BR102016003541A2 - self-priming centrifugal pump and disassembly method - Google Patents

Abstract

self-priming centrifugal pump with improved efficiency and performance characteristics and / or features that make it easy to install, inspect and maintain. For efficiency and performance, the pump may include a stable fluid flow path that improves pump performance for a given input power, including one or more specially shaped and directed volute discharges, the lack of internal reinforcements in the wall of the pump. pump housing, a tapered inlet, and a rounded flow conduit outlet opening. For maintenance and operation, the pump may include one or more coarsely threaded drive shafts and a rotor with a concentricity feature, a combination port for both casing filling and access to the membrane inlet valve and a drive disassembly system that facilitates attachment or removal of the pump drive system.

Description

SELF-BREAKING CENTRIFUGAL PUMP AND DISASSEMBLY METHOD

HISTORIC

Field of technique.

The present invention relates to pumps and, in particular, self-priming pumps with improved performance, efficiency and / or operability.

Description of Related Art Self-priming centrifugal pumps generally include a rotary rotor positioned within an annular volute, which in turn is positioned within a pump casing. The volute forms an eye in the center where liquid enters the pump and is guided to the center of the rotor. Rotation of the rotor accelerates the liquid outward to the rotor perimeter where it is collected in the volute and discharged from the pump casing at high pressure. As the liquid is driven outward by the centrifugal force of the rotary rotor, a vacuum formed in the eye is used to draw the source liquid through the inlet and into the pump.

[003] On a wet prime pump, a centrifugal pump is arranged in a housing designed to hold water when the pump is not running. When the pump is started, the rotor in the pump casing begins to mix water with air trapped in the casing. Inside the housing, a P-trap is used to allow air to be expelled from the pump cavity through the pump outlet while water remains available to the rotor. This expulsion of air continues until sufficient air has been removed from the tubing connected to the pump suction inlet so that the rotor center is substantially flooded. At this point, the bomb reaches its peak.

In such wet prime pumps, the pump casing may include a split to separate the suction side (i.e. inlet) from the pressure side (i.e. the outlet) so that the mixture of air / water is discharged exclusively to the outlet side of the housing. In the chamber on the outlet side of the housing during the self-suction operation, air is expelled through the outlet and is prevented from flowing back into the chamber on the inlet side by the room while liquid water remains available to flow back into the room. the suction side around the submerged or partially submerged pump impeller.

Self-priming centrifugal pumps are employed in applications where the source liquid may not be uniform. For example, so-called "garbage pumps" may be self-priming centrifugal pumps in which solids suspended in the liquid may be recycled through the pump. Waste pumps are used for, for example, wastewater treatment, municipal wastewater pumping stations and waste treatment for food processing plants.

SUMMARY

[006] The present invention proposes a self-priming centrifugal pump with improved efficiency and performance characteristics and / or features that facilitate its installation, inspection and maintenance. For efficiency and performance, the pump may include a stable fluid flow path that improves pump performance for a given input power, including one or more specially shaped and directed volute discharges, the lack of internal reinforcements in the pump walls. pump housing, a tapered inlet, and a rounded flow conduit outlet opening. For maintenance and operation, the pump may include one or more coarsely threaded drive shafts and a rotor with a concentricity feature, a combination port for both casing filling and access to the membrane inlet valve and a drive disassembly system that facilitates the attachment or removal of the pump drive system. Any combination of the above features may be used in accordance with the present invention.

In one of its forms, the present invention provides a centrifugal pump comprising: a drive mechanism; a rotor attached to the drive mechanism; a housing containing an inlet and an outlet. The housing includes: an inlet side wall with an inlet opening formed therein; an exit side wall joined to the entrance side wall to form a cavity within the housing, the exit side wall with an exit opening; a volute arranged in the housing and in fluid communication with the inlet opening and the outlet opening, the volute having a central opening sized to receive the rotor and a spiral-shaped fluid channel such that the fluid channel advance radially outward toward a volute discharge opening, and the volute discharge opening defines a longitudinal axis of discharge extending through the outlet opening. The volute is adapted to receive externally accelerated fluids through the rotor, drive the fluids radially outward through the spiral-shaped fluid channel and discharge the fluids along the longitudinal discharge axis toward the outlet opening.

In another form, the present invention provides a centrifugal pump including: a drive mechanism; a rotor attached to the drive mechanism; a membrane valve; a housing with one inlet and one outlet. The housing includes: an inlet side wall with an inlet port formed therein, the membrane valve positioned at the inlet port to receive fluid flow into the casing through the inlet port while preventing fluid flow to outside the housing through the opening inlet; an exit side wall joined to the entrance side wall to form a cavity within the housing, the exit side wall with an exit opening; a separating wall interposed between the inlet side wall and the outlet side wall to form a pump inlet chamber and a pump outlet chamber, the partition wall having an internal drive opening positioned to permit communication fluid between the inlet chamber and the outlet chamber through the internal opening of the drive; a combination port formed in the housing next to the membrane valve, the combination port sized and positioned to allow access to the membrane valve by a maintenance person and to allow fluid to be added to the inlet pump chamber; and a filler opening formed through the housing on an opposite side of the partition wall as the combination door, such that the filler opening allows fluid communication between the pump outlet chamber and the environment through which the liquid Added to the pump inlet chamber is allowed to flow into the pump outlet chamber through the internal opening of the drive while air contained in the pump outlet chamber is released into the atmosphere through the filler opening.

In yet another form thereof, the present invention provides a centrifugal pump including: a drive shaft having a first coarse thread and a first centering feature; a rotor attached to the drive shaft, the rotor having a second coarse thread and a second centering feature, the second coarse thread engaging with the first coarse drive shaft thread to selectively rotatably secure the drive shaft to the rotor , and the second centering feature engaging with the first centering feature to concentricly align the rotor with the drive shaft.

In yet another form thereof, the present invention provides a centrifugal pump comprising: a drive mechanism; a rotor attached to the drive mechanism; a housing with one inlet and one outlet and one drive disassembly system. The housing includes: an inlet side wall having an inlet opening formed therein; an exit side wall joined to the entrance side wall to form a cavity within the housing, the exit side wall having an exit opening; a hole that extends internally from the outside of the outlet side wall through which the hole is accessible to the pump user. The drive disassembly system includes: a guide rail sized to be comfortably received into the booster hole; and a track with a bearing and a flange attached to the bearing, the bearing sized to be slidably received on the guide rail while the flange is secured to the drive mechanism such that the drive mechanism can be mounted or removed from the housing. while being supported by the guide rail.

In yet another form thereof, the present invention provides a method of disassembling a centrifugal pump drive mechanism, the method including: inserting a rail into a hole formed in a pump casing such so that the rail fits perfectly into the hole; slide a guide rail along the rail and in engagement with the pump; attach the guide rail to the drive mechanism by keeping the guide rail in sliding engagement with the rail; and disconnect the drive mechanism from the housing and slide the drive mechanism out of the housing using the rail support.

BRIEF DESCRIPTION OF DRAWINGS

The aforementioned and other features of the present disclosure, as well as how to achieve them, will become more apparent and will be better understood by reference to the following description of embodiments of the present invention, together with the accompanying drawings. These features mentioned above, in addition to other features of the invention, may be used in any combination or permutation form.

Figure 1 is an elevational cross-sectional view of a centrifugal pump made in accordance with the present invention taken along line I-I of Figure 8, but with the drive disassembly system of Figure 8 removed;

Fig. 2 is an enlarged view of a part of Fig. 1 illustrating a connection of the drive shaft to the pump rotor;

Fig. 3 is a perspective view of the pump shown in Fig. 1 illustrating a membrane access door and the filler opening;

Figure 3A is a perspective view of an alternative pump casing in accordance with the present invention;

Fig. 3B is another perspective view of the alternative pump casing shown in Fig. 3A;

Fig. 4 is an elevational cross-sectional view of the pump casing shown in Fig. 1 taken along line IV-IV of Fig. 1;

Fig. 5 is an elevational cross-sectional view of the pump casing shown in Fig. 1 taken along line V-V of Fig. 4;

Fig. 6 is a bottom plan view of the cross-section of the pump casing shown in Fig. 1 taken along line VI-VI of Fig. 1;

Fig. 7 is an elevational view of the partial cross-section of the pump shown in Fig. 1 along line VII-VII of Fig. 8 illustrating the pump outlet;

Fig. 8 is a perspective view of the pump shown in Fig. 1, and includes a drive disassembly system attached thereto;

Fig. 9 is another perspective view of the pump shown in Fig. 8 illustrating removal of the drive mechanism by means of the drive disassembly system;

Fig. 10 is a perspective view of the drive shaft and rotor shown in Fig. 1;

Fig. 11 is an exploded partial cross-sectional view of the pump shown in Fig. 1 illustrating a rotor inspection port;

Fig. 12A is a cross-sectional perspective view of the pump casing shown in Fig. 1; and Fig. 12B is a perspective view of the pump shown in Fig. 1 illustrating features on the inlet side of the pump.

Figure 13 represents the measurements of margins, tolerances and crown gaps for single centered Acme thread centering - Classes 2C, 3C and 4C.

Corresponding reference characters indicate corresponding parts throughout the various views. The exemplifications set forth herein illustrate embodiments of the present disclosure and such exemplifications should not be construed as limiting the scope of the invention in any way.

DETAILED DESCRIPTION

The present invention provides a self-priming centrifugal pump, shown as a pump 10, for example in Figures 1, 3 and 8, which includes various features that provide increased pump efficiency and / or facilitate its installation, inspection and testing. and maintenance, among other benefits.

For example, as shown in Figure 1 and described in detail below, the centrifugal pump (10) includes a volute (34) with a geometry and configuration that tends to "target" the pressurized fluid to the outlet port ( 20) to assist in efficient fluid discharge. The outlet port (20) has a gradual rounded transition area (102) that extends to the outlet adapter (98) to further facilitate the discharge of pressurized fluid with minimal loss. Attachment projections (104) are rounded and similarly shaped to minimize swirling and turbulence in the vicinity of outlet port (20) and to efficiently direct flow through outlet port (20).

In addition, both the pump inlet chamber (30) and pump outlet chamber (32) are substantially free of reinforcements, which also promotes stable and laminar fluid flow through the chambers (30, 32). ), and minimizes turbulence. More particularly, the pump inlet and outlet chambers 30, 32 are each substantially defined by the respective inner surfaces of the housing 12, and the respective partition wall surfaces 24, as shown in Figure 5. and described below. These surfaces are substantially free of reinforcements such that no reinforcement ribs are disposed within the fluid flow paths through the chambers (30, 32). In order to provide resistance to the housing (12), the gussets (100) are located on the outer surface of the pump housing (12) as shown, for example, in Figure 3. An alternative configuration of gussets 100A is shown in the figures. 3A and 3B.

Further efficiency and performance is achieved by positioning the drain plugs (130, 134) (Figures 11 and 12B, respectively) and their associated drainage channels (132) (Figure 11) and 136 (Figure 12A). ) at locations outside the volute flow path (34) to provide gravitational drainage of the pump casing (12) without introducing any characteristics in the vicinity of the volute (34) that may cause turbulence or swirls and therefore mitigate abrasive wear during pump operation.

With respect to operability, the pump 10 includes the combining port 82 (FIG. 3) which functions as a membrane access portion and a fill port for the addition of liquid (e.g. water). in the housing (12) for the vacuum pump operation. The filler opening (92) facilitates this suction function, while the combination door cover (84) provides a single integral unit to cover both the door (82) and the opening (92). The combination door (82) reduces manufacturing cost and complexity by requiring only one opening through the housing (12) for two functions while at the same time facilitating pump installation and maintenance (10) as described. below, down, beneath, underneath, downwards, downhill.

The pump (10) can also be used in conjunction with the drive disassembly system (50) (figures 8 and 9) to facilitate removal of the drive mechanism (40) from the pump housing (12) for service or inspection. Reinstallation of the drive mechanism (40) is also facilitated by the drive disassembly system (50) as described in detail below.

Within the drive mechanism (40), the drive shaft (46) engages with the rotor (44) through thick threads (72, 76) (figure 2) which facilitate installation and prevent transverse installation. In order to maintain a high level of concentricity between the drive shaft (46) and the rotor (44), the thick threads are reinforced with a tight tolerance fit between the distal block (70) formed on the drive shaft (46). and the hole (74) formed in the rotor (44) as shown in figure 2.

The pump (10) further includes devices for inspection and maintenance of the rotor (44) at the inlet side of the housing (12) by removing the inspection cover (110) and the inspection side wear plate ( 112) as shown in figure 11.

Several features of centrifugal pump (10) are described below. The embodiment described below is not intended to be exhaustive or to limit the invention to the precise forms disclosed in the following detailed description. Instead, the embodiment is chosen and described so that those skilled in the art can use their teachings. In addition, it is contemplated that a pump made in accordance with the present invention may include any of the following characteristics, or any combination of the following characteristics, and may exclude any number of the following characteristics as required or desired for a specific application. .

Smooth Internal Surfaces The centrifugal pump (10) includes a number of features related to the pump housing (12) that, individually and in combination, contribute to increased pump efficiency and performance by minimizing turbulent flow and swirling fluid as it passes. from the inlet port (18) to the outlet port (20) through the pump inlet chamber (30) and the pump outlet chamber (32).

For example, starting at the inlet port 18 shown in Figure 1, the inlet adapter 90 may include a tapered portion 91 with a flow area that gradually increases as fluid passes through the conduit. (140) (figure 3) through the adapter (90) towards the inlet opening (18) in the housing (12). For example, and as shown in Figure 1, the flow area may be substantially constant through a cylindrical part of the adapter (90) and may then gradually increase through a tapered (e.g., tapered) part (91) which continuously increases the diameter of a circular flow area. This continuous and gradual increase provides stable, low-turbulent liquid flow from the inlet duct (140) through the inlet port (18) and into the pump inlet chamber (30) as the tapered portion (91) gradually relieves fluid pressure at the inlet port (18) and allows fluid to make a slower and more stable transition from the direction of its downward flow through the pump chamber (30) toward the rotor (44).

In addition, the presence of the tapered portion 91 in the inlet adapter 90 allows the centrifugal pump 10 to be used in a variety of nominal sizes for the inlet duct 140 and the outlet duct. (142) (Figure 3) for certain sizes of inlet and outlet openings (18, 20). For example, adapters (90 and 98) may allow a certain size of centrifugal pump (10) (for example, a 3 inch, 4 inch or 6 inch pump, referring to the nominal size of the outlet duct (142)). ) can be used with various sizes of inlet and outlet ducts (140, 142) by providing the appropriate set of adapters. For ducts (140 or (142) that do not match the size of openings (18) or ( 20), respectively, a tapered part (e.g., tapered part 91) allows for this size disparity while preventing or minimizing a lack of fluid efficiency from an abrupt change in conduit flow area (140, 142) and openings. 18, 20, respectively It is envisioned that either or both of the inlet and outlet adapters 90, 98 may include a tapered part to facilitate stable flow as required or desired for a specific application.

In an exemplary embodiment, the inlet and outlet ducts 140 and 142 are provided with the same nominal size, while opening 18 is larger than opening 20. Tapered part 91 provides a gradual "structure" of the flow path area through the inlet adapter (90) to accommodate a fluid inlet conduit (140) of a flow area smaller than the inlet opening ( 18). At the same time, the outlet adapter (98) may have a flow area substantially equal to the outlet opening (20) in order to receive pressurized flow from the volute (34) without preventing steady flow. The output adapter (98), therefore, may not need a tapered part similar to the tapered part (91) of the input adapter (90).

After passing through the pump inlet chamber (30), fluid is drawn into the channels (45) of the rotor (44) which rotates under a power supplied by the drive shaft (46) to accelerate the fluid outward. and into the fluid channel (36) of the volute (34), as best seen in Figures 4 and 5. In the illustrative embodiment of Figures 1, 11, the rotor (44) is a "double bend" design. which includes two fluid channels (45) defining a radially outwardly spiraling fluid flow path. Although the illustrated design of the rotor (44) is well suited for a "garbage pump" application to the centrifugal pump (10) (for example, where the pump (10) accepts fluids with suspended solids or other nonuniform characteristics of It is appreciated that other designs may be used for the rotor 44 as needed or desired for a specific application.

Pressurized fluid discharged from the rotor (44) to the volute (34) flows through the spiral-shaped volute fluid channel (36) to the discharge opening (38) which defines the discharge axis (AV) " intended "to pass directly through the outlet (20) as described below. Pressurized fluid is directed through the discharge opening (38) along the volute discharge (AV) axis such that fluid passes directly through the pump outlet chamber (32) toward the outlet opening (20). ) as shown in figures 4 and 5 and described in detail below.

As pressurized fluid approaches outlet port (20), outlet transition area (102) and attachment projections (104) provide smooth, rounded transition surfaces to facilitate stable fluid flow from the pump outlet chamber (32) to the outlet adapter (98) and finally to the outlet conduit (142) (figure 3). Specifically, with reference to Figure 5, the transition between the substantially horizontal upper wall of the outlet side wall (16) of the housing (12) to the substantially vertical side wall of the outlet adapter (98) (i.e. the "edge of the outlet aperture 20 is a rounded transition (also known as "fillet") in which the radius of the fillet is generally proportional to the thickness of the adjacent portion of the outlet side wall (16). In one embodiment For example, the fillet radius ranges from as small as equal to the minimum thickness of the exit side wall 16 to as large as 1.3, the minimum thickness. of the fillet around the outlet opening (20) is 0.75 inches while the wall thickness is 0.57 inches, although of course these nominal values may vary depending on the size and power of the pump (10) In embodiments In examples, the nominal radius of the fillet is at least 131% of the minimum wall thickness.

Mounting projections (104) may be provided on the inner surfaces of the housing (12) (i.e. within the pump inlet and / or outlet chambers (30, 32) adjacent to the inlet and / or outlet openings. The fastening projections (104) provide sufficient material to be available for threaded bolt engagement (105) with the housing (12) for connecting the adapters (90, 98) to the inlet side walls. and outlet (14, 16), respectively, as shown in Figure 1. Referring to the description of the protrusions (104) adjacent to the outlet opening (20) in Figures 5-7, it can be observed that the protrusions (104) have a rounded profile that facilitates stable flow from the outlet chamber (32) to the outlet adapter 98 through the outlet opening (20).

As can best be seen from FIGS. 1 and 7, the fastening projections (104) provide a convex and gently rounded distal surface at their respective ends, and a transition to an annular concave surface that forms the junction between the surface of the surface. convex end and the adjacent inner surface of the outlet side wall (16). This concave-to-convex transition avoids sharp edges or other sharp features within the fluid flow path in the outlet chamber (32) and, in particular, avoids such sharp features in the fluid flow path along the outlet discharge axis. volute (AV). In this way, rounded clamping projections (104) prevent or minimize turbulence in fluid flow, which may otherwise compromise pump efficiency and performance.

Although the lower pressure space in the inlet chamber (30) is less susceptible to adverse performance impacts related to the shape of the projections (104) around the inlet opening (18) or any other threaded opening in the housing. (12), the same round shape of the projections (104) is provided for maximum pump efficiency.

Referring now to the bottom plan view of the securing projections (104) in Figure 6, three securing projections (104) closest to the volute discharge opening (38) are illustrated. In the context of Figure 6, the three protrusions (104) in question are shown along the right part of the outlet opening (20) and inside the outlet chamber (32). As illustrated, these protrusions (104) have a "droplet" shape, wherein a tip end of the droplet points toward the outlet opening (20). This droplet shape of the fastening projections (104) promotes substantially laminar flow over the outer surface of the projections (104) as fluid discharged from the volute (34) advances toward the outlet opening (20).

Referring now to Figures 3 and 3A-3B, another flow enhancing feature is illustrated in the form of external reinforcements (100 and 100A), respectively, which are integrally and monolithically supplied as an outer casing ( 12 and 12A), respectively. Reinforcements (100 and 100A) serve to both reinforce and stiffen the housing (12) to avoid or minimize any potential bulging or bending of the housing material (12) from the substantial (positive or negative) pressures that may be developed. in the pump chambers (30, 32).

In figure 3, a vertical central reinforcement (100) extends from an upwardly lower base (106) to the outlet opening (20) and opening adapter (98) on both sides of the housing ( 12). For purposes of the present discussion, the "bottom" of the pump (10) is at the base (106) while the outlet opening (20) and the adapter (98) are at the "top" of the pump (10). “Vertical” is the direction that extends from the bottom up. In addition, a series of two-sided ribs (100) extend from the inlet side of the housing (12) along the inlet side wall ( 14), and terminate in the vertical center rib 100. An additional set of two-sided ribs 100 extend from the drive side of the housing 12 along the outlet side wall 16 , and ends at the central vertical reinforcement (100) in staggered vertical positions relative to the inlet side reinforcements (100), so that each of the drive side reinforcements (100) intersect the vertical central reinforcement (100) in a different vertical position of each of the inlet side gussets (100) as shown in figure 3. For the purposes of this discussion, the "front" of the pump (10) is considered to be the side from which the shaft of drive (46) protrudes, and the "back" of the pump (10) is the side that includes the opening (18) and the adapter (90). The "two-sided" direction is substantially perpendicular to the "vertical" direction as shown in figure 3.

On the vertical face of the outlet side wall 16, all the ribs 100 radially radiate outwardly from a common center, as best shown in Figure 8. In particular, nine ribs 100 are provided. extend radially outwardly along the vertical face of the external drive opening (22) (figure 9), around the corner at the junction between the vertical and lateral faces of the outlet side wall (16), and extend back to the vertical reinforcement (100) as mentioned above. A similar set of six radially outwardly extending ribs 100 is formed on the vertical face of the inlet side wall 14, as best seen in FIG. 12B.

An alternative housing 12A having a different arrangement of reinforcements 100A is shown in Figures 3A and 3B. For purposes of the present invention, the housings (12, 12a) having the reinforcements (100, 100A), respectively, are interchangeable with the other components of the pump (10). Accordingly, a reference to the housing 12 is here also a reference to the housing 12A unless otherwise stated. In addition, the housing 12A is substantially similar to the housing 12 described herein, with housing reference numbers 12A corresponding to housing reference numbers 12, except with an "A" attached. Frame structures (12) correspond to similar structures indicated by corresponding frame reference numbers (12A), unless otherwise indicated.

As best seen in Figure 3A, five ribs (100A) generally extend radially outwardly from a central area of the outlet side wall (16), similar to radially disposed ribs (100) and described above. However, only the two lowermost reinforcements (100) extend horizontally from the edge around the external opening of the drive (22), around the corner at the junction between the vertical and lateral faces of the output side wall. (16), and extend in reverse toward the inlet side wall (14). An upper reinforcement (100A) extends vertically along the vertical face of the outlet side wall (16), but unlike the lower reinforcements (100A), it does not adhere to the edge around the external opening of the drive (22). ). Two intermediate ribs (100A) are disposed between the upper and lower ribs (100A), and extend radially outwardly from the central area of the outlet side wall (16). Like the upper gusset (100A), the intermediate gussets (100A) do not adhere to the edge around the external opening of the drive (22).

As shown in figures 3A and 3B and, in contrast to the housing (12) described above, the housing (12A) has no vertical reinforcement and no reinforcements on the inlet side wall (14). In the illustrated embodiment, the ribs (100A) are provided only on the high pressure (i.e. outlet) side of the housing (12A), which provides resistance to bulging or bending of the outlet side wall (16). However, the size, quantity and extent of reinforcements 100A are optimized as shown in Figure 3A and described above to provide such strength with a minimum of additional material and expense. The low pressure (i.e. inlet) side of the housing (12A) is not reinforced because, in the illustrated application, the inlet side wall (14) may be sufficient in itself to prevent excessive bending at from the relatively low (and negative) pressures experienced in the pump inlet chamber (30) (figure 5).

The arrangement of the reinforcements (100 and 100A) only on the outer surface of the housings (12 and 12A) allows their reinforcing function to be fulfilled without the introduction of reinforcements into the pump chambers (30 and 32). More particularly, the portion of the pump inlet chamber (30) extending from the inlet opening (18) to the rotor (44) is free of reinforcement along the inner surfaces of the inlet side wall (14). as well as along the surface of the partition wall (24) cooperating with such internal surfaces to form the inlet chamber (30). Likewise, the portion of the pump outlet chamber 32 generally disposed between the volute discharge opening 38 and the outlet opening 20 is also free of internal reinforcements along the internal surfaces of the volute wall. exit side (16) and the adjacent part of the partition wall (24) that cooperates with such internal surfaces to form the exit chamber (32). Accordingly, the pump chamber parts (30) and (32) directly disposed in the fluid flow path passing through the centrifugal pump (10) are free of any reinforcements or other features designed for selective strengthening of the pump walls. inlet and outlet sides (14, 16).

Advantageously, the lack of reinforcements or other hardening characteristics in the flow paths within the casings 12 and 12A facilitate flow with minimal turbulence and swirls, which reduces wear caused by liquid and solids. suspended while preserving hydraulic efficiency. However, the provision of external reinforcements (100, 100A) as shown in Figures 3 and 3A-3B respectively (described in detail above) provides the strength and stiffness of the housings (12, 12A) associated with such strengthening characteristics. .

Volute Discharge [0058] In Figure 4, the volute discharge (AV) axis is shown from the front, ie from a perspective facing a "plane of rotation" of the rotor (44) that is perpendicular to its axis of rotation. In figure 5, the volute discharge shaft (AV) is illustrated from the side, i.e. from a perspective facing a vertical central plane containing the rotor axis of the rotor (44).

Figure 4 illustrates that the spiral path of the volute 34 does not end in a discharge opening defining a vertical discharge axis, but rather continues its spiral path to produce the axis ( AV) illustrated which directs fluid flow from the discharge port (38) through the center plane of the housing (12) and back to the outlet port (20), which is on the opposite side of the central plane. The channel (36) is a spiral-shaped structure as illustrated and defines a corresponding spiral-shaped flow axis centrally located in channel (36) extending through the entire length of channel (36). As fluid flows through the channel (36), it follows this spiral-shaped flow axis until it is discharged into the discharge opening (38).

In the illustrated embodiment, the discharge axis (AV) is tangent to that spiral-shaped flow axis in the discharge opening 38, and is oriented or "intended" to pass directly through the outlet opening. (20). In an exemplary embodiment, the axis (AV) is also perpendicular to a plane defined by the discharge opening (38). This angular and intended shaft (AV) arrangement directs pressurized fluid flowing from the discharge opening (38) directly to the outlet opening (20) thereby minimizing turbulence, deceleration or swirling fluid along of the side walls of the outlet side wall (16) of the housing (12) as fluid flows to and through the outlet opening (20).

Referring to the side view of Fig. 5, the axis (AV) is also shown to be at angled front with respect to a vertical direction, i.e. angled with respect to substantially vertical walls of the inlet and side walls. 14 and 16, also being in a non-perpendicular position with the substantially horizontal base 106 and opposing the tops of the inlet and outlet side walls (14, 16). In addition, the shaft (AV) is generally directed toward the outlet port 20, as seen in the side section view of figure 5, to discharge the outlet port 38 with a maximum volume of fluid received at the outlet. outlet port (20), and a minimum volume of fluid traveling at high speed along the partition wall (24) disposed near the volute (34). Directing fluid from the discharge opening (38) along an inclined path away from the adjacent partition wall (24) prevents frictional interaction between the fluid and partition wall (24) and thereby promotes efficient operation. the centrifugal pump (10).

Drainage Channels Referring now to Figures 11, 12A and 12B, the drainage channels 132 (Figure 11) and (136) (Figure 12A) passing through selected locations within the housing (12) are illustrated. . The drainage channels (132, 136) are both in direct fluid communication with the respective lower portions of the pump outlet chamber (32) such that the drainage plugs (130, 134) (figure 12B), respectively, may be removed to allow liquid trapped in the pump outlet chamber (32) to be drained from the housing (12) by gravity and without reversing the centrifugal pump (10). In particular, the two drainage channels (132, 136) are in direct fluid communication with a reservoir region (138) formed in a lower part of the housing (12).

In the illustrated embodiment, centrifugal pump 10 has a wet prime self-priming pump design. In the illustrated self-priming pump design, the housing (12) is designed to retain water or other liquid within the reservoir region (138) when the pump (10) is not operating. The rotor (44) may extract liquid stored in the reservoir region (138) upon activation of the pump (10), and may expel any trapped air from the outlet opening (20) while collecting additional liquid until a vacuum in the Inlet port (18) is created to draw additional liquid into the housing (12) from the source. At this point, the pump is "ready" and ready for regular service. As described in detail below, liquid in the reservoir region (138) may initially be introduced into the housing (12) through a filler and membrane access port combination port (82) (Figure 3). In the context of the present invention, "air" in the housing is the non-pumpable fluid (i.e. gas) that remains in the housing during normal operation.

As best seen in Figure 12A, the reservoir region (138) has a central portion which is in direct fluid communication with the rotor (44), while the remainder of the reservoir region is separated from the rotor (44). by the wall that forms the volute (34). As illustrated in FIGS. 11 and 12A respectively, the drainage channels (132, 136) are arranged on the outside of the volute flow path and on opposite sides of the volute (34) and rotor (44) and are therefore in indirect fluid communication with the central part of the reservoir region (138) accessed by the rotor (44). That is, the flow of the central portion of the reservoir region (138) through the drainage channels (132) and / or (136) would require the fluid to migrate first to the other parts of the reservoir region (138) (i.e. the parts not in direct fluid communication with the rotor (44) and then entering channel (132) or (136).

Thus, the drainage channels (132, 136) do not form any openings or other features that are in direct fluid communication with or form any part of the volute (34). Consequently, the drainage channels (132, 136) do not interrupt or affect the rotor fluid mechanics (44). For purposes of the present invention, two distinct areas of fluid are in "direct" fluid communication if fluid exchange between the two areas does not require the fluid flow path to change direction or otherwise "curve" . " On the other hand, two distinct areas of fluid are in "indirect" fluid communication if fluid exchange between the two areas requires the fluid flow path to change direction or otherwise "bend." Fill / Inspection Combination Door [0066] Referring now to Figure 3, the door (82) is shown at an upper end of the inlet side wall (14) of the housing (12). Port 82 serves as a combination port, performing two functions: access to membrane valve 80 and related structures for, for example, installation, replacement or maintenance; and as a filler port for adding liquid to the housing (12) and particularly for adding liquid to the reservoir region (138) shown in figures 1 and 11 and described above.

Referring to Figure 1, the membrane valve (80) is shown in its correct position installed on top of the inlet adapter (90). In an exemplary embodiment, the membrane valve (80) is formed as a resilient polymer or rubber material that abuts against the annular inner surface of the inlet adapter (90) (i.e. the adjacent tapered part (91)). to prevent fluid flow from the pump inlet chamber (30) back through the inlet port (18) and inlet adapter (90) while bending or "resiliently" shaking their position seated on a live hinge (81) (figure 3) so that liquid can be freely admitted into the pump inlet chamber (30) through the inlet adapter (90) and inlet port (18). 81) connects the membrane valve (80) to a valve mounting part (83), which is connected to the adapter (90) by fasteners (88) and retainers (86A, 86B) as shown.

When the centrifugal pump (10) is in service, the inlet conduit (140) and the outlet conduit (142) may be rigidly attached to the adapters (90, 98) respectively. In addition, the base (106) of the housing (12) may be attached to the underlying surface, as by mounting screws (107) shown in figure 3. For these and other reasons, disconnecting the input adapter (90) to access membrane valve 80 and its associated structures may not be practical or time-efficient. However, as the membrane valve 80 may be made of a relatively soft and resistant material such as rubber or polymer, the need for inspections, maintenance or repairs may become relatively frequent. The combination port (82) provides access to the membrane valve (80) from the top of the centrifugal pump (10), which is usually the most accessible part for a service person when the pump 10 is mounted in place. of service.

To allow or prevent access to the door (82), a combination door cover (84) is provided. When the lid (84) is affixed to the housing (12) by fasteners (114), the filler port lid portion (94) provides a seal (in cooperation with an O ring positioned over the periphery of the door (82) at membrane port port 82 which fluidly isolates the pump inlet chamber 30 from the environment and thereby allows vacuum or suction pressure to develop within it for proper operation of the When removed, as shown in Figure 3, port (82) allows a service person to remove fasteners (88), retainers (86A and 86B), and membrane valve (80) for inspection, In addition, as the door (82) is moved in a two-sided direction relative to the membrane valve (80), as shown in Figure 1, removal of the door cover (84) It also allows visual inspection of membrane valve (80) and its associated structures without removing the same of the input adapter (90).

Referring again to Figure 3, the housing (12) includes the filler opening (92) which provides selective fluid communication between the pump outlet chamber (32) and the environment. The filler opening (92) facilitates the use of the combination port (82) as a liquid inlet filler port in the housing (12) and specifically for the reservoir region (138) on the inlet side, allowing the displaced air is vented to the atmosphere from the pump outlet chamber (32) through the opening (92) as water flows into the reservoir region (138) on the inlet side. The combination port cover (84) also serves to fluidly isolate the pump outlet chamber (32) from the environment when the cover (84) is installed over the housing (12) by covering the opening (92) with the filler cap portion 96 (and an O-ring disposed over the periphery of the aperture 92. As best seen in Figure 3, the filler aperture cap portion 96 is formed as an extension of the filler cap portion (94) to pass over the dividing wall (24) toward the filler opening (92) In the illustrated embodiment, the filler cap portion (94) and portion of the filler cap (96) are integrally and monolithically formed as a single component.

In an exemplary embodiment, the fasteners (114) used to connect the combination door lid (84) to the combination door (82) include a flat and enlarged fastener head having a fastener opening (116) formed in it. For field inspections and maintenance, the field surface fasteners (114) make it easy to remove and install the combination door cover (84) by engaging any key or clamp with the hand of the service person. capable of enclosing the flat head portion of the fasteners (114). As an alternative, as shown in Fig. 9, the rod (R) may be passed through the opening of the fastener (116) to provide a leverage effect.

Mounting and aligning the drive shaft and rotor Figures 1, 2 and 10 illustrate the connection between the drive shaft (46) and the rotor (44). As described in more detail below, this connection facilitates initial assembly and subsequent reassembly by providing a coarse threaded coupling that is easy to thread and difficult to cross-thread. In order to maintain a desired concentricity between the rotor shaft (44) and the shaft (46) drive shaft (AD), the distal block (70) formed on the drive shaft (46) defines a tight fit with a corresponding hole (74) formed in the rotor (44).

Referring to Figure 1, the drive shaft (46) projects from a front surface of the housing (12) as part of the drive mechanism (40) attached thereto. In addition to the drive shaft (46), the drive mechanism (40) includes a series of bearings (47) supported by the drive shaft housing (42) and rotatably supporting the drive shaft (46) such that the drive shaft (46) is free to rotate relative to the housing (42). The drive side wear plate (48) is connected to the drive shaft (46) and biased by a biasing element (shown as a compression spring) for firm engagement with the drive shaft housing (42) and away from contact with the rotor (44). The cover plate (49) connects to the front (i.e. outer) surface of the housing (42) to retain and protect the bearings (47) (which may be, for example, a ball bearing or a roller bearing ). The rotor (44) is fixed to the drive shaft (46) (as described below) and constitutes the final component of the drive mechanism (40).

When the drive mechanism (40) is initially assembled or reassembled (for example, after inspection or maintenance) as shown in figure 10, the male threads (72) of the drive shaft (46) are engaged with the correspondingly formed female threads (76) of the rotor (44) for affixing the drive shaft (46) to the rotor (44), as best seen in Figure 2. In the illustrated embodiment, the threads (72) and (76) These are thick threads that promote easy initial thread alignment and engagement and, accordingly, prevent cross-threading or other incorrect engagement of male threads (72) with female threads (76). In an exemplary embodiment, best seen in Figure 2, threads 72 and 76 are trapezoidal thread shapes, sometimes referred to as "Acme" threads, which provide a relatively flexible thread coupling and robust thread resistance. crossed An exemplary embodiment of "thick" trapezoidal threads usable in connection with the present invention are the Acme "Centralized Threads" of tolerance class 4C as defined in ANSI / ASME B1.5 - 1997, the complete invention of which is expressly incorporated by reference herein. The use of such thick trapezoidal threads (72, 76) ensures that when the drive shaft (46) is inserted through other components of the drive mechanism (40) and initially engaged with the rotor (44), the rotation of the drive shaft (46) with respect to the rotor (44) in the tightening direction causes proper thread coupling.

Further details on class 4C centering threads according to the present invention are provided in Figure 13 and Tables 7a, 7b and 8-11 below.

Table 7a. Single Entry Acme Thread Centralization in accordance with the American National Standard - Diameter Determination Formulas (ASME / ANSI Bl.5-1988) i £ • 1, &, ί £ ι 3 1 I ■ 5 1 I «ΐ ΤΒ - ί Μ Μ, * £, a 'α! «::’ I ■ # β - ti i Λί! jO, '' I:! m: ί Μ Μ? :1 ! 1 - ! »■ I, ι ε ■:! ! 1 i Ί, ί ι 1 si - i m ■ 1 1 «s 1 ΐ ι * & 3 | s I

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1 | I © V) C0 W Ο,! 2 Ε ~ 4 = uri -β a 3 * 2 sj 'OJ f * y Ε "3 Ο 5Λ m fP wi o o u S £ _ S â 3 i li io 8 a M mm ui-2 1 S <g s_ lü T3 T3 * —OCO «npsw js b £ * <- ®« CL 'O oo - £ a. »" "" * * 1 * u, ™ Ά Mffil Ul * -----------! Z i 1 5 I ■? ! â 13 3 | = -g flowed u? σ τ} o E <S "4-1 Sí i ^ JU ._ â! wc -í®? u • * 3 2 * £ 1Ü c“ á »! 'í * § # agm Just -H e # ws = 'cu'. o <■ 1 o '£ ra "E £" o «2 ■ * J | -2 õ · = E m £ 1 3 ° i-í T |, -a? ϊ S'» 1 Sfi «U s =« (rt M - «^ 3 <ui® ■ £ g 1ϊ ^« E | .ar S -fs «-Si g £ c, ΐ -S υ p | e ^ ° -ggsg 2 S QJ w g w w U ΙΛ% fg «° o E ® * =" D ~ · = O (1 J- w ti C m * = ra o ra ra ■ B <t ϊ | »» «| · § S ffl ¾. 0 JS JS DE í ΐ JS JS DE DE DE »» »D» »» »» »» »» »» »» »» »» »» »" " “^ G 1« ΐ g -S ε ε I £ «Ε Ί π ΰ 2 2" g |, ϊ "ti 41 - 4- * + - * and 1 1121111ε% 11¾ ΐ, a ^« a 9 ra ^ oo ü S Q S - - - - - - - - - - - - - - EW pj. .E .ra _l «5§ ^.! ΕΕ“ S ra 15 -Ξ "ura ra, i JS -Ξ„ C 13 2 OO -S ü I p 1 f -I <<3 mw O w 4- j 4- + 4 * <Ç [0076] When the threads (72, 76) are fully engaged, the rotor (44) turns is rotatably fixed in the direction of travel to the distal end of the drive shaft (46), ie when the rotor is rotated in the direction of fluid acceleration by the drive shaft (46), the coupling of the threads (72, 76) tends to be tight and the full thread coupling (72, 76) is maintained. When the rotor (44) is rotated in the opposite (i.e. nonfunctional) direction, the threads (72, 76) will tend to decouple. Thus, to connect the drive shaft (46) to the rotor (44), the rotor (44) is immobilized and the drive shaft (46) is threaded in the tightening direction until the threads (72, 76) are engaged. Subsequent operation of the pump (10) will ensure that this coupling is maintained, and therefore the drive shaft (46) is selectively rotatably attached to the rotor (44). To disconnect the drive shaft (46) from the rotor (44), the rotor (44) is immobilized and the drive shaft (46) is rotated in the opposite direction to decouple the threads (72, 76).

As male threads (72) and female threads (76) approach the full coupling, as shown in Figure 2, the distal block (70) formed at the end of the drive shaft (46) encounters a hole formed (74). ) correspondingly on the rotor (44). Both the distal block (70) and hole (74) can be machined to a tight tolerance for the purpose of concentrically aligning the drive shaft (46) and rotor (44) with precise adjustment and tolerance. tight in the final assembly. In an exemplary embodiment, the total radial clearance between the distal block 70 and the hole 74 is less than 0.004 inches, for example between 0.001 inches and 0.003 inches. Advantageously, the interaction between the distal block (70) and the orifice (74) reduces or eliminates any non-concentricity between the drive shaft axis (AD) and the rotor rotation axis (44). In an exemplary embodiment, the threaded connection formed by the threads (72, 76) allows for a relatively large radial clearance of the shaft drive shaft (AD) relative to the rotor shaft of the rotor (44). That is, when the drive shaft (46) is connected by threads (72, 76) rather than the distal block (70) and the hole (74), the opposite end of the drive shaft (46) can move radially from one another. so that the drive shaft axis (AD) is angled with respect to the rotor axis of rotation (44).

In an exemplary embodiment, this radial clearance may be between 0.001 inches and 0.003 inches as defined in ANSI / ASME Bl.5-1997, the entire invention of which is expressly incorporated by reference herein. In contrast, when the distal block (70) and hole (74) are coupled, in addition to the threads (72, 76), such that the rotor (44) is tightened completely against the adjacent handle of the drive shaft (46). ), this radial clearance is eliminated and the drive shaft (AD) becomes substantially concentric with the rotor shaft (44).

Although the drive shaft (46) includes the male characteristics used to connect the drive shaft (46) to the rotor (44) (ie male threads (72) and the distal block (70), and the rotor (44) includes female characteristics (i.e. female threads (76) and bore (74), it is envisaged that this arrangement may be reversed as required or desired for a specific design. That is, one of the components may be provided). with male threads (72) and the other component may be provided with corresponding female threads (76). Similarly, one of the components may be provided with a male centering feature such as the distal block (70), and the other component can be supplied with the corresponding female characteristic, such as hole (74).

Drive Disassembly System [0080] Referring now to Figures 8 and 9, the drive disassembly system (50) used to disconnect and connect the drive mechanism (40) from the housing (12) and the remainder of the pump (10 ) is illustrated. As described below, drive disassembly system components (50) may be connected to the pump (10) to facilitate removal and / or installation of the drive mechanism (40), and may be disconnected from the pump (10) for normal operation.

The drive disassembly system (50) includes the guide rail (52) selectively received within the blind hole (66) (figure 1) formed in a central reinforcement (28). The reinforcement 28 extends in a two-sided direction from the vertical portion of the exit side wall 16 to the partition wall 24, and provides a structural support that inhibits bulging or deviation of the outlet side wall (16) under the high pressures developed within the pump outlet chamber (32). The strength and structural integrity provided by the reinforcement (28) and its associated structures also firmly support the guide rail (52) within the hole (66).

In an exemplary embodiment, the guide rail (52) is comfortably received in the hole (66). For example, the total radial clearance between guide rail 52 and hole 66 may be between 0.0015 inches and 0.0055 inches. When comfortably received, the guide rail 52 has minimal radial clearance and therefore firmly supports the drive mechanism 40 during mounting and dismounting procedures as described below.

In order to axially secure the guide rail (52) in its fully received position in the hole (66), the rail holder (56) can be used to engage the notch (54) formed in the guide rail (52) ( figure 9). The rail holder (56) can then be fixed to the housing (12) to axially secure the rail holder (56) and the guide rail (52) to the housing (12).

The guide rail (58) includes the bearing (60) sized to be slidably received along the guide rail (52), and the flange (62) is attached to the bearing (60) (by welding, for example). ).

When the drive disassembly system (50) is used to remove the drive mechanism (40) from the housing (12), the guide rail is first installed as described above. A portion of the standard mounting fasteners (43) holding the drive mechanism (40) in place (Figure 1) are removed, such as the four fasteners (43) closest to the guide rail (52). The bearing (60) is then slid over the previously installed guide rail (52) until the guide rail flange (62) abuts the housing (12) as shown in figure 8. Fasteners (65) are passed through the openings (64) (not shown) formed in the flange (62) to screw the guide rail (58) to the drive mechanism (40) where the standard fasteners (43) have been removed. In an exemplary embodiment, the openings (64) through the flange (62) are oversized relative to the fasteners (65), which allows the fasteners (65) to move slightly within the openings (64) such that the The alignment of the drive disassembly system (50) with respect to the housing (12) can be controlled by the interaction between the guide rail (52) and the bearing (60), rather than between the flange (62) and the housing (12). ).

The fasteners (65) used in connection with the drive disassembly system (50) are larger than the standard fasteners (43) used to secure the drive shaft housing (42) to the housing (12) (figure 1). In this way, the fasteners (43) may pass through the threaded openings (64) in the drive shaft housing flange (42) (i.e. without screw-coupled threaded openings (64), but the fasteners (65) connect to each other. by screwing into the openings 64. Thus, the drive mechanism (40) is fixed to the housing (12) by means of the fasteners (43), while the guide rail (58) is fixed to the housing (42) by fasteners larger threaded (65).

With the guide rail (58) affixed to the drive shaft housing (42) and slidably received over the guide rail (52), the drive mechanism (40) is ready to be removed from the external opening of the drive (22) formed on the outlet side wall (16) of the housing (12) as shown in Figure 9. Any remaining fasteners (43) securing the drive shaft housing (42) to the housing (12) are removed to loosen the drive mechanism (40) from the rest of the pump (10).

Referring to Figure 9, the drive mechanism (40) can then be freely removed from the housing (12) using the guide rail (52) to support the drive mechanism (40). Advantageously, the guide rail (52) accepts the weight of the drive mechanism (40), allowing the service person to concentrate on guiding the drive mechanism (40) safely out of the housing (12) without having to Also support the weight manually. In addition, the caster (68) may be affixed to a lower portion of the drive shaft housing (42), such as by the caster support (69), to cooperate with the guide rail (52) to provide support for the weight of the drive mechanism (40) during its removal or installation in the housing (12). In the illustrated embodiment, the standard fasteners (43) may be removed along the bottom of the housing (42) to expose the threaded openings (64) (not shown) so that the fasteners (65) may be threaded with the openings (64) for securing the support (69) to the housing (42) in a manner similar to the guide rail (58) described above.

For installation or reinstallation of the drive mechanism (40) via the drive disassembly system (50), the removal steps are simply repeated in reverse. During final alignment of the drive mechanism (40), after it has been received at the drive's external opening (22) and through the drive's internal opening (26) (figure 5), the fasteners (65) can be released as required. to allow any necessary readjustment.

Rotor Inspection [0090] Referring now to Figure 11, the inspection cover (110) and inspection side wear plate (112) are shown removed from their seated positions within the housing (12) to expose the opening of external inspection (124) leading to the pump inlet chamber (30) as well as the internal inspection opening (126) leading to the volute (34), fluid channel (36) and rotor (44) seated in the central bore of the volute (34).

In the exemplary embodiment, the inspection side wear plate 112 is secured to the inspection cover 110 with fasteners, for example. When secured in this manner, removal of the inspection cover (110) also removes the inspection side wear plate (112) as a single unit to allow access to the pump (30), volute (34) and impeller inlet chamber (44) for inspection, maintenance or repair.

When the inspection cover (110) and wear plate (112) are reinstalled in the housing (12) through the external inspection opening (124), the previous spacing and configuration between the wear plate wear surface (112) and the rolling surface next to the rotor (44) are maintained.

In order to establish and maintain such adequate spacing, the fastener (114) may be used to secure the inspection cover (110) and the inspection side wear plate (112) to the housing (12) via a cannulated screw. (118) and the screw fixing plate (120). Only one of these fastener arrangements is illustrated in Figure 11 for clarity, it being understood that the illustrated embodiment utilizes four such fastener arrangements for each of the fastener openings (116) formed in the inspection cap (110).

The fixing openings (116) are segmented to receive the corresponding threaded axis of the cannulated screw (118). The length of the threaded portion of the cannulated screw (118) is such that each screw (118) may protrude beyond the distal end of the opening (116) to rest against the adjacent face of the housing (12), which prevents the cap from inspection (110) of being fully seated in the housing (12) because the distal end of the screws (118) contacts the housing (12) before the cover (110). In this way, the spacing between the inspection side wear plate (112) and the rotor (44) can be controlled by adjusting the cannulated screws (118) to project more or less beyond the distal end of the fastener openings (116). ).

To rotate the cannulated screws (118) in a desired position corresponding to the appropriate axial spacing between the wear plate (112) and the rotor (44), the fixing plate (120) and the fastener ( 122). The clamping plate (120) includes a screw head receiving opening (121) which is generally polygonal in order to rotatably secure the cannulated screw (118) to the clamping plate (120 (when the hex head of the screw (118) received in opening 121. In the example, opening 121 is a "twelve point" style of the type generally used in wrenches and sockets and is designed to rotatably attach to hexagonal screw heads. placed over the head of the screw (118) so that the retainer fitting (123) aligns with the retaining aperture (117) formed on the inspection cover (110) .The retainer (122) is then passed through the fitting (123) ) and the threaded coupling with the opening (117) by rotatably and axially securing the bolt securing plate (120) to the inspection cover (110) and thereby securing the rotational orientation and axial adjustment of the cannulated bolt 118. The fastener 114 (described in detail above) is then it is passed through the center hole of the cannulated screw (118) and screwed into the adjacent threaded opening of the housing (12) to secure the inspection cover (110) thereto.

Although this invention has been described as having an exemplary design, the present invention may still be modified within the spirit and scope of this disclosure. This application, therefore, is intended to cover any variations, uses or adaptations of the invention using its general principles. Further, this application is intended to cover such deviations of the present invention within the scope of known or customary practice in the state of the art to which this invention relates, and which is within the limits of the appended claims.

Claims (41)

1. A self-priming centrifugal pump, comprising: a drive mechanism (40); a rotor (44) connected to the drive mechanism (40); a housing (12) with an inlet (30) and an outlet (20) comprising: an inlet side wall (14) with an inlet opening (18) formed therein; an exit side wall (16) joined to the entrance side wall (30) to form a cavity in the housing (12), wherein the exit side wall (16) has an exit opening (20); a volute (34) positioned in the housing (12) and in fluid communication with. the inlet (18) and outlet (20) openings, the volute (34) having a central opening sized to receive the rotor (44) and a spiral-shaped fluid channel (36) such that the channel of fluid advances radially outward toward a discharge opening (38) of the volute (34), and the discharge opening (38) of the open volute (34) defines a longitudinal discharge (AV) axis extending through the outlet port (20) whereby the volute (34) is adapted to receive outward accelerated fluid by the rotor (44), directing the fluid radially outward through the spiral-shaped fluid channel (36) and discharging the fluid along the longitudinal discharge (AV) axis at. towards the outlet opening (20). SELF-BREAKING PUMP according to claim 1, characterized in that the casing (12) defines a vertical central plane containing a rotor axis of rotation (44) and the longitudinal discharge axis (AV) is oriented to cross the vertical central plane. SELF-SPINNING CENTRIFUGE PUMP according to claim 1, characterized in that the rotor (44) defines a plane of rotation perpendicular to the rotor axis of the rotor (44), the discharge axis (AV) being angled at relation to the plane of rotation. SELF-BREAKING CENTRIFUGE PUMP according to claim 3, characterized in that the housing (12) further includes a partition wall (24) interposed between the inlet side wall (1.4) and the outlet side wall (16) for form an inlet chamber (30) of the pump (10) and an outlet chamber (32) of the pump (10), wherein the partition wall (24) has an internal drive opening (26) positioned to allow fluid communication between the inlet chamber (30) of the pump (10) and the outlet chamber (32) of the pump (10) through the internal drive opening (26). SELF-BREAKING CENTRIFUGAL PUMP according to Claim 4, characterized in that the discharge shaft (AV) is positioned at an angle away from the partition wall (24). SELF-BREAKING CENTRIFUGE PUMP according to Claim 4, characterized in that the housing (12) further includes a plurality of retaining projections (104) positioned in the outlet chamber (32) of the pump (10) and adjacent to the outlet opening. (20), the fixing projections (104) having a smooth rounded outer surface. SELF-BREAKING CENTRIFUGAL PUMP according to claim 6, characterized in that each of the fixing projections (104) has a convex distal surface and a concave surface at the junction between the convex distal surface and the adjacent inner surface of the outlet chamber ( 32) of the pump (10). SELF-SPINNING CENTRIFUGE PUMP according to claim 6, characterized in that the locking projections (104) define a tip-end drop shape in the direction of the outlet opening (20), with the fixing projections (104) promote the laminar flow of fluid discharged from the volute (34) and moved toward the outlet opening (20). SELF-BREAKING CENTRIFUGE PUMP according to claim 4, characterized in that the pump housing (12) (10) includes a reservoir region (138) formed in the lower region of the outlet chamber (32) of the pump (10); wherein the reservoir region (138) includes a central portion in direct fluid communication with the rotor (44) and a peripheral portion in indirect fluid communication with the rotor (44), the housing (12) further includes at least one drainage channel (132, 136) in direct fluid communication with the peripheral portion of the reservoir region (138) and in indirect fluid communication with the central part of the reservoir region (138), wherein at least one drainage channel (132, 136) forms no part of the volute (34). A self-priming centrifugal pump according to claim 9, characterized in that the housing (12) includes a first drainage channel (132) and a second drainage channel (136), the first and second channels (132, 136) being provided. opposite the volute (34). Self-priming centrifugal pump according to claim 1, characterized in that the pump (10) further includes an inlet adapter (90) connected to the inlet port (18), wherein the inlet adapter (90) includes a tapered part (91) where a flow area through the inlet adapter (90) gradually increases along a flow direction to the inlet port (18). A self-priming centrifugal pump according to claim 11, characterized in that the pump (10) further includes an outlet adapter (98) connected to the outlet opening (20), wherein the outlet adapter (98) has a passageway. of substantially cylindrical fluid, and the inlet (90) and outlet (98) adapters are configured to receive a common nominal fluid conduit size and the tapered part (91) of the inlet adapter leads to the inlet port (18). which has an area larger than the outlet opening (20). A self-priming centrifugal pump according to claim 1, characterized in that the outlet opening (20) includes an outlet transition area (102) with an inner radius of operable radius to facilitate stable flow, the flow being exit transition area (102) defines a nominal radius of at least equal to the minimum exit side wall thickness (16). SELF-BREAKING CENTRIFUGAL PUMP according to claim 13, characterized in that the nominal radius of the exit transition area (102) is at least 131% of the minimum wall thickness of the exit side (16). A self-priming centrifugal pump according to claim 1, further comprising a plurality of reinforcements (100) extending along and integrally formed with the inlet side wall (14) and the outlet side wall (16 ) of the housing (12), with the ribs (100) being positioned only on an outer surface of the housing (12). A self-priming centrifugal pump according to claim 15, characterized in that a plurality of reinforcements (100) in the outlet side wall (16) extend along a substantially vertical surface of the outlet side wall (16); around a corner at the junction between the vertical face of one side face of the exit side wall (16), and extend in a backward-forward direction on the side face. A self-priming centrifugal pump according to claim 16, characterized in that the plurality of reinforcements (100) extend radially outwardly along the vertical face from a central area of the vertical face. Self-priming centrifugal pump according to Claim 1, characterized in that the outlet side wall (16) of the housing (12) includes an external drive opening (22) sized to receive the drive mechanism (40). 19. A self-priming centrifugal pump comprising: a drive mechanism (40); a rotor (44) connected to the drive mechanism (40); a membrane valve (80); a housing (12) containing an inlet (30) and an outlet (32), wherein the housing (12) includes: an inlet side wall (14) with an inlet opening (18) formed therein; membrane valve (80) positioned at the inlet port (18) to allow fluid to flow into the housing (12) via the inlet port (18) while preventing fluid flow out of the housing (12) via the port inlet (18); an exit side wall (16) joined to the entrance side wall (14) to form a cavity in the housing (12), wherein the exit side wall (16) has an exit opening (20); a partition wall (24) interposed between the inlet side wall (14) and the outlet side wall (16) to form an inlet chamber (30) of the pump (10) and an outlet chamber (32) of the pump (10), wherein the partition wall (24) has an internal drive opening (26) positioned to allow fluid communication between the pump inlet (30) chamber (10) and the pump outlet (32) chamber pump (10) via an internal drive opening (26); a combination port (82) formed in the housing (12) next to the membrane valve (80), the combination port (82) being sized and positioned to allow access to the membrane valve (80) by a maintenance, and allow fluid to be added to the inlet chamber (30) of the pump (10); and a filler opening (96) formed through the housing (12) on the opposite side of the dividing wall (24) of the combination door (82), so that the filler opening (96) permits fluid communication between the control chamber. pump outlet (32) and the environment, in which liquid added to the pump inlet (30) (10) is allowed to flow into the pump (10) outlet (32) via the internal opening while air contained in the outlet chamber (32) of the pump (10) is vented to the atmosphere via the filler opening (96). A self-priming centrifugal pump according to claim 19, characterized in that it further includes a combination door cover (96) comprising: a portion of the filler door cover (96) sized to be received over the door. (82) to fluidly isolate the combination port (82) from the environment; and a lid portion (96) of the filler opening (92) sized to be received over the opening to fluidly isolate the ventilation from the environment. A self-priming centrifugal pump according to claim 20, characterized in that the lid portion (96) of the filler opening (92) is formed as a front extension of the filler door lid portion (96) for the passage over the partition wall (24) in the opening. A self-priming centrifugal pump according to claim 20, characterized in that the filler cap portion (96) and the aperture cap portion (92) are integrally and monolithically formed as a single component. A self-priming centrifugal pump according to claim 19, characterized in that the outlet side wall (16) of the housing (12) includes an external drive opening (22) formed therein, with the external drive opening ( 22) is sized to receive the drive mechanism (40). 24. A self-priming centrifugal pump comprising: a drive shaft (46) with the first coarse thread (76) and a first centering feature; a rotor (44) connected to the drive shaft (46), with the rotor (44) having a second coarse thread (72) and a second centering feature, the second coarse thread (72) connectable with the first thread (76) ) thick drive shaft for rotatably and selectively securing drive shaft (46) to rotor (44), and second centering feature connectable with first centering feature to concentrically align rotor (44) with shaft drive (46). Self-priming centrifugal pump according to Claim (24), characterized in that the first coarse thread (76) of the rotor (44) is a female thread and the second coarse thread (72) of the drive shaft (46) is. a male thread. Self-priming centrifugal pump according to claim (24), characterized in that the first and second coarse threads (76 and 72) are trapezoidal threads. A self-priming centrifugal pump according to claim (24), characterized in that the first centering feature is a hole (74) formed in the rotor (44) and the second centering feature is a distal end block (70). drive shaft (46). A self-priming centrifugal pump according to claim 27, characterized in that the block (70) and the orifice (74) fit together with a radial clearance of less than 0.004 inches. A self-priming centrifugal pump according to claim (24), characterized in that the drive shaft (46) is part of a drive mechanism (40), comprising: a housing (12) with an inlet (30) and an outlet (32) including: an inlet side wall (14) with an inlet aperture (18) formed therein; an exit side wall (16) joined to the entrance side wall (14) to form a cavity in the housing (12), wherein the exit side wall (16) contains an exit opening (20); a drive shaft housing (42) attached to the housing (12), the drive shaft (46) rotatably received in the drive shaft housing (42); at least one bearing (47) supported by the drive shaft housing (42) and rotatably supporting the drive shaft (46); a drive side wear plate (112) connected to the drive shaft (46); and a biasing element between the drive side wear plate (112) and the rotor (44) that biases the drive side wear plate (112) toward the drive shaft housing (42) and moves away from the rotor (44). A self-priming centrifugal pump according to claim 29, characterized in that the first drive shaft centering feature (46) includes a distal end location block (70); the second rotor centering feature (44) includes a locating hole (74) sized to receive the locating block (70); the drive shaft (46) is operatively connected to the rotor (44) by connecting the first thread (76) with the second thread (72), thereby allowing radial movement on the drive shaft (46), and the drive shaft ( 46) being concentrically located relative to the rotor (44) by a close tolerance interaction between the locating block (70) and the locating hole (74) such that radial movement is eliminated. A self-priming centrifugal pump according to claim 30, characterized in that the radial movement is less than 0.004 inches. A self-priming centrifugal pump according to claim 29, characterized in that the outlet side wall (16) includes an external drive opening (22) formed therein and the external drive opening (22) is sized to receive the rotor (44), the housing (12) further including: a partition wall (24) interposed between the inlet side wall (14) and the outlet side wall (16) to form an inlet chamber ( 30) of the pump (10) and an outlet chamber (32) of the pump (10), the partition wall (24) has an internal drive opening (26) positioned to allow fluid communication between the inlet chamber (30) (10) and the outlet chamber (32) of the pump (10) via the internal drive opening (26). 33. A self-priming centrifugal pump comprising: a drive mechanism (40); a rotor (44) connected to the drive mechanism (40); a housing (12) containing an inlet (30) and an outlet (32), including: an inlet side wall (14) with an inlet opening (18) formed therein; an exit side wall (16) joined to the entrance side wall (14) to form a cavity in the housing (12), wherein the exit side wall (16) contains an exit opening (20); an orifice extending internally from the exterior of the outlet side wall (16), wherein the orifice is accessible to a pump user (10); a drive disassembly system (50) including: a guide rail (52) sized to be received in hole (66); and a guide rail (58) with a bearing (60) and a flange (62) attached to the bearing (60), the bearing (60) being sized to be slidably received on the guide rail (52), while the The flange (62) is fixed to the drive mechanism (40) so that the drive mechanism (40) can be mounted on or removed from the housing (12) while being supported by the guide rail (58). A self-priming centrifugal pump according to claim 33, characterized in that the housing (12) further comprises: a partition wall (24) interposed between the inlet side wall (14) and the outlet side wall (16) to form an inlet chamber (30) of the pump (10) and an outlet chamber (32) of the pump (10), wherein the partition wall (24) has an internal drive opening (26) positioned to allow communication fluid between the inlet chamber (30) of the pump (10) and the outlet chamber (32) of the pump (10) via the internal drive opening (26); and a stiffener (28) extending through the outlet chamber (32) of the pump (10) from the outlet side wall (16) to the partition wall (24), the stiffener (28) containing a hole (66) formed therein as one. blind hole. A self-priming centrifugal pump according to claim 33, characterized in that the drive mechanism (40) includes a housing fixed to the housing (12) by means of a series of first fasteners (43) passing through a corresponding series. of annularly disposed openings (64) in the housing (12), the first fasteners (43) being received via thread in the housing (12); and the guide rail flange is secured to the housing (12) by a series of second fasteners (65) received via thread through a series of annularly arranged openings (64) in the flange (62), the series of openings ( 64) arranged annularly formed on the flange (62) of the guide rail (58) are oversized relative to the size of the second fastener series (65), with the alignment of the drive disassembly system (50) relative to the housing (12) It is a function of interaction between the guide rail (58) and the bearing (60), rather than between the flange (62) and the housing (12). A self-priming centrifugal pump according to claim 33, characterized in that an outer surface of the guide rail (56) includes a socket (54) positioned adjacent the exterior of the outlet side wall (16) when the guide rail (16) 52) is fully received in hole (66), the drive disassembly system (50) includes a rail bracket (56) molded to connect the socket and be secured to the housing (12) so that the rail bracket (56) and the housing (12) cooperate to axially secure the guide rail (52) relative to the housing (12). A self-priming centrifugal pump according to claim 36, characterized in that the drive disassembly system (50) includes a caster (68) selectively attached to the drive mechanism (50), with the caster (68) positioned to cooperate with the guide rail (52) to support the drive mechanism (40) while the drive mechanism (40) is mounted on or removed from the housing (12). Disassembly method of a centrifugal pump drive mechanism, characterized by including: inserting a rail (52) into a hole (66) formed in a housing (12) of the pump (10) such that the rail (52) fits into the hole (66); the slip of one. guide rail (58) over the rail (52) and into. connection to the pump (10); securing the guide rail (58) to the drive mechanism (40) while holding the guide rail (58) by sliding into the connection with the rail (52); and disconnecting the drive mechanism (40) from the housing (12) and sliding the drive mechanism (40) out of the housing (12) using the rail support (52). DISASSEMBLY METHOD according to claim 38, characterized in that it includes the attachment of a caster (68) to the underside of the drive mechanism (40), wherein the disconnection step includes the rolling of the caster (68) on top of it. a support surface (69). DISASSEMBLY METHOD according to claim 38, characterized in that it includes reconnecting the drive mechanism (40) to the housing (12) using the rail support (52). DISASSEMBLY METHOD according to claim 38, further including, after the step of inserting the rail (52) into the hole (66), the connection of a rail support (52) to the housing (12); wherein the bracket connects a notch (54) formed in the rail (52) to axially secure the rail (52) relative to the housing (12).