Self-priming positive displacement constant flow high capacity pump

Abstract

A rotary action, self-priming positive displacement constant flow high capacity fluid pump is described. None of the pump parts touch in the pump chamber to minimize pump wear allowing for extended pump life. Since there are no touching parts in the pump chamber, the pump can be operated dry without the pump liquid being present without damage to the pump. The pump may be operated either clockwise or counter-clockwise without loss of positive displacement or reduction in fluids input or output. Due to the design of the pump, the pump is inherently low-maintenance and is highly resistant to clogging by debris and the like. Fluid pressure relief sections are provided by carving out of the inside portions of the housing structure to which the ends of the shaft are mounted to vary or improved pump performance.

Claims

1. An improved rotary, self-priming, constant flow, high capacity, positive displacement pump for pumping fluids, comprising: a pump housing having a fluid inlet and a fluid outlet; a first rotary impeller operably disposed in the pump housing, comprising a shaft including shaft ends rotatably mounted in the pump housing, the shaft including a plurality of vanes having contoured faces extending outwardly therefrom; a second rotary impeller operably disposed in the pump housing, comprising a shaft including shaft ends rotatably mounted in the pump housing, the shaft including a plurality of vanes having contoured faces extending outwardly therefrom; a pair of gears each secured to at least one of the ends of the shafts of the first and second rotary impellers, wherein the gears mesh with each other and synchronize rotation of the first and second rotary impellers to ensure that the vanes do not contact one another during rotation; and a first side pressure release chamber disposed inside the pump chamber in the pump housing, the first side pressure release chamber operationally disposed at the sides of the vanes of the first impeller, wherein each vane has an end, and a flexible seal is secured to the end of each vane.

2. An improved rotary, self-priming, constant flow, high capacity, positive displacement pump for pumping fluids, comprising: a pump housing having a fluid inlet and a fluid outlet; a first rotary impeller operably disposed in the pump housing, comprising a shaft including shaft ends rotatably mounted in the pump housing, the shaft including a plurality of vanes having contoured faces extending outwardly therefrom; a second rotary impeller operably disposed in the pump housing, comprising a shaft including shaft ends rotatably mounted in the pump housing the shaft including a plurality of vanes having contoured faces extending outwardly therefrom; a pair of gears each secured to at least one of the ends of the shafts of the first and second rotary impellers, wherein the gears mesh with each other and synchronize rotation of the first and second rotary impellers to ensure the vanes do not contact one another during rotation; and a first side pressure release chamber disposed inside the pump chamber in the pump housing, the first side pressure release chamber operationally disposed at the sides of the vanes of the first impeller, wherein each vane has a complementary cut-out slot for clearance during rotation of the impellers during synchronous intermeshing of the vanes.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1A is a drawing of the stationary portion of the rotary pump housing showing the top view thereof.

(2) FIG. 1B is a drawing of the stationary portion of the rotary pump housing showing the front view taken along Plane B-B of FIG. 1A and the back view thereof.

(3) FIG. 1C is a drawing of the stationary portion of the rotary pump housing showing the side view thereof taken along Plane A-A of FIG. 1A.

(4) FIG. 2 is a diagrammatic view of the present invention showing both the exterior pump housing and the interior pump chamber, along with the input/output ports, the inlet/outlet pressure release chambers, the side pressure release chambers, the center compression release channels, and side compression release channels.

(5) FIG. 3 is a view of the two (2) impellers or vanes of the present invention shown intermeshing one with the other.

(6) FIG. 4 illustrates the use of a Neoprene tip mounted on the extremity of the impellers or vanes to increase the efficiency of the pump by effectuating a seal between the stationary pump housing and the impellers or vanes.

(7) FIG. 5 is a top view of the bottom plate with relief cavities of the stationary pump housing.

(8) FIG. 6 is a top view of the three separator plates, in an alternative embodiment of the present invention showing the special fluid seals about the two pump shafts and disposed inbetween the gear housing and the rotary pump housing taken along Plane C-C of FIG. 7.

(9) FIG. 7 is a side elevational view of the combination shown and illustrated in FIG. 6

(10) FIG. 8 is a side elevational view of the first impeller.

(11) FIG. 9 is an end view of the first impeller taken along Plane D-D of FIG. 8 of the Drawings herein.

(12) FIG. 10 shows an internal fluid pump implementation of the present invention utilizing a pair of dual impellers with contoured blades.

(13) FIG. 11 illustrates an internal fluid pump implementation of the instant invention disclosed herein utilizing a pair of dual impellers with flat blades.

(14) FIG. 12 depicts an internal fluid pump implementation of the invention described herein utilizing a pair of three impellers each having contoured blades.

(15) FIG. 13 describes an internal fluid pump of the inventive character disclosed herein incorporating the use of a pair of three impellers each with flat blades.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT OF THE INVENTION

(16) With continuing reference to all of the Drawings herein, and with primary reference to FIG. 2 FIG. 3 and FIG. 7, there is basically shown and described a new and useful positive displacement, self-priming, reduced speed, high volume fluid pump, comprising a pump housing 11 having an interior pump chamber 17 with at least one open entrance 16 thereinto, a pair of fluid inlet/outlet ports 12 and 13 in the pump housing 11 in fluid communication with the interior pump chamber 17, a pair of impellers 8, 9 each having a shaft 32, 35 for rotatably mounting each impeller 8, 9 and each impeller 8, 9 respectively having a plurality of vanes 27, 41 and 28, 42 extending respectively from each shaft 32, 35, and adapted for operative synchronistic rotatable non-contacting disposition between the plurality of vanes 27, 41 and 28, 42 within the pump chamber 17, at least one element adapted to be mounted to the pump housing 11 about the open entrance into the pump housing 11 and having means thereon for rotatably mounting the ends of the of the shafts 32, 35 therein, and on one side of the vanes 27, 41 and 28, 42 are a pair of side pressure release chambers 20A, 20B, a pair of center compression release channels 21A, 21B, a complementary pair of center pressure release chambers 19A, 19B, a plurality of side compression release channels 22A, 22B, 22C and 22D, and disposed in the pump chamber 17 on the other side of vanes 27, 41 and 28, 42 as shown in FIG. 5 are fluid pressure relief sections 26 A, 26 B, 26 C and 26 D.

(17) The primary differences between the present invention and the prior art invention of which Nachtrieb is believed to be the closest prior art reference is not only the use of re-designed, more efficient newer vane structures than those used in the prior art pump design disclosed and described by Nachtrieb where the rotary pump vanes of the impellers are flat-faced, are rectangular in shape and have a flat front face and corresponding flat backside, but primarily in the incorporation of a complementary pair of side pressure release chambers 20A, 20B, complementary center compression release channels 21A, 21B in fluid communication respectively with a corresponding complementary pair of center pressure release chambers 19 A, 19 B and a plurality of side compression release channels 22A, 22B, 22C and 22D which chambers 19A, 19B are fluidly interconnected with the side pressure release chambers 20 A, 20 B, and, on the other side of the vanes 27, 41 and 28, 42 are disposed in the pump chamber 17 as shown in FIG. 5 fluid pressure relief sections 26 A, 26 B, 26 C and 26 D.

(18) In the present invention, however, not only can flat faced vanes be used, such as depicted in FIGS. 2, 5, 8, 9, 11 and 13, but vanes can be employed which are not flat-faced, but are contoured instead, such as shown in FIGS. 3, 10 and 12 whereby they do not have flat surfaces on the front or backside portions of the vanes of the impellers of the rotary pump.

(19) Along with the important and significant modification of the impeller vanes 27, 28, fluid pressure relief sections 26 A, 26 B, 26 C and 26 D are incorporated in under the pump housing 11 structure near the ends of the shaft of the rotating pump impellers. These fluid pressure relief sections 26 A, 26 B, 26 C and 26 D which are carved out of the inside portion of the stationary pump housing 11 can be adjusted in size and volume to vary or improve pump performance at various rotational speeds to adjust the operation of the pump to pump fluids having varying amounts of particulate matter in the fluid.

(20) Fundamentally, there is described and disclosed herein a new and improved rotary action, self-priming, positive displacement, constant flow high capacity fluid pump generally indicated at 10 in the various figures showing in diagrammatic form in FIGS. 1A, 1B, and 1C. The rotary pump casing or housing is indicated generally at 11 In FIGS. 1A, 1B, and 1C. FIG. 1A is a top view of the rotary pump casing 11, FIG. 1B is a back or rear view of the rotary pump casing 11, and FIG. 1C is a side elevational view of the rotary pump housing 11.

(21) As noted in these figures, as part of the pump housing 11, there is a first inlet/outlet 12 and a second inlet/outlet 13.

(22) It should be clearly understood that the first inlet/outlet 12 and a second inlet/outlet 13 are designated as an inlet/outlet because each of these outlets, the first outlet 12 and the second outlet 13, can be used as either a fluid inlet or fluid outlet in the following manner. If the first inlet/outlet 12 is used as an inlet, then the second inlet/outlet 13 will be used as an outlet. If the second inlet/outlet is used as an inlet 13, then the first inlet/outlet 12 will be used as an outlet.

(23) As noted and shown in FIGS. 1A, 1B, and 1C, mounting lugs 14A, 14B, 14C and 14D secured to the rotary pump housing 11 to any suitable mounting surface (not shown) to stabilize the entire pump housing 11 during operation of the rotary pump 10. Attachment of the mounting lugs 14A, 14B, 14C and 14D to the mounting surface is accomplished by screws, bolts or other suitable fasteners via the holes 15A, 15B, 15C and 15D in the corresponding lugs 14A, 14B, 14C and 14D.

(24) With special reference now to FIG. 2, there is shown and illustrated the interior portion of the pump housing 11. As noted and shown, there is an open entrance 16 to the pump housing 11, with an [interior] pump chamber 17, inlet/outlet ports 12, 13, the inlet/outlet pressure release chambers 19A, 19B, the side pressure release chambers 20A, 20B, the center compression release channels 21A, 21B, and the side compression release channels 22A, 22B, 22C, and 22D.

(25) The above combination of pressure release chambers 19 A, 19 B, 20 A, and 20 B, the compression release channels 21 A, 21 B, 22 A, 22 B, 22 C and 22 D all combine to create a greater efficiency due to a reduced loss of volume as head pressure increases. Additionally, this configuration and combination creates a self-priming capability not available in high volume pumps of a different pump design.

(26) This design configuration of the pump chamber 17 eliminates compression of fluids while allowing rapid flow of the fluids through the pump 10 while, at the same time, operating in either direction without loss of positive displacement or reduction in the fluids' input or output. In short, this pump 10 can be operated in either direction; that is, the inlet/outlet ports 12, 13 can be switched to operate as either an inlet port or an outlet port. For example, if port 12 is fluidly connected as an inlet port, then port 13 will be the fluid outlet port, and visa versa.

(27) Turning now to FIG. 5 and FIG. 6, there is shown, in generally diagrammatic form, the gear and impeller separator plate assembly and fluid closure plate assembly 33 removably secured about opening 16 in pump housing 11, and a plurality of fluid pressure relief cavities 26A, 26B, 26C and 26D.

(28) With respect to the illustrations in FIGS. 6 and 7, there is shown, from a top view, the two impellers 27 and 28, driven by a driving shaft 29, through intermeshing gears 30, 31 connected to the shafts 32, 35 on which the impellers 27, 28 are rotatably mounted wherein the gears 30, 31 mesh with each other and synchronize rotation of the first and second rotary impellers 8, 9 (FIG. 2) to ensure that the vanes 27, 41 and 28, 42 do not contact one another during rotation. A gear and impeller separator plate generally indicated at 33, is formed of three (3) separate plates, 33A, 33B, and 33C which secured to the pump housing 11 completes enclosure of open entrance 16 of the fluid chamber 17 inside the pump housing 11.

(29) As shown in FIGS. 6 and 7, fluid seals 34A and 34B are provided for sealing between the plates 33A, 33B and 33C and about the shafts 32, 34.

(30) The impellers 42, 43 are shown each with four (4) vanes 36A and 36B. Shafts 37, 38 are provided for mounting the impellers 43, 42 respectively on the shafts 37, 38.

(31) With specific emphasis now on FIG. 3, there is shown and illustrated the preferred impellers generally indicated at 42 and 43. Cut-out slots 39 are provided in each of the extremities of the vanes 36A, 36B for clearance between the intermeshing extremities of the vanes between each of the tips of the vanes 36A, 36B as the impellers 43, 44 intermeshing rotate in synchronism with the vanes 36 A,

(32) As noted and illustrated in FIG. 4, there is shown a Neoprene tip seal 40 for the purpose of enhancing the dynamic fluid sealing function between the extremity of the tip of the impeller blade 36 and the fluid chamber 17 of the pump housing 11.

(33) It should be clearly understood and noted that the number of blades on the impellers can be increased for improved performance. The performance characteristics are improved over the current design shown and illustrated in these drawings based upon sealing produced by the involute design of the impeller hub and the outer extremities of impeller blades.

(34) It should be noted from the beginning that none of the pump parts touch in the pump chamber. The primary purpose of this non-contacting feature is to minimize pump wear, allowing for extended pump life, and boosting the self-priming feature of this unique fluid pump.

(35) Also, since there are no parts which touch each other in the pump chamber, the pump can be operated dry without the pump liquid being present and without incurring any damage to the pump.

(36) Additionally, the pump may be operated either clockwise or counter-clockwise without loss of positive displacement or reduction in fluids input or output. Due to the design of the pump, the pump is inherently low-maintenance and is highly resistant to clogging by debris and the like.

(37) The fluid pressure relief sections are provided by carving out of the inside portions of the housing structure to which the ends of the shaft are mounted to vary or improve pump performance.

(38) In FIG. 10, there is illustrated a pair of dual-vaned impellers generally indicated at 75 and 76 each of which is adapted for operable rotatable disposition inside the housing of a fluid pump of the type and character described previously, each impeller 75 and 76 respectively having, a pair of contoured vanes 49, 50 and 47, 48. Impeller 75 is mounted on a rotatable shaft 45 and impeller 76 is mounted on a rotatable shaft 46.

(39) FIG. 11 depicts a pair of dual-vaned impellers generally shown at 77 and 78 each of which is adapted for operable rotatable disposition inside the housing of a fluid pump of the character and type described previously herein, each impeller 77 and 78 having a pair of flat-faced vanes 53, 54 and 55, 56. Impeller 77 is mounted to a rotatable shaft 52 and impeller 78 is mounted to a rotatable shaft 51.

(40) Turning now to FIG. 12, there is additionally shown and illustrated a pair of triple-vaned impellers 79 and 80 each of which is adapted for operable rotatable disposition inside the housing of a fluid pump of the nature and character described hereinbefore. Each impeller 79 and 80 respectively having three contoured vanes 62, 63, 64 and vanes 59, 60, 61. Impeller 79 is mounted to a rotatable shaft 58 and impeller 80 is mounted to a rotatable shaft 57.

(41) There is illustrated and shown in FIG. 13 a pair of triple-vaned impellers generally indicated at 81 and 82 each of which is operatively adapted for rotatable disposition inside the housing of a fluid pump of the character and type described previously herein, each impeller 81 and 82 respectively having flat-faced triple-vanes. mounted to a rotatable shaft. Impeller 81 is mounted to rotatable shaft 65 and impeller 82 is mounted to rotatable shaft 66.

(42) The utilization of flat-faced vanes for an impeller provides for pumping a greater amount of fluid per rotation due to their greater volumetric efficiency over an impeller with contoured faced vanes.

(43) Contoured faced vanes provide a fluid pressure gradient to exist across the face of a vane with a contour which is especially useful in pumping fluids of different viscosities. With the contoured vanes shown in FIGS. 3, 10 and 12 illustrated as having bulbous outer extremities, the weight of such contoured vanes provides for smoother impeller rotation due to rotational momentum developed due to the extra weight at the outer extremity of each such vane.

(44) Although the present invention has been described in accordance with the embodiments shown, one of ordinary skill in the art will recognized that there could be variations to the embodiment and those variations would be within the spirit and scope of the present invention. Therefore, although the present invention was described in terms of a particular manner and verification system, one of ordinary skill in the art would readily recognize, that any number of parameters can be utilized and their use would be within the spirit and scope of the present invention. Accordingly, many modifications may be made by one of ordinary skill without departing from the spirit and scope of the present invention, the scope of which is defined and limited only by the following claims.