 revolutions per minute, at least revolving speed of 3500 revolutions per minute or at least 4000 revolutions per minute.By provide covering part 28 reduce from
The influence of mental and physical efforts and/or it restrained effectively the appearance cavitated in radial indentation 9 and 40, so that may occur in which the damage of transfer rate
It loses.
Fig. 5 is shown to be illustrated by the cross section in the region of internal gear pump 1.Particularly visible 2 He of conveying pinion gear herein
Gear ring 5.Internal gear pump 1 is constructed advantageously according to aforementioned discussion, therefore refers to aforementioned discussion.Supplement described below is related to being discussed
The internal gear pump 1 stated all individual or in combination with one another applicable form of implementation.
It will be obvious that filling block 26 is multi-piece type and has the first filling block part 47 and the second filling block part with regard to this
48.Filling block 26 and therefore filling block part 47 and 48 preferably have extension at least identical with gear ring 5 in the axial direction.
But filling block 26 and the therefore extension of filling block part 47 and 48 can be bigger.Have at least one between filling block part 47 and 48
A hollow space 49, the hollow space 49 can be particularly pressurized.The pressure of hollow space 49 applies for example in
Realization is connect with the flowing of pressure chamber 20 for absolutely empty 49.Due to pressure apply, filling block part 47 and 48 in radial directions by
Mutually press off so that the first filling block part 47 by be placed on conveying pinion gear 2 on and the second filling block part 48 by being placed on gear ring 5
On.
Filling block 26 is supported or is fixed by retaining pin 50 in circumferential direction, and the retaining pin 50 is for example bonded on bearing
It supports in the blind hole of covering part 32 and 33 and therefore and supports in covering part 32 and 33, such as can be revolved around its longitudinal center axis
Transhipment is dynamic.Retaining pin 50 has the retainer 51 of plane, can support filling block 26, especially first on the retainer 51 and fills out
Fill block portion point 47 and the second filling block part 48.For this purpose, filling block part 47, filling block part 48 or two filling block portions
Divide 47 and 48 correspondingly to have (not identify herein) by the face of putting relatively.It is realized by means of filling block 26 for the reliable of backlash
Sealing, so that largely or even fully preventing the fluid of the particularly period in indented joint to backlash to suction room
Reflux in 19.
For the transmission power for being further improved internal gear pump 1, the backlash in external toothing portion 4 and/or internal messing portion 7 should be realized
Particularly reliable filling.This realizes that the flowing induction element 52 is observed in circumferential direction by means of flowing induction element 52
When be present in retaining pin 50 back on the side of filling block 26.Preferably, the side towards retaining pin 50 of induction element 52 is flowed
With round or part circular gap, 50 part of retaining pin when matching with 50 shape of retaining pin, therefore observing in cross-section
Ground is bonded in the gap.It is for example fixed by fixed pin 53 to flow induction element 52, is particularly fixed on shell 11, it is special
It is not preferably fixed to bearing covering part 32 and/or supports in covering part 33.Filling block 26 is for example only embedded into conveying space
In 25 or between conveying pinion gear 2 and gear ring 5, and flowing induction element 52 can be rigidly fixed.
Flowing induction element 52 is preferably upper small with conveying in its entire extension in circumferential direction in radial directions
Gear 2 and gear ring 5 are arranged at interval.Here, when being observed in cross section, in flowing induction element 52 and conveying pinion gear
There are fluid gaps 54 between 2, and there are fluid gaps 55 between flowing induction element 52 and gear ring 5.Fluid gap 54
With 55 at least one, i.e., both fluid gap 54, fluid gap 55 or fluid gap 54 and 55 are preferably in circumferential direction
It is reduced on the direction of retaining pin 15 or filling block 26 when upper observation.With this, the fluid carried by conveying pinion gear 2 and gear ring 5
Be extruded in the backlash in external toothing portion 4 and/or internal messing portion 7, with this improve the filling of the backlash and therefore further
Improve the transmission power of internal gear pump.
The wheel of flow technique can be formed for example formed as the form of bearing surface that is, in cross section by flowing induction element 52
Exterior feature, wherein the profile nose of flowing induction element 52 be present in circumferential direction flowing induction element 52 back to filling block 26
Side on.When observing in circumferential direction, flowing induction element 52, which preferably has, to be extended, and the filling block 26 that extends to is in phase
With direction on extension at least 25%, at least 50%, at least 75% or 100%.
Fig. 6 shows the region of the internal gear pump 1 hereinbefore described, wherein there is only flowings to draw in the construction of substitution
Guiding element 52.Therefore, aforementioned discussion is fully referred to.It is that flow induction element 52 does not pass through now with the difference of aforementioned discussion
Fixed pin 53 is fixed, but exists with retaining pin 50 as single-piece and/or integrally exist with 50 material of retaining pin, or is at least solid
It is scheduled in retaining pin 50.
The blind hole that retaining pin 50 is preferably articulated to bearing covering part 32 and 33 as explained before is interior and correspondingly opposite
It is supported or held in the blind hole.With regard to this, retaining pin 50 from the two sides of flowing induction element 52 and flows in the axial direction
Dynamic induction element 52 is laterally joined in blind hole.It is formed directly into flowing guiding element now by the face of putting 51 for filling block 26
On part 52.Therefore, flowing induction element 52 can be rotated relative to its longitudinal center axis and is moveably supported on shell 11.Example
Such as, it there is provided herein end stop portion, so that the rotary motion only quilt in certain rotation angle of flowing induction element 52
Allow.Alternatively, rigid fixation can be carried out certainly.
Claims (15)
1. a kind of internal gear pump (1), the internal gear pump (1) has the conveying pinion gear (2) with external toothing portion (4) and encloses
It is described around gear ring rotation axis (6) in a rotatable way and relative to the gear ring (5) that conveying pinion gear (2) prejudicially supports
Gear ring (5) has the internal messing portion (7) locally engaged with external toothing portion (4) and radial indentation (9), the radial indentation
(9) inner peripheral surface and outer peripheral surface (16) of the gear ring (5) are penetratingly engaged, which is characterized in that the pumping in internal gear pump (1)
Covering part (28) are provided in suction-chamber (19), the covering part (28) is covered at least one spin angular position of the gear ring (5)
Cover at least one described radial indentation (9).
2. internal gear pump according to claim 1, which is characterized in that the covering part (28) has sealing surface (29), institute
It states and is parallel to outer peripheral surface (16) trend when sealing surface (29) is observed in circumferential direction, wherein the sealing surface (29) is by being placed on
It is spaced apart on the outer peripheral surface (16) of the gear ring (5) or with the outer peripheral surface (16) to form gap (30).
3. internal gear pump according to claim 2, which is characterized in that the radial indentation (9) is penetratingly bonded on axial direction
The flow area (41) of the outer peripheral surface (16) of the radial indentation (9) is accurately surrounded on direction, wherein the sealing surface (29)
Wrapping ground completely engages the flow area (41) when observing in the axial direction.
4. internal gear pump according to claim 1, which is characterized in that when the covering part (28) is observed in circumferential direction
Size be the gear ring (5) the first bearing position (12) and the second bearing position (13) between suction room lateral extent extremely
Few 25%.
5. internal gear pump according to claim 3, which is characterized in that the gear ring (5) has other radial indentation
(40), the other radial indentation (40) penetratingly engages inner peripheral surface and outer peripheral surface (16), wherein the other radial direction
Notch (40) penetratingly engages annular that accurately surround the other radial indentation (40) in the axial direction, imaginary
The other flow area (42) of outer peripheral surface (16).
6. internal gear pump according to claim 5, which is characterized in that the other flow area (42) is in the axial direction
On by the sealing surface (29) or other sealing surface (43) covering ground engagement.
7. internal gear pump according to claim 6, which is characterized in that the sealing surface (29) or other sealing surface (43)
There is extension more smaller than the gear ring (5) in the axial direction.
8. internal gear pump according to claim 1, which is characterized in that the covering part (28) is at least partially disposed in institute
In the suction connector (21) for stating internal gear pump (1).
9. internal gear pump according to claim 1, which is characterized in that seen in the axial direction in the suction room (19)
Flow path (39) are formd by the gear ring (5) when examining.
10. internal gear pump according to claim 1, which is characterized in that between the gear ring (5) and housing wall it is axial away from
From at least 75% of the size for the radial indentation (9) in the axial direction.
11. a kind of internal gear pump according to any one of the preceding claims, which is characterized in that in the conveying pinion gear
(2) it being arranged between the gear ring (5) filling block (26), the filling block (26) is supported or is fixed by retaining pin (50),
Wherein, on the side back to filling block (26) of the retaining pin (50) the conveying pinion gear (2) and the gear ring (5) it
Between arrange flowing induction element (52).
12. internal gear pump according to claim 11, which is characterized in that the flowing induction element (52) is in circumferential direction
On arrange at interval at least one portion that it extends with the conveying pinion gear (2) and/or the gear ring (5).
13. internal gear pump according to claim 11, which is characterized in that the flowing induction element (52) is in circumferential direction
On upper arranged at interval with the conveying pinion gear (2) and/or the gear ring (5) in its entire extends.
14. internal gear pump according to claim 11, which is characterized in that the flowing induction element (52) and the conveying
The distance between pinion gear (2) and/or the gear ring (5) increase on the direction back to retaining pin (50) in circumferential direction.
15. internal gear pump according to claim 11, which is characterized in that the flowing induction element (52) is in the axial direction
On size correspond to the size of at least gear ring (5).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102015209836.2 | 2015-05-28 | ||
| DE102015209836.2A DE102015209836B3 (en) | 2015-05-28 | 2015-05-28 | Internal gear pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106194722A CN106194722A (en) | 2016-12-07 |
| CN106194722B true CN106194722B (en) | 2019-01-15 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610330614.5A Active CN106194722B (en) | 2015-05-28 | 2016-05-18 | Internal gear pump |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN106194722B (en) |
| DE (1) | DE102015209836B3 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102019217049A1 (en) * | 2019-11-06 | 2021-05-06 | Robert Bosch Gmbh | Internal gear machine with hydrostatically supported inner sealing part on the filler piece |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1403899C3 (en) * | 1961-01-19 | 1974-03-07 | Otto 7502 Malsch Eckerle | Gear pump |
| DE59101434D1 (en) * | 1990-08-20 | 1994-05-26 | Barmag Luk Automobiltech | Internal gear pump for hydraulic fluid. |
| DE4135725C2 (en) * | 1991-10-30 | 1994-05-26 | Voith Gmbh J M | Internal gear pump with two ring gears and a common pinion |
| DE4338875C2 (en) * | 1993-11-13 | 2003-11-06 | Eckerle Ind Elektronik Gmbh | Reversible internal gear machine (pump or motor) |
| CN202431515U (en) * | 2011-11-25 | 2012-09-12 | 李小东 | Gap compensation structure for internal gear pump |
| CN103883515A (en) * | 2014-02-24 | 2014-06-25 | 江苏驰翔精密齿轮有限公司 | Internal meshing gear pump |
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2015
- 2015-05-28 DE DE102015209836.2A patent/DE102015209836B3/en active Active
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2016
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| Publication number | Publication date |
|---|---|
| CN106194722A (en) | 2016-12-07 |
| DE102015209836B3 (en) | 2016-06-02 |
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