CA2859250C - Progressive vortex pump - Google Patents
Progressive vortex pump Download PDFInfo
- Publication number
- CA2859250C CA2859250C CA2859250A CA2859250A CA2859250C CA 2859250 C CA2859250 C CA 2859250C CA 2859250 A CA2859250 A CA 2859250A CA 2859250 A CA2859250 A CA 2859250A CA 2859250 C CA2859250 C CA 2859250C
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- stator
- pump
- diffuser
- stage
- inlet
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/002—Regenerative pumps
- F04D5/003—Regenerative pumps of multistage type
- F04D5/006—Regenerative pumps of multistage type the stages being axially offset
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/002—Regenerative pumps
- F04D5/008—Details of the stator, e.g. channel shape
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
A progressive vortex pump having multiple pump stages in which each pump stage comprises of at least two inlet stages, with each inlet stage in communication with a respective circular channel and each circular channel in communication with a respective outlet stage; the inlet stages are evenly distributed along the internal perimeter of the stator and the outlet stages are evenly distributed along the internal perimeter of the stator, with the pump stages arranged such that each outlet stage of a front pump stage is in communication with a respective inlet stage of a rear pump stage. Beneficially, the fact that the inlet and outlet stages are evenly distributed along the internal perimeter of the stator results in zero shear stress on the shaft in each pump stage.
Description
PROGRESSIVE VORTEX PUMP
FIELD OF THE INVENTION
The present invention is in the field of progressive vortex pumps used in pumping systems.
BACKGROUND OF THE INVENTION
A conventional vortex pump was described in PI0603597-3. This progressive vortex pump comprises a pump assembly having an inlet housing in contact with a fluid to be pumped and an outlet housing connected to a pumping pipe;
the pump assembly is driven by a shaft attached to a motor assembly.
When the progressive vortex pump is installed in a well such as an oil well, for example, the pump assembly is positioned inside a well casing pipe which has an upper end situated at the surface of the well and a lower end in contact with the fluid to be pumped. Similarly, the pumping pipe runs inside the well casing pipe to the well surface.
In the case of PI0603597-3, the shaft of the progressive vortex pump runs from the pump assembly through the pumping pipe up to a motor assembly positioned at the surface of the well. MU8802106-8 describes a progressive vortex pump where the shaft runs from the pump assembly up to a motor assembly comprising a submerged electric motor positioned underneath the pump assembly.
In both the progressive vortex pump with the surface motor assembly and that with the submerged motor assembly, the pump assembly is also equipped with a
FIELD OF THE INVENTION
The present invention is in the field of progressive vortex pumps used in pumping systems.
BACKGROUND OF THE INVENTION
A conventional vortex pump was described in PI0603597-3. This progressive vortex pump comprises a pump assembly having an inlet housing in contact with a fluid to be pumped and an outlet housing connected to a pumping pipe;
the pump assembly is driven by a shaft attached to a motor assembly.
When the progressive vortex pump is installed in a well such as an oil well, for example, the pump assembly is positioned inside a well casing pipe which has an upper end situated at the surface of the well and a lower end in contact with the fluid to be pumped. Similarly, the pumping pipe runs inside the well casing pipe to the well surface.
In the case of PI0603597-3, the shaft of the progressive vortex pump runs from the pump assembly through the pumping pipe up to a motor assembly positioned at the surface of the well. MU8802106-8 describes a progressive vortex pump where the shaft runs from the pump assembly up to a motor assembly comprising a submerged electric motor positioned underneath the pump assembly.
In both the progressive vortex pump with the surface motor assembly and that with the submerged motor assembly, the pump assembly is also equipped with a
2 pump housing inside of which are several pump stages. Each pump stage is formed by a stator attached to the pump housing, a first diffuser attached to the front side of the stator, a second diffuser attached to the rear side of the stator and an impeller coupled to the shaft and positioned inside the stator.
Each pump stage comprises an inlet stage in communication with a circular channel which is in communication with an outlet stage. The impeller blades are positioned inside the circular channel. The pump stages are arranged so that the outlet stage of a front pump stage is in communication with the inlet stage of a rear pump stage.
Under operating conditions, the rotation of the impeller causes fluid to enter the pump stage through the stage inlet; the fluid then passes along the circular channel, exits the pump stage through the outlet stage and moves on to the next pump stage. Thus, the pressure of the fluid increases between the inlet stage and outlet stage.
A conventional progressive vortex pump presents a problem of excessive shear stress acting on the shaft, which may cause a shear failure of the shaft. More specifically the difference in pressure between the inlet stage and outlet stage results in a net shear stress that acts on the shaft in each pump stage.
Accordingly, what is needed therefor is a progressive vortex pump which eliminates the problem of excessive shear stress on the shaft.
SUMMARY OF THE INVENTION
The present invention seeks to provide a progressive vortex pump having multiple pump stages in which each pump stage comprises of at least two inlet stages,
Each pump stage comprises an inlet stage in communication with a circular channel which is in communication with an outlet stage. The impeller blades are positioned inside the circular channel. The pump stages are arranged so that the outlet stage of a front pump stage is in communication with the inlet stage of a rear pump stage.
Under operating conditions, the rotation of the impeller causes fluid to enter the pump stage through the stage inlet; the fluid then passes along the circular channel, exits the pump stage through the outlet stage and moves on to the next pump stage. Thus, the pressure of the fluid increases between the inlet stage and outlet stage.
A conventional progressive vortex pump presents a problem of excessive shear stress acting on the shaft, which may cause a shear failure of the shaft. More specifically the difference in pressure between the inlet stage and outlet stage results in a net shear stress that acts on the shaft in each pump stage.
Accordingly, what is needed therefor is a progressive vortex pump which eliminates the problem of excessive shear stress on the shaft.
SUMMARY OF THE INVENTION
The present invention seeks to provide a progressive vortex pump having multiple pump stages in which each pump stage comprises of at least two inlet stages,
3 with each inlet stage in communication with a respective circular channel and each circular channel in communication with a respective outlet stage; the inlet stages are evenly distributed along the internal perimeter of the stator and the outlet stages are evenly distributed along the internal perimeter of the stator, with the pump stages arranged such that each outlet stage of a front pump stage is in communication with a respective inlet stage of a rear pump stage. Beneficially, the fact that the inlet and outlet stages are evenly distributed along the internal perimeter of the stator results in zero shear stress on the shaft in each pump stage.
The present invention seeks to provide a progressive vortex pump, comprising: (a) an inlet housing (21) in contact with a fluid (F) to be pumped; (b) a pump housing (23), connected to the inlet housing (21) and comprising multiple adjacent pump stages (24), each pump stage (24) having: (b1) a stator (240) having a front and a rear side, a first diffuser (250) attached to the front side of the stator (240), a second diffuser (250) attached to the rear side of the stator (240), and an impeller (260) lodged inside the stator (240); the stator (240), the diffuser (250) and the impeller (260) constructed and arranged for receiving a shaft (40) which is connected to the impeller (260) and connected to a motor assembly (50); (b2) at least two inlet stages (E), each of the at least two inlet stages (E) in communication with a respective circular channel (C), each circular channel (C) in communication with a respective outlet stage (S); the at least two inlet stages (E) evenly distributed along an internal perimeter of the stator (240); the respective outlet stages (S) evenly distributed along the internal perimeter of the stator (240); the pump stages (24) constructed and arranged such that each outlet stage (S) is
The present invention seeks to provide a progressive vortex pump, comprising: (a) an inlet housing (21) in contact with a fluid (F) to be pumped; (b) a pump housing (23), connected to the inlet housing (21) and comprising multiple adjacent pump stages (24), each pump stage (24) having: (b1) a stator (240) having a front and a rear side, a first diffuser (250) attached to the front side of the stator (240), a second diffuser (250) attached to the rear side of the stator (240), and an impeller (260) lodged inside the stator (240); the stator (240), the diffuser (250) and the impeller (260) constructed and arranged for receiving a shaft (40) which is connected to the impeller (260) and connected to a motor assembly (50); (b2) at least two inlet stages (E), each of the at least two inlet stages (E) in communication with a respective circular channel (C), each circular channel (C) in communication with a respective outlet stage (S); the at least two inlet stages (E) evenly distributed along an internal perimeter of the stator (240); the respective outlet stages (S) evenly distributed along the internal perimeter of the stator (240); the pump stages (24) constructed and arranged such that each outlet stage (S) is
4 in communication with the respective inlet stage (E) of the adjacent pump stage (24), and (c) an outlet housing (22), connected to the pump housing (23) and connected to a pumping pipe (30). The shaft (40) connected to the motor assembly (50), driving the pump.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 shows a longitudinal section of a progressive vortex pump according to the present invention, installed in a well, with a surface motor assembly.
Figure 2 shows an enlarged view of region "A" indicated in Figure 1.
Figure 3 is an exploded view of a progressive vortex pump, with pump stages configured according to the first embodiment of the present invention.
Figure 4 is an exploded view of a pump stage, configured according to the first embodiment of the present invention.
Figure 5 is an exploded view of a pump stage, configured according to the second embodiment of the present invention.
Figure 6 shows a plan view of a diffuser, in accordance with the first embodiment of the present invention, emphasizing its rear surface.
Figure 7 shows a plan view of a diffuser, in accordance with the first embodiment of the present invention, emphasizing its front surface.
Figure 8 shows an enlarged view of region "B" indicated in Figure 2.
Figure 9 depicts a top view of a pump stage, with the diffusers hidden.
Figure 10 shows a longitudinal section of a progressive vortex pump according to the present invention, installed in a well, with a submersed motor assembly.
Figure 11 shows an enlarged view of region "C" indicated in Figure 10.
Figure 12 is an exploded view of a pump stage, configured according to the third embodiment of the present invention.
Figure 13 shows an enlarged view of a region of the progressive vortex pump configured according to the third embodiment of the present invention, the region is equivalent to the region "D" indicated in Figure 2.
DETAILED DESCRIPTION OF THE INVENTION
The present invention seeks to provide a progressive vortex pump assembly (20) comprising an inlet housing (21) in contact with a fluid (F) to be pumped and an outlet housing (22) connected to a pumping pipe (30); the pump assembly (20) is driven by a shaft (40) associated with a motor assembly (50). The pump also comprising a pump housing (23) with an internal surface, containing multiple adjacent pump stages (24) inside; each pump stage (24) comprising of a stator (240) contained by the pump housing (23), a first diffuser (250) attached to a front side of the stator (240), a second diffuser (250) attached to a rear side of the stator (240), and an impeller (260) mounted on the shaft (40), said impeller (260) lodged inside the stator (240). In accordance with the present invention, each pump stage (24) comprises at least two inlet stages (El, E2), each of the at least two inlet stage (El, E2) is in communication with a respective circular channel (Cl, C2), and each circular channel (Cl, C2) is in communication with a respective outlet stage (S1, S2). The inlet stages (El, E2) are evenly distributed along the internal perimeter of the stator (240), the outlet stages (S1, S2) are evenly distributed along the internal perimeter of the stator (240). The pump stages (24) are constructed and arranged such that each outlet stage (Si, S2) of a pump stage (24) is in communication with a respective inlet stage (El, E2) of the adjacent pump stage (24).
The stator (240) is ring-shaped and its external surface (241) remains in contact with the internal surface of the pump housing (23). The internal surface (242) of the stator (240) has at least two locking protrusions (243) with straight front and rear surfaces (243a), a circular internal surface (243h) and axial length shorter than the axial length of the stator (240). The locking protrusions (243) are evenly distributed along the internal perimeter of the stator (240). The internal surface (242) of the stator (240) further has at least two portions without protrusion, defining at least two stator inlets (244), each of which is located on one of the sides of the respective locking protrusion (243). The internal surface (242) of the stator (240) further has at least two passage protrusions (246) with straight front and rear surfaces (246a), axial length equal to the axial length of the locking protrusions (243) and internal surface (246b) in the shape of a curved double ramp with converging apexes (246c), where each passage protrusion (246) is located adjacent to the respective stator inlet (244). The internal surface (242) of the stator (240) further has at least two portions without protrusion, defining two stator outlets (245), where each stator outlet (245) is located adjacent to the respective passage protrusion (246). The arc length of the protrusions passage (246) is substantially longer than the arc length of the locking protrusions (243). The passage protrusions (246) extend over most of the internal perimeter of the stator (240), with one end of each passage protrusion (246) interrupted by the respective stator inlet (244) and the other end by the respective stator outlet (245), where the stator inlet (244) and outlet (245) are separated by the respective locking protrusion (243).
The diffuser (250) is disc-shaped with a central opening (251) for receiving the shaft (40) and having at least two axial passages (252), each of which is defined by an inexistence of material in a location of the diffuser's border (250). The axial passages (252) are distributed evenly along the external perimeter of the diffuser (250). The diffuser (250) further has at least two front recesses (253a) on its front surface (253), where each front recess (253a) extends in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b) and the diffuser (250) further has at least two rear recesses (254a) on its rear surface (254), where each rear recess (254a) extends in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b), wherein a non-recessed front portion (253b) adjacent to an axial passage (252) is offset in relation to a non-recessed rear portion (254b) adjacent to this same axial passage (252).
The impeller (260) is disc-shaped with a central opening (261) constructed and arranged to be mounted on the shaft (40), said impeller (260) having a border (262) shaped as a curved double ramp with converging impeller apexes (262a), and is equipped with multiple blades (263); the diameter of the impeller (260) measured up to the blades (263) is larger than the diameter of the impeller (260) measured up to the apex (262a).
The diffuser's (250) attachment to the front side of the stator (240) is configured by the positioning of the rear surface (254) of the diffuser (250) against the front surface of the locking protrusions (243) and the front surface of the passage protrusions (246), with each non-recessed rear portion (254b) aligned with a respective locking protrusion (243). The diffuser's (250) attachment to the rear side of the stator (240) is configured by the positioning of the front surface (253) of the diffuser (250) against the rear surface (243a) of the locking protrusions (243) and the rear surface (246a) of the passage protrusions (246), with each non-recessed front portion (253b) aligned with a respective locking protrusion (243).
A pump stage (24), configured according to the first embodiment of the invention, as it can be seen in Figure 4, has two inlet stages (El, E2). Each inlet stage (El, E2) is in communication with a respective circular channel (Cl, C2) and each circular channel (Cl, C2) is in communication with a respective outlet stage (S1, S2).
The inlet stages (El, E2) are evenly distributed along the internal perimeter of the stator (240) and the outlet stages (S1, S2) are evenly distributed along the internal perimeter of the stator (240).
In this case, the internal surface (242) of the stator (240) has two locking protrusions (243), evenly distributed along the internal perimeter of the stator (240); two stator inlets (244), each of which is located on one of the sides of the respective locking protrusion (243); two passage protrusions (246), each of which is located adjacent to the respective stator inlet (244); and two stator outlets (245), each of which is located adjacent to the respective passage protrusion (246). As shown in Figures 6 and 7, a first diffuser (250) attached to the front side of the stator (240) has two axial passages (252), which are distributed evenly along the external perimeter of the diffuser (250); two front recesses (253a) located on its front surface (253), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b); and two rear recesses (254a) located on its rear surface (254), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b). As shown in Figures 6 and 7, a second diffuser (250) attached to the rear side of the stator (240) has two axial passages (252), which are distributed evenly along the external perimeter of the diffuser (250); two front recesses (253a) located on its front surface (253), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b); and two rear recesses (254a) located on its rear surface (254), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b).
The first inlet stage (El) of a pump stage (24) configured according to the first embodiment of the invention, is formed by the alignment of an axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253b) of the second diffuser (250) attached to the rear side of the stator (240). The first circular channel (Cl) in communication with the first inlet stage (El) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240), with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The first outlet stage (S1) in communication with the first circular channel (Cl) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the first diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
The second inlet stage (E2) of a pump stage (24), configured according to the first embodiment of the invention, is formed by the alignment of a second axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253b) of the second diffuser (250) attached to the rear side of the stator (240). The second circular channel (C2) in communication with a second inlet stage (E2) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240), with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The second outlet stage (S2) in communication with the second circular channel (C2) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the first diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
A pump stage (24), configured according to the second embodiment of the invention, which can be seen in Figure 5, comprises three inlet stages (El, E2, E3), each of which (El, E2, E3) is in communication with a respective circular channel (Cl, C2, C3), each of which (Cl, C2, C3) is in communication with a respective outlet stage (S1, S2, S3). The inlet stages (El, E2, E3) are evenly distributed along the internal perimeter of the stator (240) and the outlet stages (S1, S2, S3) are evenly distributed along the internal perimeter of the stator (240).
In this case, the internal surface (242) of the stator (240) has three locking protrusions (243), evenly distributed along the internal perimeter of the stator (240);
three stator inlets (244), each of which is located on one of the sides of the respective locking protrusion (243); three passage protrusions (246), each of which is located adjacent to the respective stator inlet (244); and three stator outlets (245), each of which is located adjacent to the respective passage protrusion (246). A first diffuser (250) attached to the front side of the stator (240) has three axial passages (252), which are distributed evenly along the external perimeter of the diffuser (250); three front recesses (253a) located on its front surface (253), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b); and three rear recesses (254a) located on its rear surface (254), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b). A second diffuser (250) attached to the rear side of the stator (240) has three axial passages (252), which are distributed evenly along the external perimeter of the diffuser (250); three front recesses (253a) located on its front surface (253), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b); and three rear recesses (254a) located on its rear surface (254), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b).
The first inlet stage (El) of a pump stage (24) configured according to the second embodiment of the invention, is formed by the alignment of an axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253b) of the second diffuser (250) attached to the rear side of the stator (240). The first circular channel (Cl) in communication with the first inlet stage (El) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240) with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The first outlet stage (S1) in communication with the first circular channel (Cl) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
The second inlet stage (E2) of a pump stage (24) configured according to the second embodiment of the invention is formed by the alignment of a second axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253b) of the second diffuser (250) attached to the rear side of the stator (240). The second circular channel (C2) in communication with a second inlet stage (E2) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240), with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The second outlet stage (S2) in communication with the second circular channel (C2) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the first diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
The third inlet stage (E3) of a pump stage (24) configured according to the second embodiment of the invention is formed by the alignment of a third axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253h) of the second diffuser (250) attached to the rear side of the stator (240). The third circular channel (C3) in communication with a third inlet stage (E3) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240), with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The third outlet stage (S3) in communication with the third circular channel (C3) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the first diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
As shown in Figure 8, one circular channel (C) is delimited by the internal surface (246b) of the passage protrusion (246) of the stator (240), by the front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240), by the border (262) of the impeller (260) and by the rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240). The rotor blades (263) are positioned inside the circular channel (C). The apex (246c) of the passage protrusion (246) is aligned with the impeller apex (262a) of the border (262) of the impeller (260), dividing the circular channel (C) into two regions.
Under operating conditions, the rotation of the impeller (260) causes the fluid (F) to enter the pump stage (24) through the stage inlets (El , E2, E3);
the fluid then passes along the circular channel (Cl, C2, C3), exits the pump stage (24) through the respective outlet stage (Si, S2, S3) and moves on to the next pump stage (24).
The fluid (F) moves in a vortex in each of the two regions of the circular channels (C) as it passes through the circular channel (C), as indicated by the arrows in Figure 8.
The pressure of the fluid (F) increases gradually from the inlet stage (El, E2, E3) to the respective outlet stage (Si, S2, S3). Beneficially, the fact that the inlet (El, E2, E3) and outlet stages (Si, S2, S3) are evenly distributed along the internal perimeter of the stator (240) results in zero shear stress on the shaft (40) in each pump stage (24).
More specifically, as shown in Figure 9 for a pump stage (24) with two inlet stages (El, E2), two circular channels (Cl, C2) and two outlet stages (Si, S2), the gradual increase pressure of the fluid (F) between the first inlet (El) and first outlet (Si) causes a gradual increase in shear stress on the shaft (40), as indicated by arrows Ti, 12, T3, T4, T5 and T6. Similarly, the gradual increase in pressure of the fluid (F) between the second inlet (E2) and second outlet (S2) causes a gradual rise in shear stress on the shaft (40), as indicated by arrows Ti', 12', T3', T4', T5' and T6'. The fact that the inlet stages (El, E2) and outlet stages (Si, S2) are evenly distributed along the internal perimeter of the stator (240) means that shear stress Ti has the same magnitude and the opposite direction to shear stress Ti' so that the resultant between the two shear stresses Ti and T1' is zero. The same is true for the remaining shear stresses T2 to T6 in relation to shear stresses T2' to T6', where the resultant of the shear stress acting on the shaft (40) in each pumping stage (24) is zero.
When the progressive vortex pump is installed in a well, as shown in Figures 1 and 10, the pump assembly (20) is positioned inside a well casing pipe (10) which has an upper end (12) situated at the surface of the well (SP) and a lower end (14) in contact with the fluid (F) to be pumped. Similarly, a pumping pipe (30) runs inside the well casing pipe (10) to the well surface (SP). In a progressive vortex pump installed in a well with a surface motor assembly (50), the shaft (40) runs from the pump assembly (20) through the pumping pipe (30) to the motor assembly (50), comprising a surface electric motor (52) positioned at the well surface (SP), as shown in Figure 1. In a progressive vortex pump installed in a well with a submerged motor assembly (50'), the shaft (40) runs from the pump assembly (20) to the motor assembly (50'), comprising a submerged electric motor (54') positioned underneath the pump assembly (20), as shown in Figure 10 and 11.
As per Figures 2 and 3, the pump assembly (20) also comprises an upper radial bearing (27) located between the outlet housing (22) and a uppermost pump stage (24), a lower radial bearing (28) and an axial bearing (29), both situated between the inlet housing (21) and a lowermost pump stage (24). These bearings (27, 28, 29) are responsible for bushing of the shaft (40). A check valve (60) can also be connected to the inlet housing (21) of the pump assembly (20) of the progressive vortex pump.
Naturally, the pressure of the fluid (F) pumped increases in accordance with the number of pump stages (24) of the progressive vortex pump. As such, the number of pump stages (24) of a progressive vortex pump is configured according to the desired application. For example, Figure 2 shows a progressive vortex pump with ten pump stages (24), while Figures 3 and 11 depict a progressive vortex pump with four pump stages (24).
According to the third embodiment of the present invention, as it can be seen in Figures 12 and 13, each impeller (260) further comprises at least an axial through-hole (264) located between the central opening (261) and the border (262).
Under operating conditions, in addition to the fluid (F) pumping through the inlet stages (El, E2), the respective circular channels (Cl, C2) and the respective outlet stages (Si, S2), a front fluid film (j1) is created between the front side of each impeller (260) and the rear surface (254) of the diffuser (250) attached to the front side of the stator (240) and a rear fluid film (j2) is created between the rear side of each impeller (260) and the front surface (253) of the diffuser (250) attached to the rear side of the stator (240).
Considering that the pressure of the fluid (F) increases according to the pumping direction, the pressure of the rear fluid film (j2) is greater than the pressure of the front fluid film 01), causing an axial load acting on the impeller (260), which can result in an undesired rubbing of the impeller (260) against the diffuser (250) attached to the front side of the stator (240). The presence of the axial through-hole (264) in the impeller (260) advantageously enables a flow of fluid (F) from the rear fluid film 02) to the front fluid film (j1), causing a pressure balance between the rear fluid film (j2) and the front fluid film (j1) and, consequently, allowing an equilibrated rotation of the impeller (260) without possibility of its rubbing against the adjacent diffusers (250).
More specifically, as shown in Figure 12, each impeller (260) comprises four axial through-holes (264), each of which is located at an angle of 900 with respect to an adjacent axial through-hole (264), wherein the vertex of the angle is the axis of the impeller (260). The presence of the four axial through-holes (264) in the impeller (260) increases the pressure balance effect between the rear fluid film (j2) and the front fluid film (j1).
Each diffuser (250) further securely receives a front annular gasket (71) having an external face (711) that is salient in relation to the front surface (253) of the diffuser (250), wherein the external face (711) is in contact with a rear side of an adjacent prior impeller (260), and each diffuser (250) further securely receives a rear annular gasket (72) having an external face (721) that is salient in relation to the rear surface (254) of the diffuser (250), wherein the external surface (721) is in contact with a front side of an adjacent posterior impeller (260). For example, the gaskets (71, 72) are made on polytetrafluoroethylene.
In a pump stage (24), the rear gasket (72) of the diffuser (250) attached to the front side of the stator (240) and the front gasket (71) of the diffuser (250) attached to the rear side of the stator (240) assist to keep the impeller (260) on an equilibrated position and slightly spaced from the respective surface (253, 254) of the both adjacent diffusers (250). This feature is advantageous during pump start-up, when the front fluid film (j1) and the rear fluid film (j2) have not yet been created. Furthermore, advantageously, the gaskets (71, 72) prevent solid particles contained in the fluid (F), such as sand, to access the central portion of the pump along the shaft (40).
On the other hand, the gaskets (71, 72) do not provide a complete seal, enabling the flow of fluid (F) from the rear fluid film (j2) to the front fluid film (j1).
In the embodiment illustrated in Figures 12 and 13, the central opening (251) of each diffuser (250) receives a securely attached bushing (82), said bushing (82) comprising a central opening (823), a front side having a front annular groove (821) and a rear side having a rear annular groove (822), wherein the front gasket (71) is securely attached to the front groove (821) and the rear gasket (72) is securely attached to the rear groove (822). For example, the bushing (82) is made on bronze. According to a non-illustrated embodiment, the gaskets (71, 72) can be securely attached to grooves formed directly in the surfaces (253, 254) of each diffuser (250).
Each impeller (260) can be directly and securely coupled to the shaft (40).
The rotation of the shaft (40) results in the rotation of the impellers (260) and the shaft (40) slides in the central opening (823) of the bushing (82) of each diffuser (250).
Alternatively, as shown in Figure 13, the pump comprises a spacer bushing (92) for each impeller (260), the spacer bushing (92) having a central opening (921) and an external surface (922), wherein the central opening (921) of the spacer bushing (92) is attached to the shaft (40) in a manner that the spacer bushing (92) slides in the axial direction and is driven by the shaft (40) in the turning direction, due to a keyed joint, and the central opening (261) of the impeller (260) is securely attached to the external surface (922) of the spacer bushing (92), in a preferred embodiment due to a threaded joint. The rotation of the shaft (40) results in the rotation of the spacer bushing (92) and, consequently, the rotation of the impeller (260). In a preferred embodiment, each spacer bushing (92) has a length sufficient to a smooth portion of its external surface (922) enters into the central opening (823) of the bushing (82) of an adjacent posterior diffuser (250), in a manner that, during the rotation of the shaft (40), said smooth portion of the external surface (922) slides in the central opening (823) of the bushing (82).
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 shows a longitudinal section of a progressive vortex pump according to the present invention, installed in a well, with a surface motor assembly.
Figure 2 shows an enlarged view of region "A" indicated in Figure 1.
Figure 3 is an exploded view of a progressive vortex pump, with pump stages configured according to the first embodiment of the present invention.
Figure 4 is an exploded view of a pump stage, configured according to the first embodiment of the present invention.
Figure 5 is an exploded view of a pump stage, configured according to the second embodiment of the present invention.
Figure 6 shows a plan view of a diffuser, in accordance with the first embodiment of the present invention, emphasizing its rear surface.
Figure 7 shows a plan view of a diffuser, in accordance with the first embodiment of the present invention, emphasizing its front surface.
Figure 8 shows an enlarged view of region "B" indicated in Figure 2.
Figure 9 depicts a top view of a pump stage, with the diffusers hidden.
Figure 10 shows a longitudinal section of a progressive vortex pump according to the present invention, installed in a well, with a submersed motor assembly.
Figure 11 shows an enlarged view of region "C" indicated in Figure 10.
Figure 12 is an exploded view of a pump stage, configured according to the third embodiment of the present invention.
Figure 13 shows an enlarged view of a region of the progressive vortex pump configured according to the third embodiment of the present invention, the region is equivalent to the region "D" indicated in Figure 2.
DETAILED DESCRIPTION OF THE INVENTION
The present invention seeks to provide a progressive vortex pump assembly (20) comprising an inlet housing (21) in contact with a fluid (F) to be pumped and an outlet housing (22) connected to a pumping pipe (30); the pump assembly (20) is driven by a shaft (40) associated with a motor assembly (50). The pump also comprising a pump housing (23) with an internal surface, containing multiple adjacent pump stages (24) inside; each pump stage (24) comprising of a stator (240) contained by the pump housing (23), a first diffuser (250) attached to a front side of the stator (240), a second diffuser (250) attached to a rear side of the stator (240), and an impeller (260) mounted on the shaft (40), said impeller (260) lodged inside the stator (240). In accordance with the present invention, each pump stage (24) comprises at least two inlet stages (El, E2), each of the at least two inlet stage (El, E2) is in communication with a respective circular channel (Cl, C2), and each circular channel (Cl, C2) is in communication with a respective outlet stage (S1, S2). The inlet stages (El, E2) are evenly distributed along the internal perimeter of the stator (240), the outlet stages (S1, S2) are evenly distributed along the internal perimeter of the stator (240). The pump stages (24) are constructed and arranged such that each outlet stage (Si, S2) of a pump stage (24) is in communication with a respective inlet stage (El, E2) of the adjacent pump stage (24).
The stator (240) is ring-shaped and its external surface (241) remains in contact with the internal surface of the pump housing (23). The internal surface (242) of the stator (240) has at least two locking protrusions (243) with straight front and rear surfaces (243a), a circular internal surface (243h) and axial length shorter than the axial length of the stator (240). The locking protrusions (243) are evenly distributed along the internal perimeter of the stator (240). The internal surface (242) of the stator (240) further has at least two portions without protrusion, defining at least two stator inlets (244), each of which is located on one of the sides of the respective locking protrusion (243). The internal surface (242) of the stator (240) further has at least two passage protrusions (246) with straight front and rear surfaces (246a), axial length equal to the axial length of the locking protrusions (243) and internal surface (246b) in the shape of a curved double ramp with converging apexes (246c), where each passage protrusion (246) is located adjacent to the respective stator inlet (244). The internal surface (242) of the stator (240) further has at least two portions without protrusion, defining two stator outlets (245), where each stator outlet (245) is located adjacent to the respective passage protrusion (246). The arc length of the protrusions passage (246) is substantially longer than the arc length of the locking protrusions (243). The passage protrusions (246) extend over most of the internal perimeter of the stator (240), with one end of each passage protrusion (246) interrupted by the respective stator inlet (244) and the other end by the respective stator outlet (245), where the stator inlet (244) and outlet (245) are separated by the respective locking protrusion (243).
The diffuser (250) is disc-shaped with a central opening (251) for receiving the shaft (40) and having at least two axial passages (252), each of which is defined by an inexistence of material in a location of the diffuser's border (250). The axial passages (252) are distributed evenly along the external perimeter of the diffuser (250). The diffuser (250) further has at least two front recesses (253a) on its front surface (253), where each front recess (253a) extends in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b) and the diffuser (250) further has at least two rear recesses (254a) on its rear surface (254), where each rear recess (254a) extends in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b), wherein a non-recessed front portion (253b) adjacent to an axial passage (252) is offset in relation to a non-recessed rear portion (254b) adjacent to this same axial passage (252).
The impeller (260) is disc-shaped with a central opening (261) constructed and arranged to be mounted on the shaft (40), said impeller (260) having a border (262) shaped as a curved double ramp with converging impeller apexes (262a), and is equipped with multiple blades (263); the diameter of the impeller (260) measured up to the blades (263) is larger than the diameter of the impeller (260) measured up to the apex (262a).
The diffuser's (250) attachment to the front side of the stator (240) is configured by the positioning of the rear surface (254) of the diffuser (250) against the front surface of the locking protrusions (243) and the front surface of the passage protrusions (246), with each non-recessed rear portion (254b) aligned with a respective locking protrusion (243). The diffuser's (250) attachment to the rear side of the stator (240) is configured by the positioning of the front surface (253) of the diffuser (250) against the rear surface (243a) of the locking protrusions (243) and the rear surface (246a) of the passage protrusions (246), with each non-recessed front portion (253b) aligned with a respective locking protrusion (243).
A pump stage (24), configured according to the first embodiment of the invention, as it can be seen in Figure 4, has two inlet stages (El, E2). Each inlet stage (El, E2) is in communication with a respective circular channel (Cl, C2) and each circular channel (Cl, C2) is in communication with a respective outlet stage (S1, S2).
The inlet stages (El, E2) are evenly distributed along the internal perimeter of the stator (240) and the outlet stages (S1, S2) are evenly distributed along the internal perimeter of the stator (240).
In this case, the internal surface (242) of the stator (240) has two locking protrusions (243), evenly distributed along the internal perimeter of the stator (240); two stator inlets (244), each of which is located on one of the sides of the respective locking protrusion (243); two passage protrusions (246), each of which is located adjacent to the respective stator inlet (244); and two stator outlets (245), each of which is located adjacent to the respective passage protrusion (246). As shown in Figures 6 and 7, a first diffuser (250) attached to the front side of the stator (240) has two axial passages (252), which are distributed evenly along the external perimeter of the diffuser (250); two front recesses (253a) located on its front surface (253), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b); and two rear recesses (254a) located on its rear surface (254), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b). As shown in Figures 6 and 7, a second diffuser (250) attached to the rear side of the stator (240) has two axial passages (252), which are distributed evenly along the external perimeter of the diffuser (250); two front recesses (253a) located on its front surface (253), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b); and two rear recesses (254a) located on its rear surface (254), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b).
The first inlet stage (El) of a pump stage (24) configured according to the first embodiment of the invention, is formed by the alignment of an axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253b) of the second diffuser (250) attached to the rear side of the stator (240). The first circular channel (Cl) in communication with the first inlet stage (El) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240), with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The first outlet stage (S1) in communication with the first circular channel (Cl) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the first diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
The second inlet stage (E2) of a pump stage (24), configured according to the first embodiment of the invention, is formed by the alignment of a second axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253b) of the second diffuser (250) attached to the rear side of the stator (240). The second circular channel (C2) in communication with a second inlet stage (E2) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240), with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The second outlet stage (S2) in communication with the second circular channel (C2) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the first diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
A pump stage (24), configured according to the second embodiment of the invention, which can be seen in Figure 5, comprises three inlet stages (El, E2, E3), each of which (El, E2, E3) is in communication with a respective circular channel (Cl, C2, C3), each of which (Cl, C2, C3) is in communication with a respective outlet stage (S1, S2, S3). The inlet stages (El, E2, E3) are evenly distributed along the internal perimeter of the stator (240) and the outlet stages (S1, S2, S3) are evenly distributed along the internal perimeter of the stator (240).
In this case, the internal surface (242) of the stator (240) has three locking protrusions (243), evenly distributed along the internal perimeter of the stator (240);
three stator inlets (244), each of which is located on one of the sides of the respective locking protrusion (243); three passage protrusions (246), each of which is located adjacent to the respective stator inlet (244); and three stator outlets (245), each of which is located adjacent to the respective passage protrusion (246). A first diffuser (250) attached to the front side of the stator (240) has three axial passages (252), which are distributed evenly along the external perimeter of the diffuser (250); three front recesses (253a) located on its front surface (253), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b); and three rear recesses (254a) located on its rear surface (254), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b). A second diffuser (250) attached to the rear side of the stator (240) has three axial passages (252), which are distributed evenly along the external perimeter of the diffuser (250); three front recesses (253a) located on its front surface (253), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed front portion (253b); and three rear recesses (254a) located on its rear surface (254), each of which extending in an arc trajectory from the respective axial passage (252) until a respective non-recessed rear portion (254b).
The first inlet stage (El) of a pump stage (24) configured according to the second embodiment of the invention, is formed by the alignment of an axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253b) of the second diffuser (250) attached to the rear side of the stator (240). The first circular channel (Cl) in communication with the first inlet stage (El) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240) with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The first outlet stage (S1) in communication with the first circular channel (Cl) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
The second inlet stage (E2) of a pump stage (24) configured according to the second embodiment of the invention is formed by the alignment of a second axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253b) of the second diffuser (250) attached to the rear side of the stator (240). The second circular channel (C2) in communication with a second inlet stage (E2) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240), with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The second outlet stage (S2) in communication with the second circular channel (C2) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the first diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
The third inlet stage (E3) of a pump stage (24) configured according to the second embodiment of the invention is formed by the alignment of a third axial passage (252) of the first diffuser (250) attached to the front side of the stator (240) with a respective stator inlet (244) and with an end of a respective front recess (253a) adjacent to a non-recessed front portion (253h) of the second diffuser (250) attached to the rear side of the stator (240). The third circular channel (C3) in communication with a third inlet stage (E3) is formed by the alignment of a respective rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240) with a respective passage protrusion (246) of the stator (240), with the border (262) of the impeller (260) and with a respective front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240). The third outlet stage (S3) in communication with the third circular channel (C3) is formed by the alignment of an end of a respective rear recess (254a) adjacent to a non-recessed rear portion (254b) of the first diffuser (250) attached to the front side of the stator (240), with a respective stator outlet (245) and with a respective axial passage (252) of the second diffuser (250) attached to the rear side of the stator (240).
As shown in Figure 8, one circular channel (C) is delimited by the internal surface (246b) of the passage protrusion (246) of the stator (240), by the front recess (253a) of the second diffuser (250) attached to the rear side of the stator (240), by the border (262) of the impeller (260) and by the rear recess (254a) of the first diffuser (250) attached to the front side of the stator (240). The rotor blades (263) are positioned inside the circular channel (C). The apex (246c) of the passage protrusion (246) is aligned with the impeller apex (262a) of the border (262) of the impeller (260), dividing the circular channel (C) into two regions.
Under operating conditions, the rotation of the impeller (260) causes the fluid (F) to enter the pump stage (24) through the stage inlets (El , E2, E3);
the fluid then passes along the circular channel (Cl, C2, C3), exits the pump stage (24) through the respective outlet stage (Si, S2, S3) and moves on to the next pump stage (24).
The fluid (F) moves in a vortex in each of the two regions of the circular channels (C) as it passes through the circular channel (C), as indicated by the arrows in Figure 8.
The pressure of the fluid (F) increases gradually from the inlet stage (El, E2, E3) to the respective outlet stage (Si, S2, S3). Beneficially, the fact that the inlet (El, E2, E3) and outlet stages (Si, S2, S3) are evenly distributed along the internal perimeter of the stator (240) results in zero shear stress on the shaft (40) in each pump stage (24).
More specifically, as shown in Figure 9 for a pump stage (24) with two inlet stages (El, E2), two circular channels (Cl, C2) and two outlet stages (Si, S2), the gradual increase pressure of the fluid (F) between the first inlet (El) and first outlet (Si) causes a gradual increase in shear stress on the shaft (40), as indicated by arrows Ti, 12, T3, T4, T5 and T6. Similarly, the gradual increase in pressure of the fluid (F) between the second inlet (E2) and second outlet (S2) causes a gradual rise in shear stress on the shaft (40), as indicated by arrows Ti', 12', T3', T4', T5' and T6'. The fact that the inlet stages (El, E2) and outlet stages (Si, S2) are evenly distributed along the internal perimeter of the stator (240) means that shear stress Ti has the same magnitude and the opposite direction to shear stress Ti' so that the resultant between the two shear stresses Ti and T1' is zero. The same is true for the remaining shear stresses T2 to T6 in relation to shear stresses T2' to T6', where the resultant of the shear stress acting on the shaft (40) in each pumping stage (24) is zero.
When the progressive vortex pump is installed in a well, as shown in Figures 1 and 10, the pump assembly (20) is positioned inside a well casing pipe (10) which has an upper end (12) situated at the surface of the well (SP) and a lower end (14) in contact with the fluid (F) to be pumped. Similarly, a pumping pipe (30) runs inside the well casing pipe (10) to the well surface (SP). In a progressive vortex pump installed in a well with a surface motor assembly (50), the shaft (40) runs from the pump assembly (20) through the pumping pipe (30) to the motor assembly (50), comprising a surface electric motor (52) positioned at the well surface (SP), as shown in Figure 1. In a progressive vortex pump installed in a well with a submerged motor assembly (50'), the shaft (40) runs from the pump assembly (20) to the motor assembly (50'), comprising a submerged electric motor (54') positioned underneath the pump assembly (20), as shown in Figure 10 and 11.
As per Figures 2 and 3, the pump assembly (20) also comprises an upper radial bearing (27) located between the outlet housing (22) and a uppermost pump stage (24), a lower radial bearing (28) and an axial bearing (29), both situated between the inlet housing (21) and a lowermost pump stage (24). These bearings (27, 28, 29) are responsible for bushing of the shaft (40). A check valve (60) can also be connected to the inlet housing (21) of the pump assembly (20) of the progressive vortex pump.
Naturally, the pressure of the fluid (F) pumped increases in accordance with the number of pump stages (24) of the progressive vortex pump. As such, the number of pump stages (24) of a progressive vortex pump is configured according to the desired application. For example, Figure 2 shows a progressive vortex pump with ten pump stages (24), while Figures 3 and 11 depict a progressive vortex pump with four pump stages (24).
According to the third embodiment of the present invention, as it can be seen in Figures 12 and 13, each impeller (260) further comprises at least an axial through-hole (264) located between the central opening (261) and the border (262).
Under operating conditions, in addition to the fluid (F) pumping through the inlet stages (El, E2), the respective circular channels (Cl, C2) and the respective outlet stages (Si, S2), a front fluid film (j1) is created between the front side of each impeller (260) and the rear surface (254) of the diffuser (250) attached to the front side of the stator (240) and a rear fluid film (j2) is created between the rear side of each impeller (260) and the front surface (253) of the diffuser (250) attached to the rear side of the stator (240).
Considering that the pressure of the fluid (F) increases according to the pumping direction, the pressure of the rear fluid film (j2) is greater than the pressure of the front fluid film 01), causing an axial load acting on the impeller (260), which can result in an undesired rubbing of the impeller (260) against the diffuser (250) attached to the front side of the stator (240). The presence of the axial through-hole (264) in the impeller (260) advantageously enables a flow of fluid (F) from the rear fluid film 02) to the front fluid film (j1), causing a pressure balance between the rear fluid film (j2) and the front fluid film (j1) and, consequently, allowing an equilibrated rotation of the impeller (260) without possibility of its rubbing against the adjacent diffusers (250).
More specifically, as shown in Figure 12, each impeller (260) comprises four axial through-holes (264), each of which is located at an angle of 900 with respect to an adjacent axial through-hole (264), wherein the vertex of the angle is the axis of the impeller (260). The presence of the four axial through-holes (264) in the impeller (260) increases the pressure balance effect between the rear fluid film (j2) and the front fluid film (j1).
Each diffuser (250) further securely receives a front annular gasket (71) having an external face (711) that is salient in relation to the front surface (253) of the diffuser (250), wherein the external face (711) is in contact with a rear side of an adjacent prior impeller (260), and each diffuser (250) further securely receives a rear annular gasket (72) having an external face (721) that is salient in relation to the rear surface (254) of the diffuser (250), wherein the external surface (721) is in contact with a front side of an adjacent posterior impeller (260). For example, the gaskets (71, 72) are made on polytetrafluoroethylene.
In a pump stage (24), the rear gasket (72) of the diffuser (250) attached to the front side of the stator (240) and the front gasket (71) of the diffuser (250) attached to the rear side of the stator (240) assist to keep the impeller (260) on an equilibrated position and slightly spaced from the respective surface (253, 254) of the both adjacent diffusers (250). This feature is advantageous during pump start-up, when the front fluid film (j1) and the rear fluid film (j2) have not yet been created. Furthermore, advantageously, the gaskets (71, 72) prevent solid particles contained in the fluid (F), such as sand, to access the central portion of the pump along the shaft (40).
On the other hand, the gaskets (71, 72) do not provide a complete seal, enabling the flow of fluid (F) from the rear fluid film (j2) to the front fluid film (j1).
In the embodiment illustrated in Figures 12 and 13, the central opening (251) of each diffuser (250) receives a securely attached bushing (82), said bushing (82) comprising a central opening (823), a front side having a front annular groove (821) and a rear side having a rear annular groove (822), wherein the front gasket (71) is securely attached to the front groove (821) and the rear gasket (72) is securely attached to the rear groove (822). For example, the bushing (82) is made on bronze. According to a non-illustrated embodiment, the gaskets (71, 72) can be securely attached to grooves formed directly in the surfaces (253, 254) of each diffuser (250).
Each impeller (260) can be directly and securely coupled to the shaft (40).
The rotation of the shaft (40) results in the rotation of the impellers (260) and the shaft (40) slides in the central opening (823) of the bushing (82) of each diffuser (250).
Alternatively, as shown in Figure 13, the pump comprises a spacer bushing (92) for each impeller (260), the spacer bushing (92) having a central opening (921) and an external surface (922), wherein the central opening (921) of the spacer bushing (92) is attached to the shaft (40) in a manner that the spacer bushing (92) slides in the axial direction and is driven by the shaft (40) in the turning direction, due to a keyed joint, and the central opening (261) of the impeller (260) is securely attached to the external surface (922) of the spacer bushing (92), in a preferred embodiment due to a threaded joint. The rotation of the shaft (40) results in the rotation of the spacer bushing (92) and, consequently, the rotation of the impeller (260). In a preferred embodiment, each spacer bushing (92) has a length sufficient to a smooth portion of its external surface (922) enters into the central opening (823) of the bushing (82) of an adjacent posterior diffuser (250), in a manner that, during the rotation of the shaft (40), said smooth portion of the external surface (922) slides in the central opening (823) of the bushing (82).
Claims (4)
1. A progressive vortex pump, comprising :
(a) an inlet housing (21) in contact with a fluid (F) to be pumped;
(b) a pump housing (23), connected to the inlet housing (21) and comprising multiple adjacent pump stages (24), each pump stage (24) having:
(b1) a stator (240) having a front and a rear side, a first diffuser (250) attached to the front side of the stator (240), a second diffuser (250) attached to the rear side of the stator (240), and an impeller (260) lodged inside the stator (240); the stator (240), the diffuser (250) and the impeller (260) constructed and arranged for receiving a shaft (40) which is connected to the impeller (260) and connected to a motor assembly (50);
(b2) at least two inlet stages (E), each of the at least two inlet stages (E) in communication with a respective circular channel (C), each circular channel (C) in communication with a respective outlet stage (S); the at least two inlet stages (E) evenly distributed along an internal perimeter of the stator (240);
the respective outlet stages (S) evenly distributed along the internal perimeter of the stator (240); the pump stages (24) constructed and arranged such that each outlet stage (S) is in communication with the respective inlet stage (E) of the adjacent pump stage (24), and (c) an outlet housing (22), connected to the pump housing (23) and connected to a pumping pipe (30), wherein the shaft (40) connected to the motor assembly (50), driving the pump.
(a) an inlet housing (21) in contact with a fluid (F) to be pumped;
(b) a pump housing (23), connected to the inlet housing (21) and comprising multiple adjacent pump stages (24), each pump stage (24) having:
(b1) a stator (240) having a front and a rear side, a first diffuser (250) attached to the front side of the stator (240), a second diffuser (250) attached to the rear side of the stator (240), and an impeller (260) lodged inside the stator (240); the stator (240), the diffuser (250) and the impeller (260) constructed and arranged for receiving a shaft (40) which is connected to the impeller (260) and connected to a motor assembly (50);
(b2) at least two inlet stages (E), each of the at least two inlet stages (E) in communication with a respective circular channel (C), each circular channel (C) in communication with a respective outlet stage (S); the at least two inlet stages (E) evenly distributed along an internal perimeter of the stator (240);
the respective outlet stages (S) evenly distributed along the internal perimeter of the stator (240); the pump stages (24) constructed and arranged such that each outlet stage (S) is in communication with the respective inlet stage (E) of the adjacent pump stage (24), and (c) an outlet housing (22), connected to the pump housing (23) and connected to a pumping pipe (30), wherein the shaft (40) connected to the motor assembly (50), driving the pump.
2. The progressive vortex pump according to claim 1, wherein each impeller (260) is disc-shaped with a central opening (261) and a border (262) and comprises at least an axial through-hole (264) located between the central opening (261) and the border (262).
3. The progressive vortex pump according to any one of claims 1 or 2, wherein each diffuser (250) is disc-shaped having a front surface (253) and a rear surface (254), has a central opening (251) and securely receives a front annular gasket (71) having an external face (711) that is salient in relation to the front surface (253) of the diffuser (250), wherein the external face (711) is in contact with a rear side of an adjacent prior impeller (260), and each diffuser (250) further securely receives a rear annular gasket (72) having an external face (721) that is salient in relation to the rear surface (254) of the diffuser (250), wherein the external surface (721) is in contact with a front side of an adjacent posterior impeller (260).
4. The progressive vortex pump according to claim 3, wherein the central opening (251) of each diffuser (250) receives a securely attached bushing (82), said bushing (82) comprising a central opening (823), a front side having a front annular groove (821) and a rear side having a rear annular groove (822), wherein the front gasket (71) is securely attached to the front groove (821) and the rear gasket (72) is securely attached to the rear groove (822).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA2859250A CA2859250C (en) | 2014-08-12 | 2014-08-12 | Progressive vortex pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA2859250A CA2859250C (en) | 2014-08-12 | 2014-08-12 | Progressive vortex pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2859250A1 CA2859250A1 (en) | 2016-02-12 |
| CA2859250C true CA2859250C (en) | 2021-04-20 |
Family
ID=55299853
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2859250A Active CA2859250C (en) | 2014-08-12 | 2014-08-12 | Progressive vortex pump |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA2859250C (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2625091A (en) * | 2022-12-05 | 2024-06-12 | Jcb Res | Internal combustion engine |
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2014
- 2014-08-12 CA CA2859250A patent/CA2859250C/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CA2859250A1 (en) | 2016-02-12 |
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| Date | Code | Title | Description |
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| EEER | Examination request |
Effective date: 20190731 |