CA1224408A - Device for delivering flowable material - Google Patents
Device for delivering flowable materialInfo
- Publication number
- CA1224408A CA1224408A CA000476496A CA476496A CA1224408A CA 1224408 A CA1224408 A CA 1224408A CA 000476496 A CA000476496 A CA 000476496A CA 476496 A CA476496 A CA 476496A CA 1224408 A CA1224408 A CA 1224408A
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- Prior art keywords
- pump
- drive means
- spiral
- drive
- stator
- Prior art date
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- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A device for delivering flowable materials from a production bore, consisting of a source of pressurized medium, a pressurized medium conduit for conducting the pressurized medium into the bottom area of the bore, the pressurized medium being used to operate drive means coupled to a pump for the flowable material. The drive means and the pump are both rotary displacement devices having a spiral rotor which describes an eccentric rotational path within a spiral stator.
The rotor and the stator of the drive means and the rotor and the stator of the pump have the same eccentricity and are rigidly connected to one another.
A device for delivering flowable materials from a production bore, consisting of a source of pressurized medium, a pressurized medium conduit for conducting the pressurized medium into the bottom area of the bore, the pressurized medium being used to operate drive means coupled to a pump for the flowable material. The drive means and the pump are both rotary displacement devices having a spiral rotor which describes an eccentric rotational path within a spiral stator.
The rotor and the stator of the drive means and the rotor and the stator of the pump have the same eccentricity and are rigidly connected to one another.
Description
2~
DEVICE FOR DELIVERING FLOWABLE MATERIAL
BACKGROUND OF rHE INVENTION
Field of the Invention This invention relates to devices for delivering ~lowable material and more particularly concerns devices for delivering flowable material from an underground borehole.
Description of Prior Art ~ .S. Patent No. 4,386,654 to Becker describes a downhole pump for delivering flowable material which com-prises a helical screw type rotor mounted within a resil-ient stator. The pump is connected to drive means whichalso comprises a helical screw type rotor mounted within a resilient stator, the rotor being driven by pressurised oil delivered from the ground surface. The drive rneans is connected to the pump by drive transmission means in-cluding universal joints and a drive shaft~
An object of the present invention is to provide adevice for delivering Elowable material from an underground borehole which is simpler in construction and relatively easy to manufacture.
Another object of the present invention is to pro-vide a device of the above type which is more reliable and able to withstand better the extreme operatinq con-ditions often present in a production borehole.
SUMMARY OF THE INVENTION
According to the pr sent invention there is provided a device for delivering flowa~le material from an under-ground borehole comprising.
a source of pressurised medium;
drive means adapted to be driven by said pressurised medium;
con~luit neans connecting said source of pressurised medium alld said drive mean~;
drive tr~nsmission means associated with said drive ~2~
means;
a pump arranged to be driven by said drive trans-mission means and said transmission means;
a pump inlet and a pump outlet whereby when the pump is driven it delivers flo~able material from the inlet to the outlet;
a delivery conduit communicating with the pump out-let;
the drive and pump both being oE a rotary displace-ment type comprising a spiral rotor and a spiral stator;
the stator being mounted in a housing;
the rotor being mounted for eccentric rotation with-in the stator;
the ~Irive transmitting rneans co-nprising a rigid connection; and the rotor and stator of both the pump and ~he drive mea~s having the same eccentricity.
The concept of designing the rotors and stators of the drive means and pump to have the same eccentricity enables a rigid drive transmission means to be utilised, thereby avoiding the provision of universal joints. This simpler design with its reduced number of moviny parts is more reliable, has a reduced risk of breakdown and pro-vides for longer maintenance free operation.
In a preferred embodiment the working ch~nber volume of the pump is substantially greater than the working chamber volume of the drive means. This arrangement pro-vides for the delivery of a greater volume of flowable material from the borehole than the volume of pressurised medium which has to be supplied to the drive means.
The ~se of a smaller volume of pressurised fluid re~uires a proportionate increase iA pressuce and for this reason it is preferred to use a multistage drive m~a~s to reduce the pressure drop between stayes and thus make it relatively easy to seal the working parts of the .. . . ... ....
2~8 drive means against leakage.
The relative increase in working chamber volume of the pump can be achieved by providing the rotor and stator with a relatively large spiral pitch, by providing a relatively large cross-sectional area of the working chamber or by a combination of both.
It is advantageous that the number o~ stages SA of the drive means, the number of stages Sp of the pump, the working chamber volume Vp of the pump, the working chamber volume V~ of the drive means and the overall efficiency )~GA and ~GP
of the drive means and the pump meet the formula SA Vp Sp VA ~GA ~GP- This enables the same load to be achieved on the sealing edges between adjacent working chamhers, taking into account the drive and pump losses occurring during operation.
The spiraled rotors of both the drive means and the pump are designed to rotate together in the same direction. However, in some embodiments the drive and pump rotors spiral in the same direction of rotation and consequently the ~low of mate-rials through both the drive means and the pump is in the same direction. This tends to balance the axial reaction forces exerted on the rotors of the drive means and the pump.
Thus if the reaction forces are of the same magnitude, the resulting forces to be absorbed by the axial bearing is greatly reduced.
One way of achieving this flow path is to provide an intermediate space between the stator casing or rotor casing and a support casing therefor, by which means the existing available space can be used and an increase in the housing diameter can be avoided.
A particularly compact embodiment is achieved by arrang-ing the stators of the pump and the drive means as outer and inner stators and arranging the rotors to be carried by a common body mounted for rotation between the stators.
122~
To achieve the smallest possible flow losses of flowable material to be delivered, the pressurised medium is preferably conducted through a pressurised medium con-duit in the ~orm of a standard diameter hollo~ tube in-serted into the bore, so that the annular space, whichhas a larger cross-section compared with the hollow tube, is available between the hollow tube and the bore lining as a delivery conduit for the flowable material. Fur-thermore this embodiment has the advantage that chemi-cally aggressive flowable materials are kept away fromthe bore lining.
In th i s C3 se, the pressurised medium is fed to the drive means through the annular space between the hollow tube and the bore hole lining and the flowable material is delivered through the hollow tube. The diameter of the tube will be selected as appropriate to the circum-stances.
The pressurised medium will usually be a pressurised working oil and the flowa~le material will be a material such as crude oil to be extracted from below the surface of the ground and delivered to the surface.
BRIE~F D~SCRIPTION OF THE DRAWING
The invention will now be further descri~ed with reference to several embodiments which are shown in the accompanyin~J drawings, wherein:
~IG. 1 is a diagrammatic broken longitudinal section through a device according to the invention;
FIGS. 2, 3 and 4 are diagrammatic sections similar to that of FIG. 1 showing alternativ~ embodiments;
YIGS. 5 and 6 are cross-sections through two altern-ative einbodirnents of drive means or pump;
~IG. 7 is a diagrammatic broken longitudinal section of a further embodimellt of the device with a co~on rotor for the drive means and pump;
FTG. 8 is a diagrarnmatic longi~udinal section of another embodiment of the invention.
D~SCRIPTION OF THE PREFERRED EMBODIMENT
The device shown in FIG. 1 comprises an aboveground source 1 of pressurised medium which supplies a fluid under pressure through a conduit 3. The conduit is in the form of a hollow tube 32 which extends down to an assembly 4 including a housing 7, a drive means 5 and a pump 6 located at the bottom of the bore 2. rrhe bore 2 is provided with a bore hole lining 9.
It ~ill be appreciated that the assernbly 4 can also he arranged at a pcsition other than at the bottom of the bore 2 where flowable material 8 penetrates from a depos-it into the bore 2 through apertures in the bore hole lining 9.
In detail, the drive means 5 consists of a spiral rotor 10 which is located in a soiral stator 11. A pump 6 is located beneath the drive means 5, the pump, like the drive means, comprising a rotor 12 and a stator 13.
The drive me~ns and the pump are enclosed by the housing 7.
The rotor 12 of the pump 6 is rigidly connected to the rotor 10 of the drive means 5 and the lower end face of the rotor 12 is supported against an axial bearing 140 As can be seen from FIG. 1, the rotor 10 and the stator 11 have the same eccentricity as the rotor 12 and the stator 13, so that both rotors 10 and 12 execute tEhe same eccentric movement during operation.
The cross-sectional areas of the working chambers 18 and 19 of the drive means 5 and the pump 6 are the same but the p~mp rotor 12 and the pump stato~ 13 have ten ~:imes the pitch oE the drive rotor 13 and the drive stat-or 11. Consequently, for every rotor revolution, the pump 6 circulates ten times the vol~ne of the pressurised me~ rn delive~ed to the drive ineans 5. As a result dur-ing operation, the volume of material discharged at ~2~
ground level is made up of one part pressurised medium 30and nine parts of flowable material 8 extracted.
If loss-free conditions are assumed, the drive means 5 would have to he pressurised at ten times the pressure which the pump 6 provides; however, taking into account the overall effic.iency of the drive means 5 and the pump 6 and assuming overall efficiency values of 70% each, a value of twenty times that of ~Pp is obtained for ~ PA according to the following formula:
l~PA = Vp ~ Pp V~ ~GA ~GP
wherein VA: working chamber volume of the drive means, ~p: working chamber volume of the pump, ~PA: pressure difference over the drive means, ~Pp: pressure difference over the pump, q~GA: overall efficiency of the drive means, ~ GP: overall efficiency of the pump.
To overcome the pressure drop over the drive means 5 through the sealing edges of its working chambers 18, the drive means 5 has twenty times the number of stages of the pump 6. The pressure component acting on each sealing edge thus corresponds to that of the pump 6, so that both the drive means and the pump operate under the same load.
In the assembly 4 as shown in FIG. 1, the flowable material 8 flows through the openings 15 into the pump 6 and, together with the pressurised medium 29, through openings 16 into the annular space 34, between the bore hole lining 9 and the hollow tube 32. This annular space services as a delivery conduit 33. A direct path between the openings 15 and 16 is prevented by the packing 17, which is arranged between the housing 7 and the bore hole line 9.
In this embodiment it will be seen looking from the same end location that the spirals of the drive rotor 10 and dxive stator 11 are opposite to and the rev.erse of the spirals of the pump rotor 12 ~2~4~
and pump stator 13. H0nce upon being simultaneously ro~ated in the same direction, the axial reaction forces applied to the rotors and axial bearing 14 are therefore cumulative.
On the other hand, the alternative embodiment shown in FIG. 2 comprises a drive 5 and a pump 6 having spirals extendiny in the same direction of rotation. Whereas the pump 6 is identical to that shown in FIG. 1, pressurised medium 29 is arranged to flow through the drive means 5 in the reverse direction, that is, from the bottom upwards.
To achieve this, the pressurised medium conduit 3 is routed past and parallel to the working chamber lB of the drive means 5 and is directed into it from below.
The use of the same direction of ~low in the drive means 5 and the pump 6 lead to opposed axial reaction forces being applied to the rotors 10 and 12. Consequently the axial reaction forces on rotors 10 and 12 compensate one another and considera~ly reduce the load on the axial bearing 14. This embodiment, however, still requires a seal 20 to separate the working chamber 18 of the drive means 5 from the working chamber 19 of the pump 6.
In the embodiment shown in FIG. 3 the pressurised medium 29 is fed to the drive means 5 from below as in the embodiment shown in FIG. 2. In this embodiment however the arrangement of the drive means 5 and pump 6 is reversed in the housing 7, by which means a seal between the working chamber 18 of the drive means 5 and the working chamber 19 of the pump 6 can be dispensed with. In this embodiment the flowable material 8 enters the bore hole lining 9 through apertures at a higher level than in the embodiment of FIG 2.
Another embodimen~ of the invention is shown in FIG.
4. In this embodiment the arrangement of the drive means 5, the pump 6 and the conduit for pressurised medium are the same as the embodiment shown in FIG 1. However, the 4~3 spiral rotor and stator of the pump 6 are designed in the same direction of rotation as in the drive means 5, so that flowable Material 8 flows through the pump 6 rom top to bottom and, after reversal of direction, is delivered upwardly through a conduit 21 which extends parallel to the working chamber l9 of the pump 6 and between the stator thereof and the housing.
F`IGS. 5 and 6 are cross-sections of alternative arrangements of rotor and stator which can be utilised in a pump or drive means. In the description of these FIGS.
the reference nu~nerals of similar parts are the same as those used in FIGS. l to 4.
In FIG. 5, the stator ll, 13 is in the form of a shaped casing 22 disposed ~ithin the housing 7. The in-termediate space between the ~alls of the shaped casing22 and the housing 7 are used as a conduit such as the conduits 3 and 2l which extend parallel to the working chambers lR and l9. As indicated by the symbols 23 and 24, pressurised medium 29 or flowahle material 8 flows through the working chambers 18 and 19 in a direction into the plane of the drawing, whereas they flow through the conduit 2l and 3 in a direction out of the plane of ~he drawing.
As shown in FIG. 6, it is also possible, either add-itionally or alternatively, to design the rotors lO and12 as a casing 31 fixed to a support casing 30 and to use the intermediate space between the casirJg 31 and the support 30 as a conduit 3 or 21, or to design the rotors 10 and 12 with a hollow section and to use the space so defined for this purpose.
In the e~bodiment shown in FIG. 7, a more compact col-struction is achieved by arranging the drive means 5 and the pump 6 to nest inside one another. In this case, the drive medns is formed by the inner stator ll and the inner area 26 of a coxrunon rotor 25. The outer stator 13 and the outer area 27 of the common rotor 25 comprise the pump.
In ad~ition, an axial seal 28 is provided for the axial bearing 14. The pressurised medium 29 i5 fed to the drive means 5 via the hollow inner stator 11 a~d flows through the associated working chamber 18~ The flowable mat.erial 8, which in the lower area enters into the working chamber 19 of the pump 6, also flows upwards through the working chamber 19. The pressurised medium 29 and the flowable material 8 leaves the housing 7 vla com~on outlet openings 16. As can be seen from the draw-ing, an especially short compact construction can be ach-ieved by this arrangement.
FIG. 8 shows yet a further embodiment of the inven-t.ion in which the pressurised medium 29, instea~ of beingcondlJcted through the hollow tube 32~ is forced through the annu1ar space 34 between the hollow tube 32 and the bore hole lining 9, and the flowable mater.ial ~ is deliv-ered through the hollow tuhe ~'2. The arrangement of the drive means 5 and the pump 6 as shown are as shown in~
FIG. 3 but each of the other arrangements shown could also be adapted for use, in this embodiment~ This alt-ernative has the advantage that it protects the bore hole lining 9 in the case of chemically aggressive flowable ma~eria1s. It is easier and ~heaper to make the hollow tube 32 ~rom a more cQrrosion or wear-resistant material and also it is easier to replace the hollow tube 32 in the event of wear, damag2 or corrosion~
. , ,, . ,, ,~ .... . . ..
DEVICE FOR DELIVERING FLOWABLE MATERIAL
BACKGROUND OF rHE INVENTION
Field of the Invention This invention relates to devices for delivering ~lowable material and more particularly concerns devices for delivering flowable material from an underground borehole.
Description of Prior Art ~ .S. Patent No. 4,386,654 to Becker describes a downhole pump for delivering flowable material which com-prises a helical screw type rotor mounted within a resil-ient stator. The pump is connected to drive means whichalso comprises a helical screw type rotor mounted within a resilient stator, the rotor being driven by pressurised oil delivered from the ground surface. The drive rneans is connected to the pump by drive transmission means in-cluding universal joints and a drive shaft~
An object of the present invention is to provide adevice for delivering Elowable material from an underground borehole which is simpler in construction and relatively easy to manufacture.
Another object of the present invention is to pro-vide a device of the above type which is more reliable and able to withstand better the extreme operatinq con-ditions often present in a production borehole.
SUMMARY OF THE INVENTION
According to the pr sent invention there is provided a device for delivering flowa~le material from an under-ground borehole comprising.
a source of pressurised medium;
drive means adapted to be driven by said pressurised medium;
con~luit neans connecting said source of pressurised medium alld said drive mean~;
drive tr~nsmission means associated with said drive ~2~
means;
a pump arranged to be driven by said drive trans-mission means and said transmission means;
a pump inlet and a pump outlet whereby when the pump is driven it delivers flo~able material from the inlet to the outlet;
a delivery conduit communicating with the pump out-let;
the drive and pump both being oE a rotary displace-ment type comprising a spiral rotor and a spiral stator;
the stator being mounted in a housing;
the rotor being mounted for eccentric rotation with-in the stator;
the ~Irive transmitting rneans co-nprising a rigid connection; and the rotor and stator of both the pump and ~he drive mea~s having the same eccentricity.
The concept of designing the rotors and stators of the drive means and pump to have the same eccentricity enables a rigid drive transmission means to be utilised, thereby avoiding the provision of universal joints. This simpler design with its reduced number of moviny parts is more reliable, has a reduced risk of breakdown and pro-vides for longer maintenance free operation.
In a preferred embodiment the working ch~nber volume of the pump is substantially greater than the working chamber volume of the drive means. This arrangement pro-vides for the delivery of a greater volume of flowable material from the borehole than the volume of pressurised medium which has to be supplied to the drive means.
The ~se of a smaller volume of pressurised fluid re~uires a proportionate increase iA pressuce and for this reason it is preferred to use a multistage drive m~a~s to reduce the pressure drop between stayes and thus make it relatively easy to seal the working parts of the .. . . ... ....
2~8 drive means against leakage.
The relative increase in working chamber volume of the pump can be achieved by providing the rotor and stator with a relatively large spiral pitch, by providing a relatively large cross-sectional area of the working chamber or by a combination of both.
It is advantageous that the number o~ stages SA of the drive means, the number of stages Sp of the pump, the working chamber volume Vp of the pump, the working chamber volume V~ of the drive means and the overall efficiency )~GA and ~GP
of the drive means and the pump meet the formula SA Vp Sp VA ~GA ~GP- This enables the same load to be achieved on the sealing edges between adjacent working chamhers, taking into account the drive and pump losses occurring during operation.
The spiraled rotors of both the drive means and the pump are designed to rotate together in the same direction. However, in some embodiments the drive and pump rotors spiral in the same direction of rotation and consequently the ~low of mate-rials through both the drive means and the pump is in the same direction. This tends to balance the axial reaction forces exerted on the rotors of the drive means and the pump.
Thus if the reaction forces are of the same magnitude, the resulting forces to be absorbed by the axial bearing is greatly reduced.
One way of achieving this flow path is to provide an intermediate space between the stator casing or rotor casing and a support casing therefor, by which means the existing available space can be used and an increase in the housing diameter can be avoided.
A particularly compact embodiment is achieved by arrang-ing the stators of the pump and the drive means as outer and inner stators and arranging the rotors to be carried by a common body mounted for rotation between the stators.
122~
To achieve the smallest possible flow losses of flowable material to be delivered, the pressurised medium is preferably conducted through a pressurised medium con-duit in the ~orm of a standard diameter hollo~ tube in-serted into the bore, so that the annular space, whichhas a larger cross-section compared with the hollow tube, is available between the hollow tube and the bore lining as a delivery conduit for the flowable material. Fur-thermore this embodiment has the advantage that chemi-cally aggressive flowable materials are kept away fromthe bore lining.
In th i s C3 se, the pressurised medium is fed to the drive means through the annular space between the hollow tube and the bore hole lining and the flowable material is delivered through the hollow tube. The diameter of the tube will be selected as appropriate to the circum-stances.
The pressurised medium will usually be a pressurised working oil and the flowa~le material will be a material such as crude oil to be extracted from below the surface of the ground and delivered to the surface.
BRIE~F D~SCRIPTION OF THE DRAWING
The invention will now be further descri~ed with reference to several embodiments which are shown in the accompanyin~J drawings, wherein:
~IG. 1 is a diagrammatic broken longitudinal section through a device according to the invention;
FIGS. 2, 3 and 4 are diagrammatic sections similar to that of FIG. 1 showing alternativ~ embodiments;
YIGS. 5 and 6 are cross-sections through two altern-ative einbodirnents of drive means or pump;
~IG. 7 is a diagrammatic broken longitudinal section of a further embodimellt of the device with a co~on rotor for the drive means and pump;
FTG. 8 is a diagrarnmatic longi~udinal section of another embodiment of the invention.
D~SCRIPTION OF THE PREFERRED EMBODIMENT
The device shown in FIG. 1 comprises an aboveground source 1 of pressurised medium which supplies a fluid under pressure through a conduit 3. The conduit is in the form of a hollow tube 32 which extends down to an assembly 4 including a housing 7, a drive means 5 and a pump 6 located at the bottom of the bore 2. rrhe bore 2 is provided with a bore hole lining 9.
It ~ill be appreciated that the assernbly 4 can also he arranged at a pcsition other than at the bottom of the bore 2 where flowable material 8 penetrates from a depos-it into the bore 2 through apertures in the bore hole lining 9.
In detail, the drive means 5 consists of a spiral rotor 10 which is located in a soiral stator 11. A pump 6 is located beneath the drive means 5, the pump, like the drive means, comprising a rotor 12 and a stator 13.
The drive me~ns and the pump are enclosed by the housing 7.
The rotor 12 of the pump 6 is rigidly connected to the rotor 10 of the drive means 5 and the lower end face of the rotor 12 is supported against an axial bearing 140 As can be seen from FIG. 1, the rotor 10 and the stator 11 have the same eccentricity as the rotor 12 and the stator 13, so that both rotors 10 and 12 execute tEhe same eccentric movement during operation.
The cross-sectional areas of the working chambers 18 and 19 of the drive means 5 and the pump 6 are the same but the p~mp rotor 12 and the pump stato~ 13 have ten ~:imes the pitch oE the drive rotor 13 and the drive stat-or 11. Consequently, for every rotor revolution, the pump 6 circulates ten times the vol~ne of the pressurised me~ rn delive~ed to the drive ineans 5. As a result dur-ing operation, the volume of material discharged at ~2~
ground level is made up of one part pressurised medium 30and nine parts of flowable material 8 extracted.
If loss-free conditions are assumed, the drive means 5 would have to he pressurised at ten times the pressure which the pump 6 provides; however, taking into account the overall effic.iency of the drive means 5 and the pump 6 and assuming overall efficiency values of 70% each, a value of twenty times that of ~Pp is obtained for ~ PA according to the following formula:
l~PA = Vp ~ Pp V~ ~GA ~GP
wherein VA: working chamber volume of the drive means, ~p: working chamber volume of the pump, ~PA: pressure difference over the drive means, ~Pp: pressure difference over the pump, q~GA: overall efficiency of the drive means, ~ GP: overall efficiency of the pump.
To overcome the pressure drop over the drive means 5 through the sealing edges of its working chambers 18, the drive means 5 has twenty times the number of stages of the pump 6. The pressure component acting on each sealing edge thus corresponds to that of the pump 6, so that both the drive means and the pump operate under the same load.
In the assembly 4 as shown in FIG. 1, the flowable material 8 flows through the openings 15 into the pump 6 and, together with the pressurised medium 29, through openings 16 into the annular space 34, between the bore hole lining 9 and the hollow tube 32. This annular space services as a delivery conduit 33. A direct path between the openings 15 and 16 is prevented by the packing 17, which is arranged between the housing 7 and the bore hole line 9.
In this embodiment it will be seen looking from the same end location that the spirals of the drive rotor 10 and dxive stator 11 are opposite to and the rev.erse of the spirals of the pump rotor 12 ~2~4~
and pump stator 13. H0nce upon being simultaneously ro~ated in the same direction, the axial reaction forces applied to the rotors and axial bearing 14 are therefore cumulative.
On the other hand, the alternative embodiment shown in FIG. 2 comprises a drive 5 and a pump 6 having spirals extendiny in the same direction of rotation. Whereas the pump 6 is identical to that shown in FIG. 1, pressurised medium 29 is arranged to flow through the drive means 5 in the reverse direction, that is, from the bottom upwards.
To achieve this, the pressurised medium conduit 3 is routed past and parallel to the working chamber lB of the drive means 5 and is directed into it from below.
The use of the same direction of ~low in the drive means 5 and the pump 6 lead to opposed axial reaction forces being applied to the rotors 10 and 12. Consequently the axial reaction forces on rotors 10 and 12 compensate one another and considera~ly reduce the load on the axial bearing 14. This embodiment, however, still requires a seal 20 to separate the working chamber 18 of the drive means 5 from the working chamber 19 of the pump 6.
In the embodiment shown in FIG. 3 the pressurised medium 29 is fed to the drive means 5 from below as in the embodiment shown in FIG. 2. In this embodiment however the arrangement of the drive means 5 and pump 6 is reversed in the housing 7, by which means a seal between the working chamber 18 of the drive means 5 and the working chamber 19 of the pump 6 can be dispensed with. In this embodiment the flowable material 8 enters the bore hole lining 9 through apertures at a higher level than in the embodiment of FIG 2.
Another embodimen~ of the invention is shown in FIG.
4. In this embodiment the arrangement of the drive means 5, the pump 6 and the conduit for pressurised medium are the same as the embodiment shown in FIG 1. However, the 4~3 spiral rotor and stator of the pump 6 are designed in the same direction of rotation as in the drive means 5, so that flowable Material 8 flows through the pump 6 rom top to bottom and, after reversal of direction, is delivered upwardly through a conduit 21 which extends parallel to the working chamber l9 of the pump 6 and between the stator thereof and the housing.
F`IGS. 5 and 6 are cross-sections of alternative arrangements of rotor and stator which can be utilised in a pump or drive means. In the description of these FIGS.
the reference nu~nerals of similar parts are the same as those used in FIGS. l to 4.
In FIG. 5, the stator ll, 13 is in the form of a shaped casing 22 disposed ~ithin the housing 7. The in-termediate space between the ~alls of the shaped casing22 and the housing 7 are used as a conduit such as the conduits 3 and 2l which extend parallel to the working chambers lR and l9. As indicated by the symbols 23 and 24, pressurised medium 29 or flowahle material 8 flows through the working chambers 18 and 19 in a direction into the plane of the drawing, whereas they flow through the conduit 2l and 3 in a direction out of the plane of ~he drawing.
As shown in FIG. 6, it is also possible, either add-itionally or alternatively, to design the rotors lO and12 as a casing 31 fixed to a support casing 30 and to use the intermediate space between the casirJg 31 and the support 30 as a conduit 3 or 21, or to design the rotors 10 and 12 with a hollow section and to use the space so defined for this purpose.
In the e~bodiment shown in FIG. 7, a more compact col-struction is achieved by arranging the drive means 5 and the pump 6 to nest inside one another. In this case, the drive medns is formed by the inner stator ll and the inner area 26 of a coxrunon rotor 25. The outer stator 13 and the outer area 27 of the common rotor 25 comprise the pump.
In ad~ition, an axial seal 28 is provided for the axial bearing 14. The pressurised medium 29 i5 fed to the drive means 5 via the hollow inner stator 11 a~d flows through the associated working chamber 18~ The flowable mat.erial 8, which in the lower area enters into the working chamber 19 of the pump 6, also flows upwards through the working chamber 19. The pressurised medium 29 and the flowable material 8 leaves the housing 7 vla com~on outlet openings 16. As can be seen from the draw-ing, an especially short compact construction can be ach-ieved by this arrangement.
FIG. 8 shows yet a further embodiment of the inven-t.ion in which the pressurised medium 29, instea~ of beingcondlJcted through the hollow tube 32~ is forced through the annu1ar space 34 between the hollow tube 32 and the bore hole lining 9, and the flowable mater.ial ~ is deliv-ered through the hollow tuhe ~'2. The arrangement of the drive means 5 and the pump 6 as shown are as shown in~
FIG. 3 but each of the other arrangements shown could also be adapted for use, in this embodiment~ This alt-ernative has the advantage that it protects the bore hole lining 9 in the case of chemically aggressive flowable ma~eria1s. It is easier and ~heaper to make the hollow tube 32 ~rom a more cQrrosion or wear-resistant material and also it is easier to replace the hollow tube 32 in the event of wear, damag2 or corrosion~
. , ,, . ,, ,~ .... . . ..
Claims (9)
1. A device for delivering flowable material from an underground borehole comprising:
a source of pressurized medium;
drive means including a drive working chamber of predetermined working volume, adapted to be rotatably driven by a predetermined working volume of said pressurized medium passed therethrough from an inlet end to an outlet end during each revolution thereof;
pressurized medium conduit means connecting said source of pressurized medium and said drive means;
drive transmission means comprising a rigid connection adjacent to, associated with and connected to said drive means;
a pump arranged to be adjacent to, rigidly connected to and rotatably driven by said drive transmission means and said drive means;
said pump having a pump inlet communicating with the bore hole and flowable material therein;
a pump outlet spaced from the pump inlet and a pump working chamber between said pump inlet and pump outlet of greater working volume than the predetermined working volume of the drive working chamber whereby when the pump is driven it delivers per revolution a greater volume of flowable material from the pump inlet to the pump outlet than the predetermined working volume of pressurized medium passed during each revolution of the drive means;
a delivery conduit communicating with and extending from the pump outlet;
sealing means located between the housing and bore hole wall at a point between the pump inlet and the pump outlet;
the drive means and pump are axially aligned adjacent one another and both being of a rotary displacement type each comprising a spiral rotor mounted for eccentric rotational movement relative to a spiral stator attached to a housing;
the spiral rotor of both the pump and the drive means being rigidly connected and aligned to rotate together in the same direction about one axis and having the same eccentric rotational movement relative to each of the spiral stators and a common axis of the spiral stators; and axial bearing means fixed relative to the housing and adapted to be engaged by an end portion of one of the spiral rotors and take the axial force applied to and by the rotors during the eccentric rotational movement thereof.
a source of pressurized medium;
drive means including a drive working chamber of predetermined working volume, adapted to be rotatably driven by a predetermined working volume of said pressurized medium passed therethrough from an inlet end to an outlet end during each revolution thereof;
pressurized medium conduit means connecting said source of pressurized medium and said drive means;
drive transmission means comprising a rigid connection adjacent to, associated with and connected to said drive means;
a pump arranged to be adjacent to, rigidly connected to and rotatably driven by said drive transmission means and said drive means;
said pump having a pump inlet communicating with the bore hole and flowable material therein;
a pump outlet spaced from the pump inlet and a pump working chamber between said pump inlet and pump outlet of greater working volume than the predetermined working volume of the drive working chamber whereby when the pump is driven it delivers per revolution a greater volume of flowable material from the pump inlet to the pump outlet than the predetermined working volume of pressurized medium passed during each revolution of the drive means;
a delivery conduit communicating with and extending from the pump outlet;
sealing means located between the housing and bore hole wall at a point between the pump inlet and the pump outlet;
the drive means and pump are axially aligned adjacent one another and both being of a rotary displacement type each comprising a spiral rotor mounted for eccentric rotational movement relative to a spiral stator attached to a housing;
the spiral rotor of both the pump and the drive means being rigidly connected and aligned to rotate together in the same direction about one axis and having the same eccentric rotational movement relative to each of the spiral stators and a common axis of the spiral stators; and axial bearing means fixed relative to the housing and adapted to be engaged by an end portion of one of the spiral rotors and take the axial force applied to and by the rotors during the eccentric rotational movement thereof.
2. A device according to Claim 1 in which the spiral rotor and the spiral stator of the drive means are arranged to spiral in the same direction as the spiral rotor and spiral stator of the pump; and in which the drive means is a multistage drive means and has a greater number of stages than the pump.
3. A device according to Claim 2 in which the multi-stage drive means has a ratio of the greater number of stages of the drive means to the number of stages of the pump approximately equal to the product of the ratio of the working chamber volume of the pump to that of the drive means and reciprocals of the overall efficiency of the drive means and the pump.
4. A device according to Claim 1 in which the pressurized medium which has driven and passed through the drive means and the flowable substance delivered from the pump have an upward flow path which is parallel to the axes of the rotors and stators.
5. A device according to Claim 4 in which the flow path is defined by an intermediate space between a spiral stator casing or spiral rotor casing and a support casing associated with the spiral stator casing or spiral rotor casing.
6. A device according to Claim 1 in which one of the two spiral stators of the pump and the drive means is arranged as an outer spiral stator and the other as an inner spiral stator, and the associated spiral rotors of the pump and drive means are carried by and connected to the outer and inner sides of a common body mounted for eccentric rotational movement between the inner and outer spiral stators.
7. A device according to Claim 6 in which the spiral stators of the pump and the drive means are located within the same axial length of the device.
8. A device according to Claim 1 in which the pressurized medium conduit means is formed by a hollow tube within the bore hole, and the delivery conduit is formed by an annular space surrounding the hollow tube.
9. A device according to Claim 1 in which the delivery conduit is formed by a hollow tube within the bore hole, and the pressurized medium conduit means is formed by an annular space surrounding the hollow tube.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEG8408333.6 | 1984-03-19 | ||
| DE8408333 | 1984-03-19 | ||
| DEP3409970.0-24 | 1984-03-19 | ||
| DE3409970A DE3409970C1 (en) | 1984-03-19 | 1984-03-19 | Device for conveying flowable substances |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1224408A true CA1224408A (en) | 1987-07-21 |
Family
ID=25819477
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000476496A Expired CA1224408A (en) | 1984-03-19 | 1985-03-14 | Device for delivering flowable material |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1224408A (en) |
-
1985
- 1985-03-14 CA CA000476496A patent/CA1224408A/en not_active Expired
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |