CA2143719C - Vane cell machine - Google Patents
Vane cell machine Download PDFInfo
- Publication number
- CA2143719C CA2143719C CA002143719A CA2143719A CA2143719C CA 2143719 C CA2143719 C CA 2143719C CA 002143719 A CA002143719 A CA 002143719A CA 2143719 A CA2143719 A CA 2143719A CA 2143719 C CA2143719 C CA 2143719C
- Authority
- CA
- Canada
- Prior art keywords
- rotor
- vane
- stator
- vanes
- area
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Classifications
-
- 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
-
- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
-
- 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
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Hydraulic Motors (AREA)
- Centrifugal Separators (AREA)
- Soil Working Implements (AREA)
Abstract
In order to compensate in an efficient manner the radial and axial forces in a vane cell machine, and at the same time to increase its service life, the vane cell machine for liquids has a slotted rotor (I) mounted in a stator (4), and in which radially movable vanes (9) are slidingly mounted in such a way that they can be pressed against a stator inner wall by centrifugal, elastic or other pressure forces. Expanding or narrowing sickle-shaped feeding cells are formed and the liquid enters through a hollow, central stator, so that the vane cells are filled from the inside towards the outside. The rotor (I) is tubular and designed without a shaft; its two sides are prolonged beyond the working area determined by the vanes and the rotor is mounted in the outer stator by means of its prolongations. The rotor has vane slits that extend from its in-ner to its outer diameter. In the area of the rotor prolongations, the casing of the stator has hydraulic working surfaces oriented towards the rotor and on whose surface the operation pressure is applied and/or not applied in order to at least partially compen-sate or avoid radial forces.
Description
07-RPR-1995 07:49 RIr_HTER & PRRTNER +49 40 352415 S.02 21~3~~.~
._ . - ~ _ Vane Cell Machine SCOPE OF APPLICATION
the present invention relates to a vane cell machine for liquids, comprising a rotor having radially proceeding guide slots mounted in a stator, in which slots radially displa-ceable Vanes are slidingly disposed which, while acted upon by centrifugal forces, can be pressed against an inside wall of the stator, wherein, in the course of a rotor rotation, delivery cells are formed which expand or narroN in a cres-cent-shaped fashion and the entry of the liquid takes place through a tubular internal stator and the filling of the vane cells is effected from the inside to the outside.
STATE OF THE ART
Vane cell machines are constructed in the form of fixed dis--placement pumps nr fixed displacement motors or in the form of variable displacement pump or variable displacement motor.
Howevarr v2ne cell machines are likewise employed in the form of volumetric meters. The advantages of the vane cell machines reside in their uniform delivery flow and in their quiet run ping. Problems do arise though due to the respective hydrau-lic radial and axial bearing loads.
The hydraulic radial bearing loads in vane cell machines pos-sessing rotor lengths equal to the operating area of the va-nes result from the product of the projection surface, for-med of rotor and projecting vane and the hydraulic pressure, i.e. the pressure differential acting upon the rotor. Smaller radial loads result from the friction of the vanes on the sta-tor and in the rotor slots as well as from the dead weight of the rotor. In order to intercept the altogether resulting radial forces and the powerful forces occurring already at RPR 7 '95 02:46 +49 40 352415 PRGE.0~2 07-faPR-1995 07:49 RICHTER & PRRTNER +49 40 352415 S.03 21~~71~
._ . - ~ _ Vane Cell Machine SCOPE OF APPLICATION
the present invention relates to a vane cell machine for liquids, comprising a rotor having radially proceeding guide slots mounted in a stator, in which slots radially displa-ceable Vanes are slidingly disposed which, while acted upon by centrifugal forces, can be pressed against an inside wall of the stator, wherein, in the course of a rotor rotation, delivery cells are formed which expand or narroN in a cres-cent-shaped fashion and the entry of the liquid takes place through a tubular internal stator and the filling of the vane cells is effected from the inside to the outside.
STATE OF THE ART
Vane cell machines are constructed in the form of fixed dis--placement pumps nr fixed displacement motors or in the form of variable displacement pump or variable displacement motor.
Howevarr v2ne cell machines are likewise employed in the form of volumetric meters. The advantages of the vane cell machines reside in their uniform delivery flow and in their quiet run ping. Problems do arise though due to the respective hydrau-lic radial and axial bearing loads.
The hydraulic radial bearing loads in vane cell machines pos-sessing rotor lengths equal to the operating area of the va-nes result from the product of the projection surface, for-med of rotor and projecting vane and the hydraulic pressure, i.e. the pressure differential acting upon the rotor. Smaller radial loads result from the friction of the vanes on the sta-tor and in the rotor slots as well as from the dead weight of the rotor. In order to intercept the altogether resulting radial forces and the powerful forces occurring already at RPR 7 '95 02:46 +49 40 352415 PRGE.0~2 07-faPR-1995 07:49 RICHTER & PRRTNER +49 40 352415 S.03 21~~71~
- 2 -minor pressure differentials, the rotor shafts and supports are either dimensioned so as to be sturdy or it is atempted to provide an equalization bymeans of costly and - from a point of view of ftuidics - disadvantageous mufti-stroke pump or motor constructions.
The hydr-auL~c axial bearing toads Can be avoided by the sym-metric design of the axial hydraulically effective areas of the rotor, in which case the hydraulic pressures exerted on the effectice areas have to be uniform. In the embodiment preferred for reasons related to production engineering and costs and possessing an axially displaceable rotor, the same bears against the stator within the area on one side, while the hydraulic pressure becomes more effective on the opposite side so that no axial power balance exists. It would be possible to provide a remedy with the aid of any axially immovable construction of the rotor support with a precise, uniform adjustment of the front end rotor gap, which, however, is expensive. Thus, by way of example, for a pneumatic compressor or motor related to the subject matter of the apptication, pneumatic pads in some of the recesses machined into the front ends of the rotor are provided accor-ding to the DE-A-21 33 455 and which are located between the guide vanes and are supplied with compressed air through ducts machined in a crescent-configured manner into the late-ral covers of the housing so that, when the rotor is axially displaced, pressure differentials occur between the pneumatic pads located on both sides of the rotor, which exert repel-lent farces in the direction of a central position.
A comparatively costly solution i~ likcwisc propo~cd in the DE-A-31 2Q 350 for a vane veil machine, in which the shaft rotor is designed ~o ac to pQa~c:,:, tKV lc7rgc axially dig pLaceabte bushings which are acted upon by the teed pressure in prossurixed gaps in axially di~pLaCcablc bearing bu~hingc on the rear sides and front ends in order to bring about a RPR 7 '95 02:46 +49 40 352415 PAGE.003 07-APR-1995 07:50 RICHTER & PARTNER +49 40 352415 5.04 21~3'~~~
The hydr-auL~c axial bearing toads Can be avoided by the sym-metric design of the axial hydraulically effective areas of the rotor, in which case the hydraulic pressures exerted on the effectice areas have to be uniform. In the embodiment preferred for reasons related to production engineering and costs and possessing an axially displaceable rotor, the same bears against the stator within the area on one side, while the hydraulic pressure becomes more effective on the opposite side so that no axial power balance exists. It would be possible to provide a remedy with the aid of any axially immovable construction of the rotor support with a precise, uniform adjustment of the front end rotor gap, which, however, is expensive. Thus, by way of example, for a pneumatic compressor or motor related to the subject matter of the apptication, pneumatic pads in some of the recesses machined into the front ends of the rotor are provided accor-ding to the DE-A-21 33 455 and which are located between the guide vanes and are supplied with compressed air through ducts machined in a crescent-configured manner into the late-ral covers of the housing so that, when the rotor is axially displaced, pressure differentials occur between the pneumatic pads located on both sides of the rotor, which exert repel-lent farces in the direction of a central position.
A comparatively costly solution i~ likcwisc propo~cd in the DE-A-31 2Q 350 for a vane veil machine, in which the shaft rotor is designed ~o ac to pQa~c:,:, tKV lc7rgc axially dig pLaceabte bushings which are acted upon by the teed pressure in prossurixed gaps in axially di~pLaCcablc bearing bu~hingc on the rear sides and front ends in order to bring about a RPR 7 '95 02:46 +49 40 352415 PAGE.003 07-APR-1995 07:50 RICHTER & PARTNER +49 40 352415 5.04 21~3'~~~
3 -a pressure equalization on the shaft rotor so as to minimize the bearing loads and trictional tosses. Disadvantageous is the large and expensive number of precision components in the hydraulic operating sphere, relatively large requisite gap lengths between the high-pressure and low-pressure area and the poor efficiency of the vane cell machine resulting from this. Furthermore, the shaft for the motive power and the power take-off projecting from as rotary piston pump, due to the pressure differential on the shaft seal and with slip ring seals gives additional rise to axial bearing Loads by means of the spring tension of the same, unless a compen-sation is effected on the opposite side by means of a sym-.
metric ConStruCtiOn.
Moreover, rotary piston pumps are known e.g. from the D~-AS
12 36 64'!. TharP, in a ~tatnr hof(.~~r sp2ca of rnnstant dia-~
meter, a cylindrical revolving rotor with a plurality of substantialCy radiaC sCots, in which vanes are sliding, is supported, in which case, by means of a pertinently wavy configuration of the cross-sectional contour of tho stator cavity, several delivery cells are formed between the stator and the rotor to and from which the pumped or operating me-dium is suppCied and removed via tangentially terminating ducts, of which intake or Low-pressure side ducts are in each case bores located on one side of the vane that lead to a concentric, hollow rotor space, while the ducts on the high-pressure side located in each case on the other side of each vane, coromurri~atr irr each case in d corrrirwous lon-gitudinal duct of the rotor allocated to each vane. The lon-gitudinal ducts communicate in turn with an annular groove which communicates with the high~pressure side of the pump or the motor.
pPR 7 '95 02:47 +49 40 352415 PAGE.004 07-RPR-1995 07:50 RICHTER & PRRTNER +49 40 352415 5.05 _ 2143~1~
For the direct feeding and removal of the pumped medium it is also known to provide duw leading into or vut from the delivery cells, which will then have tv communicate in turn with ducts in a sLaLionary housing portion. The use of such rotor ducts is regarded as advantageous in as far as e.g. one orwrvr~e operating spacefs) exist bezween the rotor circumferential area and the circumferential wall of Lhe stator hollow space since, when correspondingly many intake and discharge apertures are disposed in the stator walls, Large parts of the operating spaces are unable to act as areas within which the displacement cells are sealed oft from the inlet side and the pressure side, unless a great many pumping operations are planned which once again diminish the utilizable operating space and give rise to substantial friction losses.
In order to be able to construct the feeding and the dis-charging ducts in the rotor so as to possess an adeauate Width but, on the other hand, to avoid too great a weake-ning of the rotor owing to the ducts and, finally. to pre-vent an axial thrust from pressure ducts having an adverse effect on the pressure, it is further proposed in the DE-AS
1~ 3b 941 that, in the form of delivery~side ducts on the respective side of each vane, sQVaral grnnvec he machined , into the relevant wall of the associated rotor slot, in which r..ase, furthermore, on both sides of the rotor, one annular groove each be disposed in the side walls of the stator which face the rotor front walls, into which thr delivery-side longitudinal ducts of the rotor terminate, while the annular graove~ arc in communication with pres-sure connections of the pump or of the motar_ The rotor hollow space into which the towwpressure-side bores lead, is a part of a concentric longitudinal bore of a shaft con-nected to the rotor. However, thisrotGry piston pump i5 RPR 7 '95 02:47 +49 40 352415 PRGE.005 07-RPR-1995 07:50 RICHTER & PRRTNER +49 40 352415 S.06 ~143'~~.~
expensive to construct on account of the numerous radial bvr-es - also outside the vane slots - as well as owing to the great number of outlets.
The U5-A-3,361,076 describes a vane cell motor with a ro-tor supported in a stator, said rotor being slatted within its operating area which, screwed together with each other is comprised of a accommodation space for the vanes, a terminal piece and a flow sleeve. The accommodation for the vanes comprises a terminal flange which, lust like the terminal piece, projects radially over the external dia-meter of the stator element and thereby laterally limits the hydraulic operating area. The accommodation for the vanes is, in the axial direction, outwardly construcrpd in the form of a shaft, supported on ball and roller bea-~
rind elements and sealed in the stator and caused to pass out from the vane cell motor for receiving a driving ele-ment. In thlS l'.r7SP the terminal piece possesses only a short shaft shoulder for accommodating the rolling bearing.
The filling of the vane cells is effected in this case from the inside to the outside while a rotor is provided shove the slotted area uF,ich is extended to both sides having a greater external diameter for the positively lo-cking axial centering of a displaceable lifting ring. Both extensions are mounted by means of tapered roller bearings, 3Lao for the absorption of radial anil axiel for-crs, in the housing while the one extension is passed out of the machi-ne in the form of a rotationally Sealed shaft for the drive connection. Pressure-adjustable overflow valves limit the gap pressure witlnin the gap areas arising due to leakage caused by the operating pressure which, at the same pres-sure via l,Irese gap areas up to the seal diameter, brings about a pressure equalization. The axial hydraulic forces across the rron-pressure-equatized Surface area below the sealing diameter are absorbed by the bearings. In this vane yell molar the vanes are spring~-loaded, whereby a high RPR 7 '95 02:47 +49 40 352415 PRGE.006 07-RPR-1995 07:51 RICHTER & PARTNER +49 48 352415 5.07 - ~I~3'~~~
degree of proneness exists in so far as, when the spring pressure falls off, it is no Lnnrder Assured that, in the operative state, it wilt be possible for the vanes to be brought to the inner wall of the stator, in addition, a rotation of the rotor to the stator has to be ensured in Sur:h a way that a retracting of the vanes into their re-ceiving slots in the rotor against a spring pressure is possible_ To this is added the circumstance that the three-part rotor is constructed neither to be shiftless nor in a tubular manner, which does not pusse55 a vane slot which is continuous from the internaE to the ex-ternal diamettr since the internal diameter is formed by the ftow sleeve. The pressurized space of the stator does not contritrute within the area of the rotor extensions to the compensation of radial forces which, from the opera-ting Nressure, can only become effective onto the rotor portion. The same pressure present in the gaps, adjustably limited by means of valves, avoids for the effective areas going beyond the seating diameter axial forces by means of thisd pressure, it does, however, leave the effective surfaces below the sealing diameter axially uncompensated pressure-wise.
In the US-A-3,153,384, a vane cell pump is described, in which, on a common shaft and axially rigidly tightened, two rotors separated by a spacer, two supporting rotors.
two spacing sleeves and two equalizing disks are disposed.
The Supporting rotors are Supported in a friction bearing in bushings in a housing, in which, for the compensation of radial hydraulic forces, pprtinpnt recesses acted upon by operating pressure are disposed. The operating pressure is conducted through external pipelines from the pressure side to the recesses in the bearing bushes. In this vane Gall pump, effective Surface areas acted upon by operating pressure and directed against the rotor are provided in RPR 7 '95 02:48 +49 40 352415 PAGE.007 07-RPR-1995 07:51 RICHTER & PRRTNER +49 40 352415 5.08 21~37~9 the stator. For the compensation of radial hydraulic for-ces in vane cell machines or vane pumps possessing a rotor supported in friction bearings it is accordingly known to provide, in the loaded friction bearing area, effective surface areas acted upon by operating pressure.
It is disadvantageous ir, this vane purrn that adJitional gap entry edges acted upon by operating pressure and pos-sessing relatively short gap lengths and that thereby the efficiency is impaired by increased volumetric losses.
Moreover, the formation of hydrodynamic pressure suppor-ting surfaces is prevents to a very large extent since the narrow gaps necessary for this within the supporting bea-ring area are eliminated by the effective areas acted upon by operating pressure which are planned at this point.
According to the FR-A-73 95 435, a vane cell machine is known, in which, in a stator, a shaft-journalled rotor ro-tates, wherein the inner shell surface of the stator pos-sesses three pitch-cirular recesses, whose wall areas are run in such a way that the combination area of two wall areas each comes to be located in the external rotational area of the rotor. The rotor is provided with radially pro-ceeding guide slots for four vanes, in Which case the dis-position of the guide sln*s is such that two oppositely Located guide slots each are, relative to a theoretical radius line, ars raciprocaCly staggered with the result that only one vane each comes to be lie in each indivi-dual pitch-circular reec~~. A slide or journal bearing lubricated by delivery liquid of the rotor shaft is not provided in this case.
The DE-A~2 022 $49 describes a valueless rotary piston pump with circularly rotating vanes assuming the delivery, which is comprised of a stationary sectional axis which determines the position of the vanes in the individual operating phases, wherein the hollow drive shaft is RPR 7 '95 02:48 +49 40 352415 PRGE.008 07-RPR-1995 07:52 RICHTER & PRRTNER +49 40 352415 5.09 - 2i~37I~
eccentrically supported in the pump casing in such a way that, within the operatirry area, an adequate delivery cross-sectionremains between the hollow shaft and the ca-sing and, within the separating area, the hollow shaft rests sealingly against the casing and thus takes charge of the separation between pressure and intake side. The vanes, which bring about the drawing in by suction and the delivery of the medium, project in the operating area so far from the hollow shaft that they reach the casing wall.
The drive shaft is in this case constructed in the form of a hollow shaft, in which the vanes are supported so as to be radially displaceable and are supported on a rigidly dislocated sectional axis, xhile the hollow shaft is supw ported in the pump casing. A shaftless support is thus not provided.
In the rotary piston pumps known according to the state of the art which are provided with vane cells for liauids, which are employed in the form of delivery pumps, an opera-tion far liauids with elevated vapor pressure and without a positive supply feed owing to the net positive suction head rapidly ring with thp rotational seed, an operation with economic drive speeds of e.g. 1450 min-~ and higher is no Lnngpr ~nRRihlp.
The volumetric degree of effectiveness and the dry intake Capacity (with an empty pump) of vane pumps is determined by the gap losses, whose magnitude - with the presupposi-tion of the same delivery product, the same manufacturing precision and pressure differential - depends on the lengths of the gaps. That is why, with a comparable pump flow, sLowiy rotating pumps with a correspondingly great cyclic pump volume and pump Lengths possess poorer volumetric degrees of effectiveness and a lower dry intake capacity RPR 7 '95 02:49 +49 40 352415 PRGE.009 07-APR-1995 07:52 RICHTER & PARTNER +49 40 352415 5.10 - _ 9 _ 21~3~1~
than rapidly rotating pumps with a correspondingly smaller CyCllc pump volume and gap lengths. These technical con nections mentioned, on account of the necessary reduction of the rotary speed by the net positive suction head limit also the possibilities for the constructional improvement of the volumetric effectiveness and of the dry intake ca-pacity.
Furthermore, rotary piston pumps for liquids, as a result of the Large projection area formed by rotor and projecting vanes and acted upon by the pressure differential, call for sturdily dimensioned shafts and bearings, unless the rotary piston pumps are constructed in the form of double~stroke vane pumps or motors which each possess two intake and disw charge apertures for the liquids, a step which is costly from a product engineering aspect and which, in the case of pumps, leads to an increase, and with this, to a dete~
rioration of the net positive suction head.
TECHNICAL PROBLEM~~ TECHNICAL SOLUTION, AbVANTAGES
That is why it is the technical problem of the present in-vention to further develop the known vane pump in such a way that a complete or at least extensive balance of the radial and axial fort a is provided, in which, with a view to a longer useful service fife, the wear should be miniw mined and a greater degree of effectiveness ectnieved. So far as vane cell machines are considered as volumetric meters, the measuring accuracy is intended to be improved in a like manner. It is further the object of the present invention Lo ~xparTd the possibilities of operational appl y cation in the form of a pump by means of a reduction of the net Nvsitive suction head and to improve the degree of effectiveness in the machine employed in the form of a Nump. In addition, it is Lhe Object of the present in-vention to also improve the hydraulic axial and radial APR 7 '95 02:49 +49 40 352415 PAGE.010 stresses at least in part or altogether by means of con-structional steps which do not involve any great construc-tional effort or costs.
Thus this invention seeks to provide a vane pump for liquids comprising a stator having an inner wall surface and a hollow center, a shaftless and tubular rotor mounted on the hollow center of the stator, the rotor having in a vane area thereof radially extending vane slots, the vane slots extending from an inner diameter to an outer diameter of the rotor, a vane being slidably mounted in each vane slot, the vanes being configured to bE: pressable against the inner wall surface of the stator when a compressive force is applied to the vanes, radial recesses being defined in at least one of the vane slots and the vanes, crescent-shaped delivery cells with an increasing or decreasing width being formed between the outer diameter of the rotor, the inner wall surface of the stator and the adjacent vanes, the rotor having at both ends thereof extensions protruding beyond the vane area, the extensions having a diameter equal to or smaller than the outer diameter of the rotor in the vane area, the extensions being received in the stator so as to form a gap seal, wherein the liquids enter axially through the hollow center of the stator and radially through a window defined in the hollow center of the stator in an area of a delivery cell with an increasing width and through the radial recesses into the delivery cell with the increasing width, the hollow center of the stator having recesses adjacent the extension of the rotor, wherein the stator recesses are configured to receive an operating pressure and the recesses having a location and size configured to partially or completely compensate radially directed hydraulic and weight-related forces.
- l0A -According to this the invention consists in that the rotor of the vane cell macshine is constructed so as to be devoid of a shaft and of tubular configuration and in that both sides are extended beyond the operating area determined by the vanes and supported with the extensions in the exter-nal stator and in that it possesses continuous vane slots from the internal to the external diameter and in that the stator frame, within the area of the rotor extensions, possesses on the surface hydraulically effective areas;ac-ted upon and/or relieved by the operating pressure directed against the rotor for the at least partial compensation or avoidance of radially occurring forces. However, in a shaft-less rotor extendingi beyond the operating area toeards both sides, the operating pressure becomes effective in the bearing gaps rotor/external stator located there, which results in further bearing loads. In comparison with it, by means of recesses (effective areas) in the stator frame relieved of the operating pressure, this radial load por-tion is significantly reduced. The tubular extensions on both sides are lubricated with delivery liquid due to the pressure-dependent gap leaks and slidingly supported in the stator.
The vane cell machine is, according to a further embodi-ment, provided with an inlet for the liquid through a hol-low central stator, in which case the ducts for filling the expanding vane cells are formed by radial recesses in the vanes and/or in the vane slots and the concentric sta-tor possesses on its surface effective areas acted upon 07-RPR-1995 07:53 RICHTER & PRRTNER +49 40 352415 5.12 - 2143 rllg by operating pressure and directed against the rotor for the at Least partial compensation of radial. farces, it being possible to sub~itute the recesses with small bores acted upon by operating pressure Which produce, in the bearing or supporting gaps, rotor/external stator, large effective araas directed against tha rotor_ This step is simpler in the fabrication, results in comparatively Lower gap losses and thereby improves the volumetric de-gree of effectiveness. Advantageously, this vane call ma-chine i~ of ~implc construction, a comparatively expansive additional mounting of the shaft and the frictional forces arising t,erefrom are avoided trom the outset, just as axial and radial hydraulic forces are minimized.
In this case the radial ducts for filling the delivery cells are formed by radial recesses in the vanes andlor in the vane slots which proceed continuously from the exter-nal diameter to the longitudinal bore in the form of a shaftCess rotor projecting on both sides beyond the opera-ting area determined by the vanes, while the liquid enters axially through the hoCCou rotor axis and the fiEling of the of the expanding delivery cells takes place in the the radial direction through a window in the rotor axis and, in the further course, through recesses in the rotor slots andlor in the vanes.
The rotor portion which projects beyond the c~peratiry erea or the rotor portions on both sides are rotatable against the rvtor~, bul ar-a fitted in sealingly_ In pumps, in res-pect to the net positive suction head, a significant advan-laye results since solely zhe introduction lasses of the liquid into the rotor slots are to be associated with the rrrl positive suction head and the further pressure lasses up to the filling of the vane ceCls and the speed increase of the liquids connected with this in conjunction with the RPR 7 '95 02:50 +49 40 352415 PRGE.012 07-RPR-1995 07:54 RICHTER & PRRTNER +49 40 352415 5.13 - ~~4~71~
centrifugal -force have to be produced energyNise by the drive. The radial filling of the vane cells from in~idc via the rotor slots, over and above that, has the advan-tage that the inr.lusion of the stroke volume of the vanes in the rotor slots takes place in the cyclic operating volume of the pump or of the motor without a special fil-ling operation for this stroke volume against the centri-fugal force, as i~ necessary Hhen the vane cells erw fil-led tangentially or axially from the outside according to the state of the art. The rotor axis serving at the same time as liquid intake and as a mounting means for the ro-tor does advantayeuu5ly make possible in pumps and motors a cost-saving realization of the hydraulic, in particular radial, Nressure balance by means of a hydrauW c support against the rotor axis.
Further developments of the invention are described in the subclaims.
The recesses are thus preferably acted upon by the opera-ting pressure given by the liquid ~o that no further pres-sure sources or control means are necessary.
According to a first embodiment, the recesses in the sta-tor shell are located opposite the external rotor casing outside the vane operating area, thus, Nith regard to a vertical area passing through the vane operating area, symmetricalyl disposed. According to an alternative embo-diment, the recesses are located in the shell of a stator pivot Hhich reaches through the concentric opening of a rotor tube and bears against the same in a sealing fa-shion. The last-mentioned embodiment possesses the advan-tage that the recesses may also Lie at the same level as the vane operating area, Nhereby a reduction in the over-all height may possibly result. Combinations of said em-bodiment are likewise possible.
RPR 7 '95 02:51 +49 40 352415 PRGE.013 07-RPR-1995 07:54 RICHTER & PRRTNER +49 40 352415 5.14 '.
According to a further construction of the invention, the rvtar portion Which projects beyond the vane operating area possesses an identical or reduced externs! diameter in comparison with a diameter in the vane operating area.
A reduced diameter outside the vane operating area pos-sesses the advantage that, in the course of the vane cell machine operation, the rotor receives an axial centering.
Nhen the vane cell machine is inoperative, the vanes imy merse into the rotor slots whereby, in a rotor poSSeSsing a continuous constant diameter, axial displacements may be possible. In the rotor extended with reduced diameters which otherwise is axially freely movable, the diameter increases serve to center the motor in relation tn thp operating area, in which case it is possible to put up.
with the afaredescribed disadvantage of thp un;lateral~ly greater effectiveness of the hydraulic pressure by bearing against the oppositely Iw ated side since the effective area is kept smalE by a minor difference in diameter. By means of this rotor Centering in relation to the operating space, between the front end areas of the rotor and the stators on both sides, the gap for a hydrostatic force balance at the same pressure is ensured.
In the rotor extended with the same diameter towards both sides, the requisite centering of the rotor relative to the operating area is effected by the vanes. The space in the guide slots underneath the vanes communicates with the vane cell located before the same in the direction of ro-tation, e.g. by means of radial recesses in the vane and!
or in the rotor. Since, in the inoperative state of the vane cell machine, the vanes moved outwardly by centrifu-gal force when operative, can be immersed into the rotor and the freely movable rotor may be axially and unilate-rally displaced against the front-end stator and because RPR 7 '95 02:51 +49 40 352415 PAGE.014 07-RPR-1995 07:54 RICHTER & PARTNER +49 40 352415 5.15 214~7~.~
this may, uhen the pump is started up, hinder the vanes from emerging or may even lead too tilting or wedging within the area of the vanes that are not acted upon by the pressure differential, the stator parts which late-rally delimit the operating space are slightly chamfered in thr dirwtivw Cvkdocls Lhe axis of rwtdtiun str ~s to extend the operating space. These chamferings are carried a little farther on both sides than confiorms to the axial mobility of the rotor in the stator so that, when the vane cell machine commences to rotate, the vanes emerging due to the centrifugal force bring about an immediate cente-ring of the rotor relative to the operating space and this is retained because of lacking axial forces also wi-thout any additional friction on the vanes.
In a special construction according to the invention of the vane cell machine, the rotor is constructed so as to be tubular and possesses a longitudinal bore in which an even number of vane slots terminate openly and in which, the in each case diametrically opposed vanes are rigidly interconnected or of one-piece construction.
However, alternatively to this, the rotor can, when of tubular construction, also receive in the tube apertures a stator pivot which is hollow on the inside and, within the area of the slots passing through the rotor for the displaceable vanes, possesses a window and in which the vanes andlor the rotor slots possess radial recesses. This Corm of construction makes d partial balance of the radial hydraulic fortes on the rotr possible.
By preference, the rotor, at its front ends, is coupled to an axially fixated shaft as drive connection or as power takeoff connection, in whit case the shaft is accommodated in the stator frame.
APR 7 '95 02:51 +49 40 352415 PAGE.015 07-RPR-1995 07:55 RICHTER & PRRTNER +49 40 352415 5.16 _ 15 Thus, preferably within the filling area of the delivery ceELs, the stator bore is executed acroe~ the area which passes through the maximal radial deflection of the vanes radially towards thQ outside in a pitch circlC so that, by means of the recess provided hereby, a communication of two ar more delivery cells exists. This sm p facili-tates the filling of the delivery cells.
Furthermore, the stator frame transitional area between two delivery cells is by preference concentrically disposed with regard to the axis of rotation so that the vanes, when rotating in this area acted upon by a pressure dif-ferential, do not execute any radial movement.
According to a further canstrurtion, the outer shell of the inner stator possesses depressions which can be acted upon by tha p«mp del.ivery pressure or by the input pres-sure of the motor for the at least partial compensation of the radial hydraulic bearing load. By means of this con-structivnaLLy simply effected step it is possible to dis-pense with a ~turdsly dimensioned mounting or support.
The rotor portions which project over the vane operating area preferably possess a reduced external diameter in comparison with the rotor diameter in the vane operating area. Hereby the rotor is axiaEly centered during the ope-ration.
When the rotor is inoperative, the vanes sink into the rotor slots. which may result in an axial displacement of the rotor that does not possess a reduced external diame-ter. In order to pre~ant, when the rotor is restarted, that the vanes become wedged outside their operating area with the stator inner shell, thQ stator shell which late-ratly delimits the vane operating area, within the area of tha non-pressurized vanos, is sonically configured so RPR 7 '95 02:52 +49 40 352415 PRGE.016 07-RPR-1995 07:55 RICHTER & PRRTNER +49 40 352415 S.17 - 1~ - ~~~J~~~
that the vanes slide constrainedly guided into the axially centered position when starting up.
According to a further embodiment, the rotor is connected direct or by means of a coupling on the front side Located opposite the intake aperture to a shaft in the form of a drive or power- take-off means, the shafit being sealingly inserted into the stator shell.
BRIEF DESCRIPTION OF THE pRAWINGS
Embodiment examples of the invention are explained below with the aid of the drawings. This F i g. 1 shows a vertical section through a vane cell machine, F i g. ~ shows a verticalsection in the direction of Line II - II in Fig. 1;
F i g. 3 shows a partial view of a Longitudinal section through a vane cell machine with canically con-figured transitional areas between the Vane operational area and the adjacent stator frame;
F i g. ~+ shows a sectional view through a vane cell ma-chine having a tubular rotor, whose diametri-cally opposed vanes are interconnected;
F i g. 5 shows a vertical section in the direction of Line V - V in Fig. 4;
F i g. 6' shoos a sectional vicw of a vane cell machine with a rotor possessing a concentric bore into which a stator pivot is fitted;
F i g. 7 shows a vertical section in the direction of Line VII - UII in Fig. 6;
RPR 7 '95 02:52 +49 40 352415 PRGE.017 07-APR-1995 07:56 RICHTER & PARTNER +49 40 352415 S.18 - 2143r119~
1~ -F i g. 8 shows an embodiment in which the concentric sta-tor to the intake connection is constructed, in a vertical section;
F i g. 9 shows a vertical section in the direction of dine IX - IX in Fig. $;
F i g. 10 shows a longitudinal cross-section of a further embodiment of a vane cell machine, and F i g. 11 shows a cross-section at the level of the vane ope-rating area vertically to the section as per Fig. 10, F i g. 1Z shows a vertical section through the vane cell maehine~ and F i g. i3 shows a vertical section in the direction of Line XIII - XII in Fig. 12.
DETAILED i)ESCRIpTION OF THE INVENTION AND THE BEST WAY OF
REALIZING THE INVENTION
The vane tell machine is preferably constructed in the form of a single-strske vane pump which, in the embvdimenC slnourn in the Figs. 1 and Z, is in the form of a pump, possesses a shaftless rotor 1 whivh, in the axial direction may possess either an external diameter 2 with a uniform circumference as irr the vane operating area 15, or a circumference 3 redu-ced in contrast thereto. Outside the vane operating area, the rotor 1 is fitted into a stator 4 so as to be sealingly sup-ported. Within this fitting-in area the stator possesses re-cesses 5 which, according to their position arid size, are constructed in such a way that the operating pressure of the liquid acting herein results in a partial or complete hydrau-lic force balance also when taking the frictional and weight related forces into consideration. In the embodiment depicted APR 7 '95 02:53 +49 40 352415 PRGE.018 07-RPR-1995 07:56 RICHTER & PRRTNER +49 40 352415 5.19 ~~ ~ 214371 in Fig. 2, the recesses 5, when viewed in the axial direc-tion, arc disposed in front of on t~ehind the vane operating area 75 and symmetrically thereto.
The vertical front end areas or spacing differences b in diameter difference existing in the top half of Fig. 2 of the rotor 9 serve at the same time for the centering of the rotor, whereby, in operation, an the front end, equal gaps 7 result between the rotor front end and the, in each case, oppositely located stator front end. In the rotors extended with reduced diameters which are otherwise freely movable, these diameter differences 6 serve to center the rotor relative to the operating space, in which connection the previously described disadvantage of the unilaterally greater effectiveness of the hydraulic pressure by bearing against the opposite side is acceptable since the front end area 6 in the form of an effective area is kept small by means of a slight difference in diameter. By means ~f this centering of the rotor relative to the operating space, betNeen the front end areas of the rotor 1 and the stator 4 on both sides, the gaps 7 fore hydrostatic force compensation at the camp pressure are ensured_ The rotor 1 possesses slats 8, each of which proceeds ra-dially, in which the vanes 9 are slidingly guided. The space in the guide scats 8 underneath the vanes 9 communi-cates in each case with the vane cell located in front of the same in the direction of rotation, in the present case by means of radial recesses '10 on the vane andlor recesses 91 in the rotor. Since, in the inoperative state of the vane cell machine, as depicted in Fig. 3, the vanes 9, which, in operation, are moved outwardly by centrifugal force, can be immersed in the rotor and the freely movable rotor 1, whose diameter has not been reduced, may be dis-placed axially on one side against the front end of the APR 7 '95 02:53 +49 40 352415 PRGE.019 07-RPR-1995 07:56 RICHTER & PRRThIER +49 40 352415 5.20 stator 4, whereby, when the vane cell machine is started up, the vanes9 are prevented from emerging, which may lead to as much as a wedging of the Vanes on the stator inner wall in question; within the area of the vanes 4 which are not acted upon by differential pressure, the stator inner frame components 12 Laterally delimiting the operating space are constructed in the direction towards the axis of rotation so as to be conical ar slightly r.hamfered, thus expanding the working space. These conical or chamfe~
red stator inner frame compnnpnts 12 do extend on both ~i-des insignificantly farther than conforms with the axial mobility of the rotor 1 in the stator so that, with the start of rotation of the vane cell machine, the vanes emerging d~.ie to centrifugal force immcdiatcLy bring about a centering of the rotor 1 relative to the operating space 15 and the same is retained in tht case of lacki~ig axial forces also without any additional friction on the vanes g, fhe drive and power take-off connection of the vane cell machine is effected by means of a shaft 13 projecting into the stator frame 4 and seated there, which is connected by means of a coupling 14 with the rotor in a non-interacting manner.
In the alternative embodiment according to the Figs. b and 7, the rotor 1 is of tubular constructi~nr in which case a stator pivot 16 projects concentrically into the tube aperture. the stator pivot 96 hPing rigidly connected with the other stator components, ey means of this construction the hydraulic operai-ing pressure within the area of the tube slots does not become effective an the rotor. The re~-maining hydraulic fortes and thQ radial farces given ri3e to both by weight and friction are partially or completely compensated by means of recesses 17 acted upon by the I
RPR 7 '95 02:,53 +49 40 352415 PAGE.020 07-RPR-1995 07:57 RICHTER & PARTNER +49 40 352415 5.21 2~1~3'~1~
_ ZQ _ hydraulic operating pressure on the surface of the con-centric stator pivot 16 in pumps in the area of the nar-rowing vane Cells and in motors in the area of the ex-panding vane cells in denenriance U~1011 the size and the position of the recesses.
whereas in the embodiments described in the foregoing the filling of the expanding vane cells takes place sub-stantially tangentially from the outside, in the embodi-ment depicted in the Figs. 8 and 9, an intake connection is provided on the stator pivot 16 Which is constructed so as to be hollow up to the end of the operating space width 2Q.. This stator is provided with a window in the operating area 15 of the expanding vanes 9, in which case;
in the vanes 9 and./or in the rotor 1, radial recesses. 10 and 11 ars provided, through which the expanding vane w ells' are filled with the assistance of the centrifugal force. The recesses 10 and 11, when viewed in the direc-tion of rotation, are located on the rear of the vanes and/or in the rotor immediately behind the vanes.
The vane pump depicted in the Figs. 10 and 11 is, substan-tially comprised of a rotor 919 mounted on a hollow shaft 110 i~~the forrti of an inner.frame 100, which is disposed, so as to be rotatable and surrounded by the latter in its stator 112. The stator 112 may - as can be gathered from the Fig. 10 -- be of two-piece construction, more particu-larly with a structural element 113 integrated with the hollow ~h~aft 11Q. The rotor 919 p~ssrssrs, outside tire operating area determined by the vanes 124 Cfig. 10), in each case lateratly frm~ these, a reduced diameter and, with it-s outer shell surface, bears sealingly against the stator innrr~ shell. In each case, between the front ends 114 and 115 of the rotor, a gap 116 or 117 is formed re~-lative to the o~ruvsitely located front end of the stator, RPR 7 '95 02:54 +49 40 352415 PAGE.021 07-RPR-1995 07:57 RICHTER & PRRTNER +49 40 352415 S.22 which is pressurized. By way of example, a~ axial bore 118 and a radial bare 118' ensure.a pressure equalization between the gaps 116 and 117. On the drive side and on the power take-off side, the rotor is connected either direct or by means of a non-depicted coupling, with a shaft 119 which is supported so as to be sealed in the stator frame or rotatably in the drive or in the power take-off means. The hollow shaft 11Q is constructed in the form of a front-end intake aperture which is ac-cessible in the direction of the arrow 12E} which commu-nicates via a window opening 121 of the hollow shaft by means of pertinent recPSCes of the rotor with radialLy extending groove-like recesses 112 in the rotor and re-rPSSes 173 in the vanes_ The vanes 124 are Located in radial slots 1Z5 of the rotor 111. The inner shell 100 is provided with depressions 126 on its running surface, which are acted upon hydraulically by the pump delivery pressure of the motor and, in size and position, are dis-posed in such a way that the radial hydraulic bearing load is partially or compCetely compensated.
The space located between the rotor 111 and the stator 112 with the crescent-shaped delivery cells 127 is in each case subdivided by vanes 124, which rotate within the area depicted with the arch 128 with the respective vane end. Over and above that, the stator inner shell possesses additional recesses 129 which project in a crescent-Like fashion over the maximal radial deflection (curve 128).
F3Ptween an expanding and a narrowing delivery cell 127, a transfer area 130 is provided, wherein the vanes 124, when rotating in the direction of the arrow 131, do not execute a radiaC movement.
RPR 7 '95 02:54 +49 40 352415 PRGE.022 07-RPR-1995 07~58 RICHTER & PRRTNER +49 40 352415 S.23 2~4~'~I~
_ 22 _ The vane cell machine according to the Figs. 'IO and 11 functions ac rtptailed below.
The liquid which streams in the direction of the arrow 92U is conducted via the window opening 921 into the groove-like radial recesses 122, 123 radially outwardly into the delivery cells 12r' and is substantially tangen-tially conducted away in the direction of the arrow 132.
The intake of the liquid through the hollow axis and the filling of the expanding vane cells from the inside to the outside is effected in pumps very largely by the energy supply from the drive and, even at high rotational speeds, Leads to low net positive suction heads. It is at the same time possible to provide a hydraulic compen-sation by means of simpte constructions! steps.
In the Figs. 12 and 13, based on the example of the pump, a functionally and, from the viewpoint of production en-gineerin~, particularly advantageous form of the equali-zation of the tadial hydraulic compressive forces acting upon the rotor is illu~tr~tcd.
The tubular rotor 201 is provided with friction bearings in both supports 202 and 203. The single-stroke suction ring 204 constitutes the operating space 20S and is ri-gidly connected with the supports 202 and 203. this three-piece externally cylindrical stator is inserted with a gap 206 which carries liquid or which can be passed through by liquid into the pump housing 207 and sealed e.g.
with the aid of sealing rings 208 at both ends relative to the pump housing. The pressure vent 209 located in the suc-tion ring, in the course of its passage to the pertinent outlet connection piece 218 of the housing 207 arts upon the gap 206 with the respective operating pressure of the pump.
RPR 7 '95 02:55 +49 40 352415 PRGE.023 07-RPR-1995 07:58 RICHTER & PRRTNER +49 40 352415 5.24 21~3'~1~~
_ 23 Located opposite the radial hydraulic compressive farces acting upon thp rntnr, approximately in the direction of the Line of intersection of Fig. 12, oneor several radial bores Z10 are disposed in the supports 2D2 and 2D3, which allow antagonistic compressive forces within the bearing areas to became effective upon the rotor and which tend to a partial or complete pressure balance.
The stator frame 213 is fitted in a contactless fashion, but with a narrow gap, into the internal diameter of the rotor 201. Via the intake bore 21~ of the stator frame 213 which is continuous to the drive side and the window 215 within the area of the expanding vane cells, the fil-ling of the Same is effected. The input pressure is ef-fected via the through bore 214 and the bore Z16 on both front ends of the rotor.
In order to restrict the hydraulic radial pressures very largely to the operating area, i.e. the axial length of the suction ring, the bearings, within the circumferential effective area of the hydraulic radial compre~~ive force, are provided with recesses 211 which, via the gap 217 and the bores 214 and 218, communicate with the low-pressure side so that, within the area of the recesses 211, only a Short bearing length 212 rembins which is adequate for sealing and support.
The hydraulic operating pressure acts through the slots 217 without constituting a load on the rotor, on the stator frame direct and, in addition, the gap between rotor and stator frame is acted upon by pressure via the rotor slots, which contributes to a further partial pressure equaliza-tion.
RPR 7 '95 02:55 +49 40 352415 PRGE.024
metric ConStruCtiOn.
Moreover, rotary piston pumps are known e.g. from the D~-AS
12 36 64'!. TharP, in a ~tatnr hof(.~~r sp2ca of rnnstant dia-~
meter, a cylindrical revolving rotor with a plurality of substantialCy radiaC sCots, in which vanes are sliding, is supported, in which case, by means of a pertinently wavy configuration of the cross-sectional contour of tho stator cavity, several delivery cells are formed between the stator and the rotor to and from which the pumped or operating me-dium is suppCied and removed via tangentially terminating ducts, of which intake or Low-pressure side ducts are in each case bores located on one side of the vane that lead to a concentric, hollow rotor space, while the ducts on the high-pressure side located in each case on the other side of each vane, coromurri~atr irr each case in d corrrirwous lon-gitudinal duct of the rotor allocated to each vane. The lon-gitudinal ducts communicate in turn with an annular groove which communicates with the high~pressure side of the pump or the motor.
pPR 7 '95 02:47 +49 40 352415 PAGE.004 07-RPR-1995 07:50 RICHTER & PRRTNER +49 40 352415 5.05 _ 2143~1~
For the direct feeding and removal of the pumped medium it is also known to provide duw leading into or vut from the delivery cells, which will then have tv communicate in turn with ducts in a sLaLionary housing portion. The use of such rotor ducts is regarded as advantageous in as far as e.g. one orwrvr~e operating spacefs) exist bezween the rotor circumferential area and the circumferential wall of Lhe stator hollow space since, when correspondingly many intake and discharge apertures are disposed in the stator walls, Large parts of the operating spaces are unable to act as areas within which the displacement cells are sealed oft from the inlet side and the pressure side, unless a great many pumping operations are planned which once again diminish the utilizable operating space and give rise to substantial friction losses.
In order to be able to construct the feeding and the dis-charging ducts in the rotor so as to possess an adeauate Width but, on the other hand, to avoid too great a weake-ning of the rotor owing to the ducts and, finally. to pre-vent an axial thrust from pressure ducts having an adverse effect on the pressure, it is further proposed in the DE-AS
1~ 3b 941 that, in the form of delivery~side ducts on the respective side of each vane, sQVaral grnnvec he machined , into the relevant wall of the associated rotor slot, in which r..ase, furthermore, on both sides of the rotor, one annular groove each be disposed in the side walls of the stator which face the rotor front walls, into which thr delivery-side longitudinal ducts of the rotor terminate, while the annular graove~ arc in communication with pres-sure connections of the pump or of the motar_ The rotor hollow space into which the towwpressure-side bores lead, is a part of a concentric longitudinal bore of a shaft con-nected to the rotor. However, thisrotGry piston pump i5 RPR 7 '95 02:47 +49 40 352415 PRGE.005 07-RPR-1995 07:50 RICHTER & PRRTNER +49 40 352415 S.06 ~143'~~.~
expensive to construct on account of the numerous radial bvr-es - also outside the vane slots - as well as owing to the great number of outlets.
The U5-A-3,361,076 describes a vane cell motor with a ro-tor supported in a stator, said rotor being slatted within its operating area which, screwed together with each other is comprised of a accommodation space for the vanes, a terminal piece and a flow sleeve. The accommodation for the vanes comprises a terminal flange which, lust like the terminal piece, projects radially over the external dia-meter of the stator element and thereby laterally limits the hydraulic operating area. The accommodation for the vanes is, in the axial direction, outwardly construcrpd in the form of a shaft, supported on ball and roller bea-~
rind elements and sealed in the stator and caused to pass out from the vane cell motor for receiving a driving ele-ment. In thlS l'.r7SP the terminal piece possesses only a short shaft shoulder for accommodating the rolling bearing.
The filling of the vane cells is effected in this case from the inside to the outside while a rotor is provided shove the slotted area uF,ich is extended to both sides having a greater external diameter for the positively lo-cking axial centering of a displaceable lifting ring. Both extensions are mounted by means of tapered roller bearings, 3Lao for the absorption of radial anil axiel for-crs, in the housing while the one extension is passed out of the machi-ne in the form of a rotationally Sealed shaft for the drive connection. Pressure-adjustable overflow valves limit the gap pressure witlnin the gap areas arising due to leakage caused by the operating pressure which, at the same pres-sure via l,Irese gap areas up to the seal diameter, brings about a pressure equalization. The axial hydraulic forces across the rron-pressure-equatized Surface area below the sealing diameter are absorbed by the bearings. In this vane yell molar the vanes are spring~-loaded, whereby a high RPR 7 '95 02:47 +49 40 352415 PRGE.006 07-RPR-1995 07:51 RICHTER & PARTNER +49 48 352415 5.07 - ~I~3'~~~
degree of proneness exists in so far as, when the spring pressure falls off, it is no Lnnrder Assured that, in the operative state, it wilt be possible for the vanes to be brought to the inner wall of the stator, in addition, a rotation of the rotor to the stator has to be ensured in Sur:h a way that a retracting of the vanes into their re-ceiving slots in the rotor against a spring pressure is possible_ To this is added the circumstance that the three-part rotor is constructed neither to be shiftless nor in a tubular manner, which does not pusse55 a vane slot which is continuous from the internaE to the ex-ternal diamettr since the internal diameter is formed by the ftow sleeve. The pressurized space of the stator does not contritrute within the area of the rotor extensions to the compensation of radial forces which, from the opera-ting Nressure, can only become effective onto the rotor portion. The same pressure present in the gaps, adjustably limited by means of valves, avoids for the effective areas going beyond the seating diameter axial forces by means of thisd pressure, it does, however, leave the effective surfaces below the sealing diameter axially uncompensated pressure-wise.
In the US-A-3,153,384, a vane cell pump is described, in which, on a common shaft and axially rigidly tightened, two rotors separated by a spacer, two supporting rotors.
two spacing sleeves and two equalizing disks are disposed.
The Supporting rotors are Supported in a friction bearing in bushings in a housing, in which, for the compensation of radial hydraulic forces, pprtinpnt recesses acted upon by operating pressure are disposed. The operating pressure is conducted through external pipelines from the pressure side to the recesses in the bearing bushes. In this vane Gall pump, effective Surface areas acted upon by operating pressure and directed against the rotor are provided in RPR 7 '95 02:48 +49 40 352415 PAGE.007 07-RPR-1995 07:51 RICHTER & PRRTNER +49 40 352415 5.08 21~37~9 the stator. For the compensation of radial hydraulic for-ces in vane cell machines or vane pumps possessing a rotor supported in friction bearings it is accordingly known to provide, in the loaded friction bearing area, effective surface areas acted upon by operating pressure.
It is disadvantageous ir, this vane purrn that adJitional gap entry edges acted upon by operating pressure and pos-sessing relatively short gap lengths and that thereby the efficiency is impaired by increased volumetric losses.
Moreover, the formation of hydrodynamic pressure suppor-ting surfaces is prevents to a very large extent since the narrow gaps necessary for this within the supporting bea-ring area are eliminated by the effective areas acted upon by operating pressure which are planned at this point.
According to the FR-A-73 95 435, a vane cell machine is known, in which, in a stator, a shaft-journalled rotor ro-tates, wherein the inner shell surface of the stator pos-sesses three pitch-cirular recesses, whose wall areas are run in such a way that the combination area of two wall areas each comes to be located in the external rotational area of the rotor. The rotor is provided with radially pro-ceeding guide slots for four vanes, in Which case the dis-position of the guide sln*s is such that two oppositely Located guide slots each are, relative to a theoretical radius line, ars raciprocaCly staggered with the result that only one vane each comes to be lie in each indivi-dual pitch-circular reec~~. A slide or journal bearing lubricated by delivery liquid of the rotor shaft is not provided in this case.
The DE-A~2 022 $49 describes a valueless rotary piston pump with circularly rotating vanes assuming the delivery, which is comprised of a stationary sectional axis which determines the position of the vanes in the individual operating phases, wherein the hollow drive shaft is RPR 7 '95 02:48 +49 40 352415 PRGE.008 07-RPR-1995 07:52 RICHTER & PRRTNER +49 40 352415 5.09 - 2i~37I~
eccentrically supported in the pump casing in such a way that, within the operatirry area, an adequate delivery cross-sectionremains between the hollow shaft and the ca-sing and, within the separating area, the hollow shaft rests sealingly against the casing and thus takes charge of the separation between pressure and intake side. The vanes, which bring about the drawing in by suction and the delivery of the medium, project in the operating area so far from the hollow shaft that they reach the casing wall.
The drive shaft is in this case constructed in the form of a hollow shaft, in which the vanes are supported so as to be radially displaceable and are supported on a rigidly dislocated sectional axis, xhile the hollow shaft is supw ported in the pump casing. A shaftless support is thus not provided.
In the rotary piston pumps known according to the state of the art which are provided with vane cells for liauids, which are employed in the form of delivery pumps, an opera-tion far liauids with elevated vapor pressure and without a positive supply feed owing to the net positive suction head rapidly ring with thp rotational seed, an operation with economic drive speeds of e.g. 1450 min-~ and higher is no Lnngpr ~nRRihlp.
The volumetric degree of effectiveness and the dry intake Capacity (with an empty pump) of vane pumps is determined by the gap losses, whose magnitude - with the presupposi-tion of the same delivery product, the same manufacturing precision and pressure differential - depends on the lengths of the gaps. That is why, with a comparable pump flow, sLowiy rotating pumps with a correspondingly great cyclic pump volume and pump Lengths possess poorer volumetric degrees of effectiveness and a lower dry intake capacity RPR 7 '95 02:49 +49 40 352415 PRGE.009 07-APR-1995 07:52 RICHTER & PARTNER +49 40 352415 5.10 - _ 9 _ 21~3~1~
than rapidly rotating pumps with a correspondingly smaller CyCllc pump volume and gap lengths. These technical con nections mentioned, on account of the necessary reduction of the rotary speed by the net positive suction head limit also the possibilities for the constructional improvement of the volumetric effectiveness and of the dry intake ca-pacity.
Furthermore, rotary piston pumps for liquids, as a result of the Large projection area formed by rotor and projecting vanes and acted upon by the pressure differential, call for sturdily dimensioned shafts and bearings, unless the rotary piston pumps are constructed in the form of double~stroke vane pumps or motors which each possess two intake and disw charge apertures for the liquids, a step which is costly from a product engineering aspect and which, in the case of pumps, leads to an increase, and with this, to a dete~
rioration of the net positive suction head.
TECHNICAL PROBLEM~~ TECHNICAL SOLUTION, AbVANTAGES
That is why it is the technical problem of the present in-vention to further develop the known vane pump in such a way that a complete or at least extensive balance of the radial and axial fort a is provided, in which, with a view to a longer useful service fife, the wear should be miniw mined and a greater degree of effectiveness ectnieved. So far as vane cell machines are considered as volumetric meters, the measuring accuracy is intended to be improved in a like manner. It is further the object of the present invention Lo ~xparTd the possibilities of operational appl y cation in the form of a pump by means of a reduction of the net Nvsitive suction head and to improve the degree of effectiveness in the machine employed in the form of a Nump. In addition, it is Lhe Object of the present in-vention to also improve the hydraulic axial and radial APR 7 '95 02:49 +49 40 352415 PAGE.010 stresses at least in part or altogether by means of con-structional steps which do not involve any great construc-tional effort or costs.
Thus this invention seeks to provide a vane pump for liquids comprising a stator having an inner wall surface and a hollow center, a shaftless and tubular rotor mounted on the hollow center of the stator, the rotor having in a vane area thereof radially extending vane slots, the vane slots extending from an inner diameter to an outer diameter of the rotor, a vane being slidably mounted in each vane slot, the vanes being configured to bE: pressable against the inner wall surface of the stator when a compressive force is applied to the vanes, radial recesses being defined in at least one of the vane slots and the vanes, crescent-shaped delivery cells with an increasing or decreasing width being formed between the outer diameter of the rotor, the inner wall surface of the stator and the adjacent vanes, the rotor having at both ends thereof extensions protruding beyond the vane area, the extensions having a diameter equal to or smaller than the outer diameter of the rotor in the vane area, the extensions being received in the stator so as to form a gap seal, wherein the liquids enter axially through the hollow center of the stator and radially through a window defined in the hollow center of the stator in an area of a delivery cell with an increasing width and through the radial recesses into the delivery cell with the increasing width, the hollow center of the stator having recesses adjacent the extension of the rotor, wherein the stator recesses are configured to receive an operating pressure and the recesses having a location and size configured to partially or completely compensate radially directed hydraulic and weight-related forces.
- l0A -According to this the invention consists in that the rotor of the vane cell macshine is constructed so as to be devoid of a shaft and of tubular configuration and in that both sides are extended beyond the operating area determined by the vanes and supported with the extensions in the exter-nal stator and in that it possesses continuous vane slots from the internal to the external diameter and in that the stator frame, within the area of the rotor extensions, possesses on the surface hydraulically effective areas;ac-ted upon and/or relieved by the operating pressure directed against the rotor for the at least partial compensation or avoidance of radially occurring forces. However, in a shaft-less rotor extendingi beyond the operating area toeards both sides, the operating pressure becomes effective in the bearing gaps rotor/external stator located there, which results in further bearing loads. In comparison with it, by means of recesses (effective areas) in the stator frame relieved of the operating pressure, this radial load por-tion is significantly reduced. The tubular extensions on both sides are lubricated with delivery liquid due to the pressure-dependent gap leaks and slidingly supported in the stator.
The vane cell machine is, according to a further embodi-ment, provided with an inlet for the liquid through a hol-low central stator, in which case the ducts for filling the expanding vane cells are formed by radial recesses in the vanes and/or in the vane slots and the concentric sta-tor possesses on its surface effective areas acted upon 07-RPR-1995 07:53 RICHTER & PRRTNER +49 40 352415 5.12 - 2143 rllg by operating pressure and directed against the rotor for the at Least partial compensation of radial. farces, it being possible to sub~itute the recesses with small bores acted upon by operating pressure Which produce, in the bearing or supporting gaps, rotor/external stator, large effective araas directed against tha rotor_ This step is simpler in the fabrication, results in comparatively Lower gap losses and thereby improves the volumetric de-gree of effectiveness. Advantageously, this vane call ma-chine i~ of ~implc construction, a comparatively expansive additional mounting of the shaft and the frictional forces arising t,erefrom are avoided trom the outset, just as axial and radial hydraulic forces are minimized.
In this case the radial ducts for filling the delivery cells are formed by radial recesses in the vanes andlor in the vane slots which proceed continuously from the exter-nal diameter to the longitudinal bore in the form of a shaftCess rotor projecting on both sides beyond the opera-ting area determined by the vanes, while the liquid enters axially through the hoCCou rotor axis and the fiEling of the of the expanding delivery cells takes place in the the radial direction through a window in the rotor axis and, in the further course, through recesses in the rotor slots andlor in the vanes.
The rotor portion which projects beyond the c~peratiry erea or the rotor portions on both sides are rotatable against the rvtor~, bul ar-a fitted in sealingly_ In pumps, in res-pect to the net positive suction head, a significant advan-laye results since solely zhe introduction lasses of the liquid into the rotor slots are to be associated with the rrrl positive suction head and the further pressure lasses up to the filling of the vane ceCls and the speed increase of the liquids connected with this in conjunction with the RPR 7 '95 02:50 +49 40 352415 PRGE.012 07-RPR-1995 07:54 RICHTER & PRRTNER +49 40 352415 5.13 - ~~4~71~
centrifugal -force have to be produced energyNise by the drive. The radial filling of the vane cells from in~idc via the rotor slots, over and above that, has the advan-tage that the inr.lusion of the stroke volume of the vanes in the rotor slots takes place in the cyclic operating volume of the pump or of the motor without a special fil-ling operation for this stroke volume against the centri-fugal force, as i~ necessary Hhen the vane cells erw fil-led tangentially or axially from the outside according to the state of the art. The rotor axis serving at the same time as liquid intake and as a mounting means for the ro-tor does advantayeuu5ly make possible in pumps and motors a cost-saving realization of the hydraulic, in particular radial, Nressure balance by means of a hydrauW c support against the rotor axis.
Further developments of the invention are described in the subclaims.
The recesses are thus preferably acted upon by the opera-ting pressure given by the liquid ~o that no further pres-sure sources or control means are necessary.
According to a first embodiment, the recesses in the sta-tor shell are located opposite the external rotor casing outside the vane operating area, thus, Nith regard to a vertical area passing through the vane operating area, symmetricalyl disposed. According to an alternative embo-diment, the recesses are located in the shell of a stator pivot Hhich reaches through the concentric opening of a rotor tube and bears against the same in a sealing fa-shion. The last-mentioned embodiment possesses the advan-tage that the recesses may also Lie at the same level as the vane operating area, Nhereby a reduction in the over-all height may possibly result. Combinations of said em-bodiment are likewise possible.
RPR 7 '95 02:51 +49 40 352415 PRGE.013 07-RPR-1995 07:54 RICHTER & PRRTNER +49 40 352415 5.14 '.
According to a further construction of the invention, the rvtar portion Which projects beyond the vane operating area possesses an identical or reduced externs! diameter in comparison with a diameter in the vane operating area.
A reduced diameter outside the vane operating area pos-sesses the advantage that, in the course of the vane cell machine operation, the rotor receives an axial centering.
Nhen the vane cell machine is inoperative, the vanes imy merse into the rotor slots whereby, in a rotor poSSeSsing a continuous constant diameter, axial displacements may be possible. In the rotor extended with reduced diameters which otherwise is axially freely movable, the diameter increases serve to center the motor in relation tn thp operating area, in which case it is possible to put up.
with the afaredescribed disadvantage of thp un;lateral~ly greater effectiveness of the hydraulic pressure by bearing against the oppositely Iw ated side since the effective area is kept smalE by a minor difference in diameter. By means of this rotor Centering in relation to the operating space, between the front end areas of the rotor and the stators on both sides, the gap for a hydrostatic force balance at the same pressure is ensured.
In the rotor extended with the same diameter towards both sides, the requisite centering of the rotor relative to the operating area is effected by the vanes. The space in the guide slots underneath the vanes communicates with the vane cell located before the same in the direction of ro-tation, e.g. by means of radial recesses in the vane and!
or in the rotor. Since, in the inoperative state of the vane cell machine, the vanes moved outwardly by centrifu-gal force when operative, can be immersed into the rotor and the freely movable rotor may be axially and unilate-rally displaced against the front-end stator and because RPR 7 '95 02:51 +49 40 352415 PAGE.014 07-RPR-1995 07:54 RICHTER & PARTNER +49 40 352415 5.15 214~7~.~
this may, uhen the pump is started up, hinder the vanes from emerging or may even lead too tilting or wedging within the area of the vanes that are not acted upon by the pressure differential, the stator parts which late-rally delimit the operating space are slightly chamfered in thr dirwtivw Cvkdocls Lhe axis of rwtdtiun str ~s to extend the operating space. These chamferings are carried a little farther on both sides than confiorms to the axial mobility of the rotor in the stator so that, when the vane cell machine commences to rotate, the vanes emerging due to the centrifugal force bring about an immediate cente-ring of the rotor relative to the operating space and this is retained because of lacking axial forces also wi-thout any additional friction on the vanes.
In a special construction according to the invention of the vane cell machine, the rotor is constructed so as to be tubular and possesses a longitudinal bore in which an even number of vane slots terminate openly and in which, the in each case diametrically opposed vanes are rigidly interconnected or of one-piece construction.
However, alternatively to this, the rotor can, when of tubular construction, also receive in the tube apertures a stator pivot which is hollow on the inside and, within the area of the slots passing through the rotor for the displaceable vanes, possesses a window and in which the vanes andlor the rotor slots possess radial recesses. This Corm of construction makes d partial balance of the radial hydraulic fortes on the rotr possible.
By preference, the rotor, at its front ends, is coupled to an axially fixated shaft as drive connection or as power takeoff connection, in whit case the shaft is accommodated in the stator frame.
APR 7 '95 02:51 +49 40 352415 PAGE.015 07-RPR-1995 07:55 RICHTER & PRRTNER +49 40 352415 5.16 _ 15 Thus, preferably within the filling area of the delivery ceELs, the stator bore is executed acroe~ the area which passes through the maximal radial deflection of the vanes radially towards thQ outside in a pitch circlC so that, by means of the recess provided hereby, a communication of two ar more delivery cells exists. This sm p facili-tates the filling of the delivery cells.
Furthermore, the stator frame transitional area between two delivery cells is by preference concentrically disposed with regard to the axis of rotation so that the vanes, when rotating in this area acted upon by a pressure dif-ferential, do not execute any radial movement.
According to a further canstrurtion, the outer shell of the inner stator possesses depressions which can be acted upon by tha p«mp del.ivery pressure or by the input pres-sure of the motor for the at least partial compensation of the radial hydraulic bearing load. By means of this con-structivnaLLy simply effected step it is possible to dis-pense with a ~turdsly dimensioned mounting or support.
The rotor portions which project over the vane operating area preferably possess a reduced external diameter in comparison with the rotor diameter in the vane operating area. Hereby the rotor is axiaEly centered during the ope-ration.
When the rotor is inoperative, the vanes sink into the rotor slots. which may result in an axial displacement of the rotor that does not possess a reduced external diame-ter. In order to pre~ant, when the rotor is restarted, that the vanes become wedged outside their operating area with the stator inner shell, thQ stator shell which late-ratly delimits the vane operating area, within the area of tha non-pressurized vanos, is sonically configured so RPR 7 '95 02:52 +49 40 352415 PRGE.016 07-RPR-1995 07:55 RICHTER & PRRTNER +49 40 352415 S.17 - 1~ - ~~~J~~~
that the vanes slide constrainedly guided into the axially centered position when starting up.
According to a further embodiment, the rotor is connected direct or by means of a coupling on the front side Located opposite the intake aperture to a shaft in the form of a drive or power- take-off means, the shafit being sealingly inserted into the stator shell.
BRIEF DESCRIPTION OF THE pRAWINGS
Embodiment examples of the invention are explained below with the aid of the drawings. This F i g. 1 shows a vertical section through a vane cell machine, F i g. ~ shows a verticalsection in the direction of Line II - II in Fig. 1;
F i g. 3 shows a partial view of a Longitudinal section through a vane cell machine with canically con-figured transitional areas between the Vane operational area and the adjacent stator frame;
F i g. ~+ shows a sectional view through a vane cell ma-chine having a tubular rotor, whose diametri-cally opposed vanes are interconnected;
F i g. 5 shows a vertical section in the direction of Line V - V in Fig. 4;
F i g. 6' shoos a sectional vicw of a vane cell machine with a rotor possessing a concentric bore into which a stator pivot is fitted;
F i g. 7 shows a vertical section in the direction of Line VII - UII in Fig. 6;
RPR 7 '95 02:52 +49 40 352415 PRGE.017 07-APR-1995 07:56 RICHTER & PARTNER +49 40 352415 S.18 - 2143r119~
1~ -F i g. 8 shows an embodiment in which the concentric sta-tor to the intake connection is constructed, in a vertical section;
F i g. 9 shows a vertical section in the direction of dine IX - IX in Fig. $;
F i g. 10 shows a longitudinal cross-section of a further embodiment of a vane cell machine, and F i g. 11 shows a cross-section at the level of the vane ope-rating area vertically to the section as per Fig. 10, F i g. 1Z shows a vertical section through the vane cell maehine~ and F i g. i3 shows a vertical section in the direction of Line XIII - XII in Fig. 12.
DETAILED i)ESCRIpTION OF THE INVENTION AND THE BEST WAY OF
REALIZING THE INVENTION
The vane tell machine is preferably constructed in the form of a single-strske vane pump which, in the embvdimenC slnourn in the Figs. 1 and Z, is in the form of a pump, possesses a shaftless rotor 1 whivh, in the axial direction may possess either an external diameter 2 with a uniform circumference as irr the vane operating area 15, or a circumference 3 redu-ced in contrast thereto. Outside the vane operating area, the rotor 1 is fitted into a stator 4 so as to be sealingly sup-ported. Within this fitting-in area the stator possesses re-cesses 5 which, according to their position arid size, are constructed in such a way that the operating pressure of the liquid acting herein results in a partial or complete hydrau-lic force balance also when taking the frictional and weight related forces into consideration. In the embodiment depicted APR 7 '95 02:53 +49 40 352415 PRGE.018 07-RPR-1995 07:56 RICHTER & PRRTNER +49 40 352415 5.19 ~~ ~ 214371 in Fig. 2, the recesses 5, when viewed in the axial direc-tion, arc disposed in front of on t~ehind the vane operating area 75 and symmetrically thereto.
The vertical front end areas or spacing differences b in diameter difference existing in the top half of Fig. 2 of the rotor 9 serve at the same time for the centering of the rotor, whereby, in operation, an the front end, equal gaps 7 result between the rotor front end and the, in each case, oppositely located stator front end. In the rotors extended with reduced diameters which are otherwise freely movable, these diameter differences 6 serve to center the rotor relative to the operating space, in which connection the previously described disadvantage of the unilaterally greater effectiveness of the hydraulic pressure by bearing against the opposite side is acceptable since the front end area 6 in the form of an effective area is kept small by means of a slight difference in diameter. By means ~f this centering of the rotor relative to the operating space, betNeen the front end areas of the rotor 1 and the stator 4 on both sides, the gaps 7 fore hydrostatic force compensation at the camp pressure are ensured_ The rotor 1 possesses slats 8, each of which proceeds ra-dially, in which the vanes 9 are slidingly guided. The space in the guide scats 8 underneath the vanes 9 communi-cates in each case with the vane cell located in front of the same in the direction of rotation, in the present case by means of radial recesses '10 on the vane andlor recesses 91 in the rotor. Since, in the inoperative state of the vane cell machine, as depicted in Fig. 3, the vanes 9, which, in operation, are moved outwardly by centrifugal force, can be immersed in the rotor and the freely movable rotor 1, whose diameter has not been reduced, may be dis-placed axially on one side against the front end of the APR 7 '95 02:53 +49 40 352415 PRGE.019 07-RPR-1995 07:56 RICHTER & PRRThIER +49 40 352415 5.20 stator 4, whereby, when the vane cell machine is started up, the vanes9 are prevented from emerging, which may lead to as much as a wedging of the Vanes on the stator inner wall in question; within the area of the vanes 4 which are not acted upon by differential pressure, the stator inner frame components 12 Laterally delimiting the operating space are constructed in the direction towards the axis of rotation so as to be conical ar slightly r.hamfered, thus expanding the working space. These conical or chamfe~
red stator inner frame compnnpnts 12 do extend on both ~i-des insignificantly farther than conforms with the axial mobility of the rotor 1 in the stator so that, with the start of rotation of the vane cell machine, the vanes emerging d~.ie to centrifugal force immcdiatcLy bring about a centering of the rotor 1 relative to the operating space 15 and the same is retained in tht case of lacki~ig axial forces also without any additional friction on the vanes g, fhe drive and power take-off connection of the vane cell machine is effected by means of a shaft 13 projecting into the stator frame 4 and seated there, which is connected by means of a coupling 14 with the rotor in a non-interacting manner.
In the alternative embodiment according to the Figs. b and 7, the rotor 1 is of tubular constructi~nr in which case a stator pivot 16 projects concentrically into the tube aperture. the stator pivot 96 hPing rigidly connected with the other stator components, ey means of this construction the hydraulic operai-ing pressure within the area of the tube slots does not become effective an the rotor. The re~-maining hydraulic fortes and thQ radial farces given ri3e to both by weight and friction are partially or completely compensated by means of recesses 17 acted upon by the I
RPR 7 '95 02:,53 +49 40 352415 PAGE.020 07-RPR-1995 07:57 RICHTER & PARTNER +49 40 352415 5.21 2~1~3'~1~
_ ZQ _ hydraulic operating pressure on the surface of the con-centric stator pivot 16 in pumps in the area of the nar-rowing vane Cells and in motors in the area of the ex-panding vane cells in denenriance U~1011 the size and the position of the recesses.
whereas in the embodiments described in the foregoing the filling of the expanding vane cells takes place sub-stantially tangentially from the outside, in the embodi-ment depicted in the Figs. 8 and 9, an intake connection is provided on the stator pivot 16 Which is constructed so as to be hollow up to the end of the operating space width 2Q.. This stator is provided with a window in the operating area 15 of the expanding vanes 9, in which case;
in the vanes 9 and./or in the rotor 1, radial recesses. 10 and 11 ars provided, through which the expanding vane w ells' are filled with the assistance of the centrifugal force. The recesses 10 and 11, when viewed in the direc-tion of rotation, are located on the rear of the vanes and/or in the rotor immediately behind the vanes.
The vane pump depicted in the Figs. 10 and 11 is, substan-tially comprised of a rotor 919 mounted on a hollow shaft 110 i~~the forrti of an inner.frame 100, which is disposed, so as to be rotatable and surrounded by the latter in its stator 112. The stator 112 may - as can be gathered from the Fig. 10 -- be of two-piece construction, more particu-larly with a structural element 113 integrated with the hollow ~h~aft 11Q. The rotor 919 p~ssrssrs, outside tire operating area determined by the vanes 124 Cfig. 10), in each case lateratly frm~ these, a reduced diameter and, with it-s outer shell surface, bears sealingly against the stator innrr~ shell. In each case, between the front ends 114 and 115 of the rotor, a gap 116 or 117 is formed re~-lative to the o~ruvsitely located front end of the stator, RPR 7 '95 02:54 +49 40 352415 PAGE.021 07-RPR-1995 07:57 RICHTER & PRRTNER +49 40 352415 S.22 which is pressurized. By way of example, a~ axial bore 118 and a radial bare 118' ensure.a pressure equalization between the gaps 116 and 117. On the drive side and on the power take-off side, the rotor is connected either direct or by means of a non-depicted coupling, with a shaft 119 which is supported so as to be sealed in the stator frame or rotatably in the drive or in the power take-off means. The hollow shaft 11Q is constructed in the form of a front-end intake aperture which is ac-cessible in the direction of the arrow 12E} which commu-nicates via a window opening 121 of the hollow shaft by means of pertinent recPSCes of the rotor with radialLy extending groove-like recesses 112 in the rotor and re-rPSSes 173 in the vanes_ The vanes 124 are Located in radial slots 1Z5 of the rotor 111. The inner shell 100 is provided with depressions 126 on its running surface, which are acted upon hydraulically by the pump delivery pressure of the motor and, in size and position, are dis-posed in such a way that the radial hydraulic bearing load is partially or compCetely compensated.
The space located between the rotor 111 and the stator 112 with the crescent-shaped delivery cells 127 is in each case subdivided by vanes 124, which rotate within the area depicted with the arch 128 with the respective vane end. Over and above that, the stator inner shell possesses additional recesses 129 which project in a crescent-Like fashion over the maximal radial deflection (curve 128).
F3Ptween an expanding and a narrowing delivery cell 127, a transfer area 130 is provided, wherein the vanes 124, when rotating in the direction of the arrow 131, do not execute a radiaC movement.
RPR 7 '95 02:54 +49 40 352415 PRGE.022 07-RPR-1995 07~58 RICHTER & PRRTNER +49 40 352415 S.23 2~4~'~I~
_ 22 _ The vane cell machine according to the Figs. 'IO and 11 functions ac rtptailed below.
The liquid which streams in the direction of the arrow 92U is conducted via the window opening 921 into the groove-like radial recesses 122, 123 radially outwardly into the delivery cells 12r' and is substantially tangen-tially conducted away in the direction of the arrow 132.
The intake of the liquid through the hollow axis and the filling of the expanding vane cells from the inside to the outside is effected in pumps very largely by the energy supply from the drive and, even at high rotational speeds, Leads to low net positive suction heads. It is at the same time possible to provide a hydraulic compen-sation by means of simpte constructions! steps.
In the Figs. 12 and 13, based on the example of the pump, a functionally and, from the viewpoint of production en-gineerin~, particularly advantageous form of the equali-zation of the tadial hydraulic compressive forces acting upon the rotor is illu~tr~tcd.
The tubular rotor 201 is provided with friction bearings in both supports 202 and 203. The single-stroke suction ring 204 constitutes the operating space 20S and is ri-gidly connected with the supports 202 and 203. this three-piece externally cylindrical stator is inserted with a gap 206 which carries liquid or which can be passed through by liquid into the pump housing 207 and sealed e.g.
with the aid of sealing rings 208 at both ends relative to the pump housing. The pressure vent 209 located in the suc-tion ring, in the course of its passage to the pertinent outlet connection piece 218 of the housing 207 arts upon the gap 206 with the respective operating pressure of the pump.
RPR 7 '95 02:55 +49 40 352415 PRGE.023 07-RPR-1995 07:58 RICHTER & PRRTNER +49 40 352415 5.24 21~3'~1~~
_ 23 Located opposite the radial hydraulic compressive farces acting upon thp rntnr, approximately in the direction of the Line of intersection of Fig. 12, oneor several radial bores Z10 are disposed in the supports 2D2 and 2D3, which allow antagonistic compressive forces within the bearing areas to became effective upon the rotor and which tend to a partial or complete pressure balance.
The stator frame 213 is fitted in a contactless fashion, but with a narrow gap, into the internal diameter of the rotor 201. Via the intake bore 21~ of the stator frame 213 which is continuous to the drive side and the window 215 within the area of the expanding vane cells, the fil-ling of the Same is effected. The input pressure is ef-fected via the through bore 214 and the bore Z16 on both front ends of the rotor.
In order to restrict the hydraulic radial pressures very largely to the operating area, i.e. the axial length of the suction ring, the bearings, within the circumferential effective area of the hydraulic radial compre~~ive force, are provided with recesses 211 which, via the gap 217 and the bores 214 and 218, communicate with the low-pressure side so that, within the area of the recesses 211, only a Short bearing length 212 rembins which is adequate for sealing and support.
The hydraulic operating pressure acts through the slots 217 without constituting a load on the rotor, on the stator frame direct and, in addition, the gap between rotor and stator frame is acted upon by pressure via the rotor slots, which contributes to a further partial pressure equaliza-tion.
RPR 7 '95 02:55 +49 40 352415 PRGE.024
Claims (7)
1. A vane pump for liquids comprising a stator having an inner wall surface and a hollow center, a shaftless and tubular rotor mounted on the hollow center of the stator, the rotor having in a vane area thereof radially extending vane slots, the vane slots extending from an inner diameter to an outer diameter of the rotor, a vane being slidably mounted in each vane slot, the vanes being configured to be pressable against the inner wall surface of the stator when a compressive force is applied to the vanes, radial recesses being defined in at least one of the vane slots and the vanes, crescent-shaped delivery cells with an increasing or decreasing width being formed between the outer diameter of the rotor, the inner wall surface of the stator and the adjacent vanes, the rotor having at both ends thereof extensions protruding beyond the vane area, the extensions having a diameter equal to or smaller than the outer diameter of the rotor in the vane area, the extensions being received in the stator so as to form a gap seal, wherein the liquids enter axially through the hollow center of the stator and radially through a window defined in the hollow center of the stator in an area of a delivery cell with an increasing width and through the radial recesses into the delivery cell with the increasing width, the hollow center of the stator having recesses adjacent the extension of the rotor, wherein the stator recesses are configured to receive an operating pressure and the recesses having a location and size configured to partially or completely compensate radially directed hydraulic and weight-related forces.
2. A vane pump according to Claim 1 further including a stator casing which laterally delimits a vane operating area, said stator casing being, in the direction of the axis of rotation, conically configured with chamfers so as to expand the operating area, the chamfers being carried further on both sides in correspondence with the axial mobility of the rotor.
3. A vane pump according to Claims 1 or 2 wherein the rotor is of tubular construction and possesses a longitudinal bore, in which an even number of vane slots terminates openly and diametrically opposed vanes are each rigidly interconnected.
4. A vane pump according to Claims 1, 2 or 3 wherein the rotor on each of its front ends, is coupled to an axially fixed shaft in the form of a power drive or power take-off connection.
5. A vane pump according to Claims 1, 2 or 3 wherein the rotor is coupled, on the front end located opposite an inlet aperture, to a shaft serving as power drive or power take-off means.
6. A vane pump according to Claim 1 wherein the crescent-shaped delivery cells are formed with an increasing width.
7. A vane pump according to Claim 1 wherein the crescent-shaped delivery cells are formed with a decreasing width.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE9211768U DE9211768U1 (en) | 1992-09-02 | 1992-09-02 | Vane machine |
| DEG9211768.6U | 1992-09-02 | ||
| PCT/EP1993/002311 WO1994005912A1 (en) | 1992-09-02 | 1993-08-26 | Vane cell machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2143719A1 CA2143719A1 (en) | 1994-03-17 |
| CA2143719C true CA2143719C (en) | 2001-07-17 |
Family
ID=6883305
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002143719A Expired - Fee Related CA2143719C (en) | 1992-09-02 | 1993-08-26 | Vane cell machine |
Country Status (10)
| Country | Link |
|---|---|
| EP (1) | EP0659237B1 (en) |
| JP (1) | JP3129737B2 (en) |
| KR (1) | KR950703124A (en) |
| CN (1) | CN1040786C (en) |
| AT (1) | ATE137306T1 (en) |
| AU (1) | AU684725B2 (en) |
| CA (1) | CA2143719C (en) |
| DE (2) | DE9211768U1 (en) |
| DK (1) | DK0659237T3 (en) |
| WO (1) | WO1994005912A1 (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5545014A (en) * | 1993-08-30 | 1996-08-13 | Coltec Industries Inc. | Variable displacement vane pump, component parts and method |
| EP0650801A1 (en) * | 1993-10-29 | 1995-05-03 | Ing. Büro H. Schellenberg | Pneumatic positioning device |
| AUPO580397A0 (en) * | 1997-03-24 | 1997-04-17 | Baker Medical Research Institute | Positive displacement pump |
| SE9804317D0 (en) * | 1998-12-15 | 1998-12-15 | Gunnar Bjoerk | pulse Pump |
| CN100398824C (en) * | 2004-06-25 | 2008-07-02 | 丁桂秋 | Volumetric vane pump |
| JP4780154B2 (en) * | 2008-07-18 | 2011-09-28 | パナソニック電工株式会社 | Vane pump |
| DE102010022677B4 (en) | 2010-06-04 | 2016-06-30 | Nidec Gpm Gmbh | Vane pump |
| WO2012023426A1 (en) * | 2010-08-18 | 2012-02-23 | 三菱電機株式会社 | Vane compressor |
| CN103001344A (en) * | 2012-10-29 | 2013-03-27 | 无锡金阳电机有限公司 | Shaftless motor |
| RU2554691C1 (en) * | 2014-02-03 | 2015-06-27 | Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский национальный исследовательский технический университет им. А.Н. Туполева-КАИ" | Oscillation generating device |
| FR3033370B1 (en) * | 2015-03-02 | 2017-03-24 | Peugeot Citroen Automobiles Sa | VANE PUMP |
| CN105545744B (en) * | 2015-12-22 | 2017-12-26 | 重庆市高新技术产业开发区潞翔能源技术有限公司 | Compressor in absorption type natural gas system |
| CN106017199B (en) * | 2016-07-27 | 2017-11-17 | 广州市昕恒泵业制造有限公司 | pump for shell-and-tube heat exchanger |
| RU172054U1 (en) * | 2016-11-02 | 2017-06-28 | Виктор Иванович Чудин | CAMERA VOLUME LIQUID METER |
| CN106640515B (en) * | 2016-11-29 | 2018-06-29 | 河南科技大学 | A kind of chain minor rotor hydraulic motor |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3153384A (en) * | 1961-06-12 | 1964-10-20 | Pacific Ind Mfg Co | Vane type pump |
| FR1395435A (en) * | 1964-05-22 | 1965-04-09 | Fluid actuated device | |
| US3361076A (en) * | 1966-05-06 | 1968-01-02 | William B Pritchett Jr | Expansible chamber device |
| DE2022841A1 (en) * | 1970-05-11 | 1971-11-25 | Adolf Kresin | Valveless rotary piston pump |
| DE3120350A1 (en) * | 1981-05-22 | 1983-01-27 | Albert Wagner | Vane cell pumps and motors with pressure gap balancing |
| CN2045031U (en) * | 1989-03-15 | 1989-09-27 | 浙江省仙居液压件厂 | Dual-purpose variable paddle pump |
-
1992
- 1992-09-02 DE DE9211768U patent/DE9211768U1/en not_active Expired - Lifetime
-
1993
- 1993-08-26 AU AU49543/93A patent/AU684725B2/en not_active Ceased
- 1993-08-26 JP JP06506841A patent/JP3129737B2/en not_active Expired - Fee Related
- 1993-08-26 WO PCT/EP1993/002311 patent/WO1994005912A1/en active IP Right Grant
- 1993-08-26 EP EP93919192A patent/EP0659237B1/en not_active Expired - Lifetime
- 1993-08-26 DK DK93919192.0T patent/DK0659237T3/en active
- 1993-08-26 DE DE59302390T patent/DE59302390D1/en not_active Expired - Fee Related
- 1993-08-26 KR KR1019950700840A patent/KR950703124A/en not_active IP Right Cessation
- 1993-08-26 CA CA002143719A patent/CA2143719C/en not_active Expired - Fee Related
- 1993-08-26 AT AT93919192T patent/ATE137306T1/en not_active IP Right Cessation
- 1993-09-02 CN CN93118992A patent/CN1040786C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| EP0659237A1 (en) | 1995-06-28 |
| CN1103931A (en) | 1995-06-21 |
| AU684725B2 (en) | 1998-01-08 |
| ATE137306T1 (en) | 1996-05-15 |
| CN1040786C (en) | 1998-11-18 |
| KR950703124A (en) | 1995-08-23 |
| JP3129737B2 (en) | 2001-01-31 |
| JPH08500877A (en) | 1996-01-30 |
| DK0659237T3 (en) | 1996-07-29 |
| DE59302390D1 (en) | 1996-05-30 |
| CA2143719A1 (en) | 1994-03-17 |
| EP0659237B1 (en) | 1996-04-24 |
| AU4954393A (en) | 1994-03-29 |
| WO1994005912A1 (en) | 1994-03-17 |
| DE9211768U1 (en) | 1992-11-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |