Turbulence element, system and fluid conveying device for protecting a sealing assembly

Abstract

A turbulence element (212) for an annular sealing cavity (252) in a fluid conveying device, the turbulence element (212) comprising: an inner surface (510) having an at least partially concave arcuate profile arranged to cooperate with a seal assembly (206) in the annular seal cavity (252) to define an inner channel (514) between the inner surface (510) and the seal assembly (206). an outer surface (518) having an arcuate profile arranged to cooperate with a housing (232) to define a flow path providing outer channel (550) in the annular sealing cavity (252) between the outer surface (518) and the housing (232); a front surface (520) extending between the inner surface (510) and the outer surface (518); and a rear surface (526) spaced from the front surface (520) and extending between the inner surface (510) and the outer surface (518), wherein the inner surface (510) with the at least partially concave arcuate profile of the turbulence element (212) forms a corresponding arcuate profile in the inner channel (514), and wherein the inner channel (514) and the outer channel (530) disrupt fluid flow within the annular seal cavity (252) to inhibit the formation of an air pocket adjacent to the seal assembly (206).

Description

[0001] Embodiments of the subject matter disclosed herein relate to fluid conveying devices. Other embodiments relate to turbulence elements and seal protection systems for fluid conveying devices.

[0002] Fluid handling devices, such as centrifugal pumps, can be used in a variety of applications to move fluid through a system. A centrifugal pump includes a rotating impeller that receives fluid flowing along its rotational axis and accelerates or propels the fluid radially outward through an outlet. In certain centrifugal pumps, a mechanical seal is used where the rotating shaft carrying the impeller passes through a stationary casing. In some examples, the mechanical seal may be disposed within a seal cavity defined by the impeller, a portion of the stationary casing, and a feedthrough plate.

[0003] During normal operation, a portion of the fluid moved by the centrifugal pump flows into the seal cavity and comes into contact with the mechanical seal. Such fluid can provide lubrication and cooling for the mechanical seal. However, in some cases, the centrifugal forces generated by the impeller in the seal cavity can pull fluid away from the mechanical seal, and one or more air pockets can form adjacent to the mechanical seal. The formation of such air pockets can locally increase friction and temperatures in the mechanical seal components, causing increased wear on these components and, consequently, a reduction in seal life. This increased heat can also affect other regions of the pump, for example, causing permanent compression set of elastomeric O-rings, leading to leakage and failure in adjacent areas.

[0004] US 3 076 412 A relates to a method and apparatus for eliminating the high failure rate of sealing structures in pumps used in systems for pumping liquids at high temperatures.

[0005] US 4 812 108 A relates to a magnetic pump comprising a front housing, a rear housing provided behind the front housing with a partition wall arranged therebetween, a rotating shaft extending from the front housing into the rear housing and supported by a bearing device provided in the partition wall, an impeller fixed to the rotating shaft within the front housing, a driven magnet drivingly connected to the rotating shaft within the rear housing, and a driving magnet provided outside the rear housing and rotatable by a motor, the magnetic pump being characterized in that the bearing device is formed at an intermediate portion thereof with lubricant supply channels, the partition wall has bores facing the rear plate of the impeller to guide the fluid within the front housing into the rear housing,wherein the rear housing has a supply bore for conducting a lubricant from the outside into the rear housing, wherein guide vanes for conducting the fluid from the rear housing into the channels of the bearing device are provided on at least one of the surface of the partition wall and the surface of the rear housing, which define the interior of the rear housing.

[0006] US 2007 / 0 217 907 A1 relates to systems and methods for improving seal performance in a centrifugal water pump for an internal combustion engine, increasing the static pressure at the seal by incorporating a combination of slots and ribs into a seal cavity of the pump housing, arranged to convert dynamic fluid pressure into static pressure at the seal while simultaneously reducing the coolant velocity at the seal. Appropriately sized and positioned vent holes in the impeller can also be used to increase the static pressure at the seal and improve seal performance.

[0007] In one embodiment, a turbulence element for an annular seal cavity in a fluid handling device is provided. The turbulence element has an inner surface arranged to cooperate with a seal assembly within the annular seal cavity to define an inner channel between the inner surface and the seal assembly. The turbulence element has an outer surface arranged to cooperate with a housing to define an outer channel within the annular seal cavity. The turbulence element also has a front surface extending between the inner surface and the outer surface and a rear surface spaced from the front surface and extending between the inner surface and the outer surface.

[0008] In one embodiment, the turbulence element disrupts fluid flow within the annular seal cavity to inhibit the formation of an air pocket adjacent the seal assembly. The turbulence element may be removably connected to a grommet, allowing for convenient removal and / or adjustment of the position of the turbulence element. In some examples, the inner channel of the turbulence element may have a variable inner channel depth, and the outer channel of the turbulence element may have a variable outer channel depth. In this way, an improved flow disturbance effect may be created. In other examples, two or more turbulence elements may be provided within the annular seal cavity. Advantageously, the provision of two or more turbulence elements may enable desired flow disturbance characteristics for a particular seal assembly.

[0009] Note that the above brief description is intended as a simplified introduction to a selection of concepts further described in the detailed description. It is not intended to identify the important or essential features of the claimed subject matter, the scope of which is defined solely by the claims that follow the detailed description. Furthermore, the claimed subject matter is not limited to implementations that solve any of the disadvantages identified above or in any part of the disclosure.

[0010] The present invention will be better understood from reading the following description of non-limiting embodiments with reference to the accompanying drawings, in which: Fig. 1 is a schematic diagram of an embodiment of a rail vehicle with a fluid conveying device and a seal protection system and an associated turbulence element according to an embodiment of the invention. Fig. 2 is a cutaway, approximately to scale view of an embodiment of a centrifugal pump having a seal protection system and an associated turbulence element according to an embodiment of the invention. Fig. 3 a perspective, approximately to scale view of a section of the centrifugal pump of Fig. 2, which shows an embodiment of the turbulence element installed on a feedthrough plate. Fig. 4 a detailed, cropped, approximately scaled view of a section of the centrifugal pump of Fig. 2, which shows an embodiment of the turbulence element arranged in an annular sealing cavity. Fig. 5 a cross-sectional view of the turbulence element of Fig. 4 along a line 5-5 from Fig. 4 shows. Fig. 6 a side view of the Fig. 5 shows the turbulence element. Fig. Figure 7 is a partially cutaway view of an embodiment showing two turbulence elements disposed on opposite sides of a seal assembly. Fig. 8 shows a perspective, approximately to scale, view of an embodiment of a turbulence element installed on a feedthrough plate of a fluid conveying device. Fig. 9 shows a perspective, approximately to scale, view of an embodiment of two turbulence elements installed on a feedthrough plate of a fluid conveying device. Fig. 10 shows a perspective, approximately to scale, view of an embodiment of three turbulence elements installed on a feedthrough plate of a fluid conveying device. Fig. 11 shows a perspective, approximately to scale, view of an embodiment of four turbulence elements installed on a feedthrough plate of a fluid conveying device. Fig. 12 shows a perspective, approximately to scale, view of an embodiment of four pairs of turbulence elements installed on a feedthrough plate of a fluid conveying device. Fig. 13 shows a perspective, approximately to scale, view of an embodiment of two turbulence elements installed on a feedthrough plate of a fluid conveying device. Fig. 14 shows a perspective, approximately to scale, view of an embodiment of four turbulence elements installed on a feedthrough plate of a fluid conveying device. Fig. 15 shows a perspective, approximately to scale, view of an embodiment of two turbulence elements installed on a feedthrough plate of a fluid conveying device. Fig. 16 shows a perspective, approximately to scale, view of an embodiment of eight turbulence elements installed on a feedthrough plate of a fluid conveying device.

[0011] The following description relates to various embodiments of seal protection systems for a seal assembly in a fluid handling device, where the seal protection systems comprise one or more turbulence elements arranged in an annular seal cavity. In some embodiments, the seal protection systems and turbulence elements are designed for a water pump in an engine cooling system of an internal combustion engine in a vehicle, such as a rail vehicle. In other embodiments, the seal protection systems and turbulence elements may be designed for other fluid handling devices and for use with other engines and / or vehicles.

[0012] Fig. Figure 1 shows a schematic diagram of an example of a rail vehicle in which the seal protection systems and turbulence elements can be used. Fig. 2 shows a cutaway view of an embodiment of a centrifugal pump having a seal protection system and an associated turbulence element according to an embodiment of the invention. Fig. 3 shows a perspective view of part of the centrifugal pump of Fig. 2, in which an embodiment of a turbulence element is installed on a feedthrough plate of the pump.

[0013] Fig. Figure 4 shows a detailed, cutaway, approximately to scale view of a section of the centrifugal pump of Fig. 2, which shows an embodiment of a turbulence element arranged in an annular sealing cavity. Fig. Figure 5 shows a cross-sectional view of the turbulence element of Fig. 4 along a line 5-5 from Fig. 4. Fig. 6 shows a side view of the Fig. 5 shown turbulence element. Fig. Figure 7 is a partially cutaway view of an embodiment showing two turbulence elements disposed on opposite sides of a seal assembly. Fig. 8-16 show perspective views of one or more turbulence elements installed on a feedthrough plate of a fluid conveying device.

[0014] It should be understood that the methods described herein may be applied in a variety of fluid handling devices used in various applications. In some examples, the methods described herein may be used in centrifugal pumps used in cooling systems of various engine types and with various engine-driven systems. Some of these engine systems may be stationary, while others may be on semi-mobile or mobile platforms. In some examples, semi-mobile platforms may be relocated between periods of operation, for example, mounted on flatbed trailers. In other examples, mobile platforms may include self-propelled vehicles. Such vehicles may include, for example, mining equipment, boats, road transport vehicles, overhead trucks (OHVs), and rail vehicles.To make the illustration clearer, a locomotive is taken as an example of a mobile platform carrying a system incorporating an embodiment of the invention.

[0015] Before further discussing the methods described herein, an example of a platform is disclosed in which the seal protection systems and turbulence elements may be designed for an engine in a vehicle, such as a rail car. Fig. 1 shows a block diagram of one embodiment of a vehicle system 100 (e.g., a locomotive system), depicted herein as a rail vehicle 108, configured to travel 102 on a rail via a plurality of wheels 110. As depicted, the rail vehicle 108 includes an engine 104, such as an internal combustion engine. In other non-limiting embodiments, the engine 104 may be a stationary machine, such as in a power plant application, or a machine in a vessel or propulsion system for other non-road vehicles, as noted above.

[0016] The vehicle system 100 includes an engine cooling system 150. The engine cooling system 150 includes a tank 158 that may contain a coolant, such as water. A pump 166, such as a centrifugal pump, circulates the coolant through the engine 104 to absorb heat dissipated by the engine and to deliver the heated cooling fluid to a heat exchanger, such as a heat sink 154. In one example, the pump 166 is splined to and driven by the crankshaft 106 of the engine 104. In this example, the pump 166 may be a variable-speed pump that operates at different speeds depending on the speed of the crankshaft 106.

[0017] A fan 162 may be connected to the heat sink 154 to maintain airflow through the heat sink while the engine 104 is operating and the vehicle 108 is traveling slowly or stopped. In some examples, the fan speed may be controlled by a control unit (not shown). Coolant cooled by the heat sink 152 enters the tank 158. The coolant may then be pumped by the pump 166 back to the engine 104 or to another component of the vehicle system, such as an exhaust gas recirculation (EGR) cooler.

[0018] As in Fig. 1, the engine 104 may receive intake air for combustion from an intake conduit 112. The intake conduit 112 receives ambient air from an air cleaner (not shown) that filters air from the ambient air of the rail vehicle 108. Exhaust gas resulting from combustion in the engine 104 may be supplied to an exhaust conduit 116. Exhaust gas flows through the exhaust conduit 116 and out an exhaust stack (not shown) of the rail vehicle 108. A portion of the exhaust gas may also flow through an EGR conduit 134 and into the EGR cooler 138, where it is cooled and returned to the intake conduit 112.

[0019] The vehicle system 100 may also include a turbocharger 120 disposed between the intake conduit 112 and the exhaust conduit 116. The turbocharger 120 increases the air loading of outside air drawn into the intake conduit 112 to provide greater charge density during combustion to increase power output and / or engine operating efficiency. The supercharger 120 may include a compressor (not shown) driven at least in part by a turbine (not shown).

[0020] In one example, engine 104 is a diesel engine that combusts air and diesel fuel through compression ignition. In other non-limiting embodiments, engine 104 may combust fuel including gasoline, kerosene, biodiesel, or other petroleum distillates of similar density through compression ignition (and / or spark ignition).

[0021] The rail vehicle 108 may further include a controller (not shown) to control various components related to the vehicle system 104. In one example, the controller comprises a computer control system. The controller may further include computer-readable storage media containing code to enable on-board monitoring and control of the operation of the rail vehicle. While the controller directs the control of the vehicle system 104, it may also be configured to receive signals from a variety of engine sensors to determine operating parameters and conditions and, accordingly, to control various engine actuators to control the operation of the rail vehicle.For example, the controller 148 may receive signals from various engine sensors, including engine speed, engine load, engine coolant temperature, boost pressure, exhaust pressure, ambient pressure, exhaust temperature, etc. Accordingly, the controller may control the engine 104 by sending commands to various components, such as a heat sink 154, a pump 166, drive motors, alternator, cylinder valves, throttle body, etc.

[0022] Fig. 2 is a cutaway view of a centrifugal pump 204 having a seal assembly 206 and a seal protection system 208 and an associated turbulence element 212 according to an embodiment of the invention. Fig. 2 is approximately to scale. As in Fig. 2, fluid enters an inlet 216 of pump 204 generally in an axial direction along a central axis 220. A shaft 224 is disposed downstream of the inlet and rotatably disposed parallel to and coaxial with the central axis 220. A rotatable member, such as an impeller 228, is connected to the shaft 224 and rotatably disposed within a housing 232 of the pump 204. As described in more detail below, the housing 232 includes an annular seal portion 234 disposed generally around the seal assembly 206 and the seal protection system 208.

[0023] As in Fig. 2, the shaft 224 has a driven end 236 connected to a gear 240. In one example, the gear 240 is driven by a crankshaft of an engine, such as the crankshaft 106 of the engine 104, as described above with reference to Fig. 1. Note that the gear 240 may be driven in any suitable manner, such as via a belt, a driven gear, etc. An output end 244 of the shaft 224 is disposed opposite the driven end 236. The output end 244 of the shaft 224 extends through a grommet 248 and through the seal assembly 206 and is connected to the impeller 228 to cause rotation of the impeller.

[0024] As described in more detail below, the seal protection system 208 includes the grommet plate 248 disposed circumferentially around the shaft 224. The seal assembly 206 has a first end adjacent the grommet plate 248 and also disposed circumferentially around the shaft 224. The seal assembly 206 also has a second end opposite the first end and adjacent an inner surface 246 of the impeller 228. The grommet plate 248, the inner surface 246 of the impeller 228, the seal assembly 206, and the annular seal portion 234 of the housing 232 cooperate to form an annular seal cavity 252.

[0025] When the gear 240 is driven, rotation of the shaft 224 and impeller 228 is effected. Fluid entering the inlet 216 along the central axis 200 is moved radially outward by the rotating impeller 228 through an outlet 256 fluidly connected to the inlet 216. As shown by arrows 260, a portion of the fluid moved by the impeller 228 flows behind the impeller and along its inner surface 246 into the annular seal cavity 252. Under some operating conditions, the fluid flow 260 may substantially fill the annular seal cavity 252. Under other operating conditions, the fluid flow 260 may only partially fill the annular seal cavity 252. As stated above, such fluid in the annular seal cavity 252 may contact the seal assembly 206 and provide lubrication and cooling of the components of the seal assembly.

[0026] Fluid within the annular seal cavity 252 may also be subjected to centrifugal forces generated by the impeller 228. These forces may tend to pull fluid away from the seal assembly 206, which may result in the formation of one or more air pockets adjacent to the seal assembly 206. As indicated above, such air pockets may locally increase the friction and temperatures of the seal assembly 206, causing increased wear of these components and potentially shortening the service life of the seal assembly 206.

[0027] To solve the problems mentioned and as in Fig. 3-6, the seal protection system 208 includes a turbulence element 212 disposed within the annular seal cavity 252. Fig. 3 shows a perspective, approximately to scale view of the Fig. 2, which is arranged on a feedthrough plate 248. Note that Fig. 3 shows the shaft 224 without the impeller 228 to simplify the illustration. In one example, the impeller 228 may rotate in the direction of arrow R during operation of the pump 204, thereby correspondingly creating a fluid flow direction within the annular seal cavity 252 in the direction of the action arrow R. As shown in Fig. 4, the turbulence element 212 is mounted on the feedthrough plate 248 between the seal assembly 206 and the annular seal portion 234 of the housing 232. Thus, and as described in more detail below, one advantage that may be realized in practicing some embodiments of the described systems and devices is that the turbulence element disrupts fluid flow within the annular seal cavity 252 to inhibit the formation of an air pocket adjacent the seal assembly 206.

[0028] The seal assembly 206 has a first end 402 adjacent to the feedthrough plate 248 and a second, opposite end 404 adjacent to the impeller 228. As shown in Fig. 4, in one example, the seal assembly 206 may include a collar 406 disposed circumferentially around the shaft 224. An elastomeric collar O-ring 408 may be retained in an annular O-ring detent within the collar 406. A mating ring 410 surrounds the collar 406 and is disposed between the collar and an axially extending surface 414 of the feedthrough plate 248. An elastomeric mating ring O-ring 418 may be retained in an annular mating ring O-ring detent 422 within the collar 410.

[0029] Further with reference to Fig. 4, an annular sealing element 426 rests against the mating ring 410 and is received by a support element 430. The annular sealing element 426 can be urged against a mating surface 428 of the mating ring 410 by an elastic element 434, for example a spring, via the support element 430. A retaining part 438 is captively attached to a distal end of the sleeve 406 and has an axially extending surface 442 that holds a portion of the elastic element 434 between the axially extending surface and the sleeve 406. The retaining part 438 further has an outer surface 446 that extends radially from the distal end of the sleeve 406 and defines a working height 450 of the sealing assembly 206. In one example, the working height 450 of the seal assembly 206 may be an axial distance between the mating surface 428 of the mating ring 410 and the outer surface 446 of the retaining part 438.As described in more detail below, in one example, the turbulence element 212 may extend axially from the feedthrough plate 248 to a distance less than the working height 450 of the seal assembly 206.

[0030] What Fig. 5 and Fig. 6 is concerned, Fig. 5 a cross-sectional view of the turbulence element 212 of Fig. 4 along line 5-5 from Fig. 4. Fig. 6 shows a side view of the Fig. 5. In this example, the turbulence element 212 may comprise a block having an upper surface 502 and an opposite parallel lower surface 506. An inner surface 510 may extend between the upper surface 502 and the lower surface 506 and may have an arcuate profile. In one example, the arcuate profile of the inner surface 510 may have a radius of curvature A of about 4.29 cm. In other examples, the inner surface 510 may have a different radius of curvature according to the design and dimensions of a corresponding seal assembly, a corresponding impeller, and other components of a fluid conveying device. As also shown in Fig. 3, the inner surface 510 may cooperate with the seal assembly 206 in the annular seal cavity 252 to define an internal channel 514 between the inner surface and the seal assembly. As best seen in Fig. 3, the inner channel 514 in this example may have an arcuate profile that substantially corresponds to the arcuate profile of the inner surface 510 of the turbulence element 212.

[0031] The turbulence element 212 has an outer surface 518 that is spaced from the inner surface 510 and that also has an arcuate profile. In one example, the arcuate profile of the outer surface 518 may have a radius of curvature B of approximately 9.37 cm. In other examples, the outer surface 518 may have a different radius of curvature according to the design and dimensions of a corresponding seal assembly, impeller, and other components of a fluid handling device. A front surface 520 extends between the inner surface 510 and the outer surface 518. A rear surface 526 is spaced from the front surface 520 and also extends between the inner surface 510 and the outer surface 518.The inner surface 510, the outer surface 518, the front surface 520, and the rear surface 526 each extend between the upper surface 502 and the lower surface 506 to define a thickness D of the turbulence element 212. In one example, the thickness D may be approximately 3.0 cm. In other examples, the turbulence element 212 may have a different thickness D according to the design and dimensions of a corresponding seal assembly, impeller, and other components of a fluid handling device.

[0032] As again in Fig. 3, in one example, the outer surface 518 may cooperate with the annular sealing portion 234 of the housing 232 to form an outer channel 530 in the annular sealing cavity 252 between the outer surface and the annular sealing portion of the housing. As best seen in Fig. 3, the outer channel 530 in this example may have an arcuate profile that substantially corresponds to the arcuate profile of the outer surface 518 of the turbulence element 212.

[0033] In this example, a portion of the fluid flowing within the annular seal cavity 252 in the direction of the action arrow contacts the front surface 520 of the turbulence element 212. Other portions of the fluid are directed around the turbulence element 212 through the inner channel 514 and the outer channel 530 and over the upper surface 502 of the turbulence element. Advantageously, in this configuration, the turbulence element 212 can disrupt the fluid flow within the annular seal cavity 252 to inhibit the formation of an air pocket adjacent to the seal assembly 206 while also allowing a portion of the fluid flow to continuously flow through the inner channel 514 and contact the seal assembly. The flow path provided by the outer channel 530 can also prevent the buildup of excessive pressure in areas adjacent to the front surface 520.

[0034] As again in Fig. 5, the upper surface of the turbulence element 212 may define a first region bounded by the inner surface 510, the outer surface 518, the front surface 520, and the rear surface 526. A second region, corresponding to the annular sealing cavity 252, may be defined as an annular region created by moving the front surface 520 of the turbulence element 212 through a 360-degree radius of curvature A through the annular sealing cavity to create an annular region. In some examples, the first region defined by the upper surface 502 of the turbulence element 212 is no greater than one percent of the second annular region corresponding to the annular sealing cavity 252. In more specific examples, the percentage may range from about 5.0% to 20%, and in other examples from about 10% to 15%, and in one example, it may range from about 12.5%.In this way, in the practice of some embodiments, an advantage may be realized in that sufficient circulation of fluid may be maintained within the annular seal cavity 252 and adjacent the seal assembly 206, while simultaneously providing flow disturbance to inhibit the formation of one or more air pockets adjacent the seal assembly 206.

[0035] In other non-limiting embodiments, the turbulence element 212 may be removably connected to the feedthrough plate 248. With reference to Fig. 3-5, in one example, the turbulence element 212 may have a first opening 534, and the feedthrough plate 248 may have a second opening 538. A fastener 542 may extend through the first opening 534 and the second opening 538 to connect the turbulence element 212 to the feedthrough plate 248. The turbulence element 212 may also have a third opening 546, and the feedthrough plate 248 may have a fourth opening (not shown). A second fastener 554 may extend through the third opening 546 and the fourth opening to removably connect the turbulence element 212 to the feedthrough plate 248.

[0036] In some examples, the first opening 534 and the second opening 546 may be disposed at a common radius of curvature E. In a more specific, non-limiting example, the radius of curvature E may be about 8.26 cm, and the first opening 534 and the second opening 546 may be spaced apart along the radius of curvature E by an angle F of about 22.5 degrees. In this example, the center of the first opening 534 may be spaced apart from the front surface 520 by an angle G of about 10.0 degrees along the radius of curvature E. Likewise, the center of the second opening 546 may be spaced apart from the rear surface 526 by an angle G of about 10.0 degrees along the radius of curvature E. With reference to this non-limiting example, one advantage that may be realized is improved manufacturability of the turbulence element 212.

[0037] Advantageously, by releasably connecting the turbulence element 212 to the feedthrough plate 248, the turbulence element can be conveniently removed from the feedthrough plate for repair or maintenance. Furthermore, in other non-limiting embodiments, the turbulence element 212 can be removed and replaced with another turbulence element, for example, having a different configuration. It should also be noted that in yet other non-limiting embodiments, the turbulence element 212 can be welded or otherwise non-releasably connected to the feedthrough plate 248, or can be attached to a separate mounting plate that is subsequently attached to the feedthrough plate.In still other non-limiting embodiments, thin plates welded to the feedthrough plate 248 or a separate mounting plate subsequently bolted to the feedthrough plate may also be used.

[0038] There now follow descriptions of other non-limiting embodiments of one or more turbulence elements that may be used in conjunction with the seal protection system 208 and the centrifugal pump 204 described above and in Fig. 1-6. The one or more turbulence elements are shown mounted on a feedthrough plate, such as feedthrough plate 248, with the other components of seal protection system 208 and centrifugal pump 204 not shown for clarity. As indicated above, the one or more turbulence elements may be removably connected to feedthrough plate 248, welded or otherwise non-removably connected to the feedthrough plate, or attached to a separate mounting plate that is subsequently attached to the feedthrough plate.

[0039] As in Fig. 7, in one non-limiting embodiment, a first turbulence element 702 and a second turbulence element 706 may be provided on opposite sides of the shaft 224. In one example, the first turbulence element 702 and the second turbulence element 706 may have the shape and dimensions of the turbulence element 212 described above. In other examples, one or both of the first turbulence element 702 and the second turbulence element 706 may have a shape and / or dimensions that differ from those of the turbulence element 212.

[0040] As in Fig. 7, the first turbulence element 702 may define a first inner channel 710 having a first inner diameter 714 relative to the central axis 220 of the shaft 224 (as shown in Fig. 2). The first inner channel 710 may also have a first outer diameter 718 with respect to the central axis 220. In one example, the second turbulence element 706 may have a second inner channel 722 having a second inner diameter 726 with respect to the central axis 220 of the shaft 224, wherein the second inner diameter is substantially equal to the first inner diameter 714. The second inner channel 722 may also have a second outer diameter 730 with respect to the central axis 220, wherein the second outer diameter is substantially equal to the first outer diameter 718. Advantageously, the configuration of the first turbulence element 702 and the second turbulence element 706 on the feedthrough plate 248 may create increased flow disturbance within the annular seal cavity 252 to further prevent the formation of air pockets adjacent the seal assembly 206.

[0041] Fig. 8 shows another non-limiting orientation form having a turbulence element comprising an elongated, substantially rectangular block 802. An inner surface 806 of the block 802 is spaced from an inner edge 810 of the feedthrough plate 248 to define an inner channel 414 between the inner surface and the seal assembly 206 (not shown). The inner surface 806 may be oriented in a plane substantially perpendicular to a top surface 250 of the feedthrough plate 248. A line 812 is shown extending axially through the center of the feedthrough plate 248 and substantially perpendicular to the top surface 250 of the feedthrough plate. The plane of the inner surface 806 may also be substantially perpendicular to a line 808 extending radially from the line 812.

[0042] An outer surface 818 of block 802 is spaced from an outer edge 822 of feedthrough plate 248 to define an outer channel 826 between the outer surface and the annular sealing portion 234 of housing 232 (not shown). Like inner surface 806, the outer surface may be oriented in a plane substantially perpendicular to the top surface 250 of feedthrough plate 248. The plane of outer surface 818 may also be substantially perpendicular to line 808. Advantageously, this configuration of turbulence element 802 on feedthrough plate 248 may provide flow disturbance within the annular sealing cavity 252 to help prevent the formation of air pockets adjacent seal assembly 206.

[0043] Fig. Figure 9 shows another non-limiting embodiment comprising a first turbulence element 902 and a second turbulence element 906 located on opposite sides of the feedthrough plate 248. Both the first turbulence element 902 and the second turbulence element 906 have a structure and geometry similar to the daily, substantially rectangular block 802 shown in Fig. 8. The first turbulence element 902 has an inner surface 910 spaced from an inner edge 914 of the feedthrough plate 248 to define an inner channel 918 between the inner surface and the seal assembly 206 (not shown). An outer surface 922 of the first turbulence element 902 is spaced from an outer edge 926 of the feedthrough plate 248 to define an outer channel 930 between the outer surface and the annular seal portion 234 of the housing 232 (not shown).

[0044] Likewise, an inner surface 934 of the second turbulence element 906 is spaced from an inner edge 938 of the feedthrough plate 248 to define an inner channel 942 between the inner surface and the seal assembly 206. An outer surface 946 of the second turbulence element 902 is spaced from an outer edge 950 of the feedthrough plate 248 to define an outer channel 954 between the outer surface and the annular seal portion 234 of the housing 232. In one example, the two inner surfaces 910 and 934 may be aligned in planes substantially perpendicular to the top surface 250 of the feedthrough plate 248. A line 962 is shown extending axially through the center of the feedthrough plate 248 and substantially perpendicular to the top surface 250 of the feedthrough plate. The planes of the two inner surfaces 910 and 934 may also be substantially perpendicular to lines 908 and 958, respectively, extending radially from line 962.

[0045] Like the inner surfaces 910 and 934, the two outer surfaces 922 and 946 can be aligned in planes substantially perpendicular to the upper surface 250 of the feedthrough plate 248. The planes of the two outer surfaces 922 and 946 can also be substantially perpendicular to lines 908 and 958, respectively. Advantageously, this configuration of the first turbulence element 902 and the second turbulence element 906 on the feedthrough plate 248 can cause flow disturbance within the annular seal cavity 252, preventing the formation of air pockets adjacent to the seal assembly 206. By arranging the first turbulence element 902 and the second turbulence element 906 on opposite sides of the feedthrough plate 248, this configuration can also create substantially symmetrical turbulence in regions adjacent to the opposite sides.Advantageously, such symmetrical turbulence can balance corresponding loads applied by the circulating fluid to the rotating impeller 228.

[0046] Fig. 10 shows another non-limiting embodiment that includes a first turbulence element 1002, a second turbulence element 1006, and a third turbulence element 1010. In one example, the first turbulence element 1002, the second turbulence element 1006, and the third turbulence element 1010 may be evenly spaced around the perimeter of the feedthrough plate 248. In other words, the first turbulence element 1002, the second turbulence element 1006, and the third turbulence element 1010 may be spaced approximately in 120-degree increments around the perimeter of the feedthrough plate 248. The first turbulence element 1002, the second turbulence element 1006, and the third turbulence element 1010 may each have a structure and geometry similar to that shown in Fig. 8 is similar to the elongated, substantially rectangular block 802 shown.

[0047] In one example, the first turbulence element 1002, the second turbulence element 1006, and the third turbulence element 1010 may each be aligned with the upper surface 250 of the feedthrough plate 248 in a manner similar to that shown in Fig. 8. More specifically, the first turbulence element 1002, the second turbulence element 1006, and the third turbulence element 1010 may each have an inner surface 1014, 1018, and 1022, respectively, spaced from a corresponding inner edge 1026, 1030, and 1034 of the feedthrough plate 248 to define an inner channel 1038, 1042, and 1046, respectively, between the inner surfaces and the seal assembly 206. Likewise, the first turbulence element 1002, the second turbulence element 1006, and the third turbulence element 1010 may each have an outer surface 1050, 1054, and 1058, respectively, spaced from a corresponding outer edge 1062, 1066, and 1070 of the feedthrough plate 248 to define an outer channel 1074, 1078, and 1082, respectively, between the outer surfaces and the annular sealing portion 234 of the housing 232.

[0048] In one example, the three inner surfaces 1014, 1018, and 1022 may be aligned in planes substantially perpendicular to the top surface 250 of the feedthrough plate 248. A line 1090 is shown extending axially through the center of the feedthrough plate 248 and substantially perpendicular to the top surface 250 of the feedthrough plate. The planes of the three inner surfaces 1014, 1018, and 1022 may also be substantially perpendicular to lines 1084, 1086, and 1088, respectively, extending radially from line 1090.

[0049] Like the inner surfaces 1014, 1018, and 1022, the three outer surfaces 1050, 1054, and 1058 may be aligned in planes substantially perpendicular to the top surface 250 of the feedthrough plate 248. The planes of the three outer surfaces 1050, 1054, and 1058 may also be substantially perpendicular to lines 1084, 1086, and 1088, respectively, extending radially from line 1090. Advantageously, this configuration of the first turbulence element 1002, the second turbulence element 1006, and the third turbulence element 1010 on the feedthrough plate 248 may provide flow disturbance within the annular seal cavity 252, preventing the formation of air pockets adjacent to the seal assembly 206.Furthermore, by evenly spacing the first turbulence element 1002, the second turbulence element 1006, and the third turbulence element 1010 around the perimeter of the feedthrough plate 248, this design can create substantially symmetrical turbulence around the feedthrough plate. Advantageously, such symmetrical turbulence can balance corresponding loads applied by the circulating fluid to the rotating impeller 228.

[0050] Fig. 11 shows another non-limiting embodiment including a first turbulence element 1102, a second turbulence element 1106, a third turbulence element 1110, and a fourth turbulence element 1114. In one example, the first turbulence element 1102, the second turbulence element 1106, the third turbulence element 1110, and the fourth turbulence element 1114 may be evenly spaced around the perimeter of the feedthrough plate 248.

[0051] In other words, the first turbulence element 1102, the second turbulence element 1106, the third turbulence element 1110, and the fourth turbulence element 1114 may be spaced apart from one another approximately in 90-degree increments around the circumference of the feedthrough plate 248. The first turbulence element 1102, the second turbulence element 1106, the third turbulence element 1110, and the fourth turbulence element 1114 each have a structure and geometry similar to the elongated, substantially rectangular block 802 shown in Fig. 8 is similar.

[0052] In one example, the first turbulence element 1102, the second turbulence element 1106, the third turbulence element 1110, and the fourth turbulence element 1114 may each be aligned on the upper surface 250 of the feedthrough plate 248 in a manner that corresponds to the Fig. 8. More specifically, the first turbulence element 1102, the second turbulence element 1106, the third turbulence element 1110, and the fourth turbulence element 1114 may each have an inner surface 1118, 1120, 1122, and 1124, respectively, spaced from a corresponding inner edge 1126, 1128, 1130, and 1132 of the feedthrough plate 248 to define an inner channel 1142, 1144, 1146, and 1148, respectively, between the inner surfaces and the seal assembly 206. Likewise, the first turbulence element 1102, the second turbulence element 1106, the third turbulence element 1110, and the fourth turbulence element 1114 may each have an outer surface 1150, 1152, 1154, and 1156, respectively, spaced from a corresponding outer edge 1158, 1160, 1162, and 1164 of the feedthrough plate 248 to define an outer channel 1166, 1168, 1170, and 1172, respectively, between the outer surfaces and the annular sealing portion 234 of the housing 232.

[0053] In one example, the four inner surfaces 1118, 1120, 1122, and 1124 may be aligned in planes substantially perpendicular to the top surface 250 of the feedthrough plate 248. A line 1186 is shown extending axially through the center of the feedthrough plate 248 and substantially perpendicular to the top surface 250 of the feedthrough plate. The planes of the four inner surfaces 1118, 1120, 1122, and 1124 may also be substantially perpendicular to lines 1176, 1178, 1180, and 1182, respectively, which extend radially from line 1186.

[0054] Like the inner surfaces 1118, 1120, 1122 and 1124, the four outer surfaces 1150, 1152, 1154, and 1156 are aligned in planes substantially perpendicular to the upper surface 250 of the feedthrough plate 248. The planes of the four outer surfaces 1150, 1152, 1154, and 1156 may also be substantially perpendicular to the lines 1176, 1178, 1180, and 1182, respectively. Advantageously, this configuration of the first turbulence element 1102, the second turbulence element 1106, the third turbulence element 1110, and the fourth turbulence element 1114 on the feedthrough plate 248 may provide flow disturbance within the annular seal cavity 252, preventing the formation of air pockets adjacent to the seal assembly 206.Furthermore, by evenly spacing the first turbulence element 1102, the second turbulence element 1106, the third turbulence element 1110, and the fourth turbulence element 1114 around the perimeter of the feedthrough plate 248, this design can create substantially symmetrical turbulence around the feedthrough plate. Advantageously, such symmetrical turbulence can balance corresponding loads applied by the circulating fluid to the rotating impeller 228.

[0055] Fig. 12 shows another non-limiting embodiment that includes four pairs of turbulence elements. In one example, a first pair of turbulence elements includes a first turbulence element 1202 and a second turbulence element 1204 arranged substantially parallel to each other to define a gap 1206 between them. The first turbulence element 1202 may be radially aligned with a third turbulence element 1208 arranged on an opposite side of the feedthrough plate 248. The second turbulence element 1204 may be radially aligned with a fourth turbulence element 1210 arranged on an opposite side of the feedthrough plate 248. The third turbulence element 1208 and the fourth turbulence element 1210 comprise a second pair of turbulence elements and are arranged substantially parallel to each other to define a gap 1212 between them.

[0056] Likewise, a third pair of turbulence elements includes a fifth turbulence element 1216 and a sixth turbulence element 1218 arranged substantially parallel to each other to define a gap 1220 therebetween. The fifth turbulence element 1216 may be radially aligned with a seventh turbulence element 1222 arranged on an opposite side of the feedthrough plate 248. The sixth turbulence element 1218 may be radially aligned with an eighth turbulence element 1224 arranged on an opposite side of the feedthrough plate 248. The seventh turbulence element 1222 and the eighth turbulence element 1224 comprise a fourth pair of turbulence elements and are arranged substantially parallel to each other to define a gap 1226 therebetween.The first turbulence element 1202, the second turbulence element 1204, the third turbulence element 1208, the fourth turbulence element 1210, the fifth turbulence element 1216, the sixth turbulence element 1218, the seventh turbulence element 1222, and the eighth turbulence element 1224 may each also have a structure and geometry similar to the elongated, substantially rectangular block 802 shown in FIG. Fig. 8. Advantageously, this configuration of four pairs of turbulence elements on the feedthrough plate 248 can provide flow disturbance within the annular seal cavity 252, preventing the formation of air pockets adjacent to the seal assembly 206. Furthermore, the gap between each pair of turbulence elements can provide increased turbulence within the annular seal cavity 252 for applications and designs that can benefit from a higher degree of flow disturbance.

[0057] Fig. Figure 13 shows another non-limiting embodiment having the first turbulence element 902 and the second turbulence element 906 shown in Fig. 9 and described above. In this embodiment, the first turbulence element 902 and the second turbulence element 906 are angled with respect to the center of the feedthrough plate 248. In one example, the inner surface 934 of the second turbulence element 906 is oriented in a plane that forms an oblique angle 1304 with respect to the line 958 extending radially from the line 962. In this example, the line 958 intersects the right edge 970 of the second turbulence element 906. The angle 1304 may range between about 91 degrees and 179 degrees, and more particularly between about 100 degrees and 169 degrees, and more particularly between about 110 and 159 degrees, and more particularly about 135 degrees.Additionally, with respect to this non-limiting embodiment, during operation of the pump 204, the impeller 228 may rotate in the opposite direction of the action arrow R', thus creating a fluid flow direction within the annular seal cavity 252 in the opposite direction of the arrow R'. Advantageously, the angled configuration of the first turbulence element 902 and the second turbulence element 906 directs the fluid flow toward the seal assembly 206, thereby preventing air pockets from forming adjacent the seal assembly.

[0058] Still referring to Fig. 13, the inner surface 934 may define a variable-depth inner channel 942' between the inner surface and the seal assembly 206. Similarly, the inner surface 910 of the first turbulence element 902 may define a variable-depth channel 918' between the inner surface 910 and the seal assembly 206. It should also be noted that the outer channels 930' and 954' may have a variable depth relative to the outer perimeter of the feedthrough plate 248 adjacent to the respective outer channel. Furthermore, the outer channels 930' and 954' may have a variable depth greater than the variable depth of the corresponding inner channels 918' and 942', respectively.Advantageously, for certain applications and designs of seal assemblies and corresponding fluid conveying devices, this configuration of the first turbulence element 902 and the second turbulence element 906 on the feedthrough plate 248 can create a flow disturbance within the annular seal cavity 252, which ensures that the formation of air pockets adjacent to the seal assembly 206 is better avoided.

[0059] Fig. 14 shows another non-limiting embodiment including a first turbulence element 1402, a second turbulence element 1406, a third turbulence element 1410, and a fourth turbulence element 1414. In one example, the first turbulence element 1402, the second turbulence element 1406, the third turbulence element 1410, and the fourth turbulence element 1414 may be evenly spaced around the perimeter of the feedthrough plate 248. In other words, the first turbulence element 1402, the second turbulence element 1406, the third turbulence element 1410, and the fourth turbulence element 1414 may be spaced approximately 90-degree apart around the perimeter of the feedthrough plate 248.

[0060] The first turbulence element 1402, the second turbulence element 1406, the third turbulence element 1410, and the fourth turbulence element 1414 may each have an arcuate shape with a rectangular cross-section. In one example, the first turbulence element 1402 and the third turbulence element 1410 are as shown in Fig. 14, are arranged on an opposite side of the feedthrough plate 248 and have curvatures oriented in opposite directions with respect to the feedthrough plate's upper surface 250. In other words, the first turbulence element 1402 may have a convex shape with a leading edge oriented counterclockwise around the feedthrough plate 248, while the third turbulence element 1410 may have a convex shape with a leading edge oriented clockwise around the feedthrough plate. In other words, the second turbulence element 1406 may have a convex shape with a leading edge oriented clockwise around the feedthrough plate 248, while the third turbulence element 1414 may have a convex shape with a leading edge oriented counterclockwise around the feedthrough plate.

[0061] In one example, the first turbulence element 1402, the second turbulence element 1406, the third turbulence element 1410, and the fourth turbulence element 1414 may each have a rectangular inner surface 1418, 1420, 1422, and 1424. A line 1444 may extend axially through the center of the feedthrough plate 248 and substantially perpendicular to the feedthrough plate top surface 250. Each of the rectangular inner surfaces 1418, 1420, 1422, and 1424 may be aligned in a plane that forms an oblique angle 1426, 1428, 1430, and 1432 with respect to lines 1436, 1438, 1440, and 1442, respectively, extending radially from the line 1444. Each of the angles 1426, 1428, 1430, and 1432 can range between about 91 degrees and 179 degrees, and more specifically between about 100 degrees and 169 degrees, and even more specifically between about 110 and 159 degrees, and even more specifically at about 135 degrees. As also in Fig. 14, each of the inner surfaces 1418, 1420, 1422, and 1424 may define an inner channel 1450, 1452, 1454, and 1456, respectively, between the inner surface and the seal assembly 206.

[0062] It should also be noted that the outer channels 1460, 1462, 1464, and 1466 may have a variable depth relative to the outer perimeter of the feedthrough plate 248 adjacent to the respective outer channel. Advantageously, this configuration of the first turbulence element 1402, the second turbulence element 1406, the third turbulence element 1410, and the fourth turbulence element 1414 on the feedthrough plate 248 may create specific flow disruption patterns within the annular seal cavity 252, which may better prevent the formation of air pockets adjacent to the seal assembly 206 for certain applications and designs of seal assemblies and corresponding fluid handling devices.

[0063] Fig. 15 shows another non-limiting embodiment including a first turbulence element 1502 and a second turbulence element 1506, each having an arcuate shape with a rectangular cross-section. In one example, the first turbulence element 1502 and the second turbulence element 1506 may have curvatures oriented in opposite directions with respect to the top surface 250 of the feedthrough plate. In other words, the first turbulence element 1502 may have a convex shape with a leading side 1510 oriented clockwise around the feedthrough plate 248, while the second turbulence element 1506 may have a convex shape with a leading side 1514 oriented counterclockwise around the feedthrough plate.Additionally, at least a portion of the leading side 1510 of the first turbulence element 1502 may oppose at least a portion of the leading side 1514 of the second turbulence element 1506 to form a passage 1518 therebetween.

[0064] In one example, a narrow portion of the passage 1518 may have a passage width 1520 that is smaller than a turbulence element width 1522 of the first turbulence element 1502. In one example, both the first turbulence element 1502 and the second turbulence element 1506 may each have an inner surface 1526 and 1530, respectively. A line 1550 is shown extending axially through the center of the feedthrough plate 248 and substantially perpendicular to the feedthrough plate top surface 250. Each of the inner surfaces 1526 and 1530 is oriented in a plane forming an oblique angle 1534 and 1538, respectively, with respect to lines 1542 and 1546, respectively, extending radially from the line 1550. Each of the angles 1534 and 1538 can range between about 91 degrees and 179 degrees, and more specifically between about 100 degrees and 169 degrees, and even more specifically between about 110 and 159 degrees, and even more specifically at about 135 degrees.

[0065] As also in Fig. 15, each of the inner surfaces 1526 and 1530 may define an inner channel 1554 and 1558, respectively, of variable depth between the inner surface and the seal assembly 206. It should also be noted that the outer channels 1562 and 1566 may have a variable depth relative to the outer perimeter of the feedthrough plate 248 adjacent to the respective outer channel. Advantageously, for certain applications and designs of seal assemblies and corresponding fluid handling devices, this configuration of the first turbulence element 1502 and the second turbulence element 1506 on the feedthrough plate 248 may create flow disturbance patterns within the annular seal cavity 252 that may better prevent the formation of air pockets adjacent the seal assembly 206.

[0066] Fig. 16 shows another non-limiting embodiment having a plurality of disc-shaped turbulence elements, such as turbulence elements 1602, 1606, and 1608, disposed on the upper surface 250 of the feedthrough plate 248. As shown in Fig. 16, in one example, the plurality of disc-shaped turbulence elements may have different diameters. In other examples, one or more of the plurality of disc-shaped turbulence elements may have the same diameter. At least one of the disc-shaped turbulence elements, such as turbulence element 1602, may define an internal channel of variable depth, such as channel 1612, between the turbulence element and the seal assembly 206. In some examples, additional turbulence elements may also define channels of variable depth between the turbulence element and the seal assembly 206.Advantageously, for certain applications and designs of seal assemblies and corresponding fluid conveying devices, this configuration of multiple disc-shaped turbulence elements on the feedthrough plate 248 can create flow disturbance patterns within the annular seal cavity 252 that better prevent the formation of air pockets adjacent to the seal assembly 206.

[0067] Another embodiment relates to a turbulence element for an annular sealing cavity in a fluid conveying device. The turbulence element comprises a turbulence element body (e.g., a solid body made of metal, polymer, and / or other materials) arranged to cooperate with a seal assembly in the annular sealing cavity to define an internal channel between the inner surface and the seal assembly. The turbulence element body is further arranged to cooperate with a housing to define an external channel in the annular sealing cavity. The turbulence element serves to disrupt fluid flow in the annular sealing cavity to inhibit the formation of an air pocket adjacent to the seal assembly. The body of the turbulence element may be shaped as described elsewhere herein (e.g., Fig. 3, Fig. 8, Fig. 13, Fig. 14, Fig. 16 and so on).

[0068] Another embodiment relates to a seal protection system for a fluid conveying device. The system includes a seal assembly, a shaft extending through the seal assembly, an impeller mounted on the shaft, and a grommet disposed around the shaft. The grommet, impeller, seal assembly, and a housing cooperate to define an annular seal cavity. The system further includes a turbulence element disposed within the annular seal cavity and connected to the grommet. The turbulence element includes a turbulence element body disposed adjacent to the seal assembly and arranged to cooperate with the seal assembly to define an internal channel between the inner surface and the seal assembly. The body of the turbulence element is further disposed adjacent to the housing (i.e.a portion of the body extends from immediately adjacent the seal assembly to immediately adjacent the housing) and is arranged to cooperate with the housing to define an external channel within the annular seal cavity. The turbulence element serves to disrupt fluid flow within the annular seal cavity to inhibit the formation of an air pocket adjacent the seal assembly. The body of the turbulence element may be shaped as described elsewhere herein (e.g., . Fig. 3, Fig. 8, Fig. 13, Fig. 14, Fig. 16 and so on).

[0069] Another embodiment relates to a seal protection system for a fluid conveying device. The fluid conveying device includes a housing, a seal assembly, and a seal cavity, and may, but need not, additionally include other features as described elsewhere herein, e.g., a shaft extending through the seal assembly, an impeller mounted on the shaft, and a grommet disposed around the shaft. The seal protection system includes one or more turbulence elements disposed within the seal cavity (e.g., connected to the grommet or otherwise). The one or more turbulence elements serve to disrupt fluid flow within the seal cavity to inhibit the formation of an air pocket adjacent to the seal assembly. In one embodiment, the turbulence element is a wedge-shaped block having arcuate inner and outer surfaces ( Fig. 3 and the associated description apply thereto). In one embodiment, two or more spaced-apart turbulence elements are provided, each being a wedge-shaped block with arcuate inner and outer surfaces ( Fig. 3 and the associated description apply thereto). In another embodiment, the turbulence element is a rectangular solid body ( Fig. 8 and the associated description apply thereto). In another embodiment, two or more spaced-apart turbulence elements are provided, each of which is a rectangular solid body ( Fig. 8-13 and the associated description apply thereto). In another embodiment, the turbulence element has an arcuate shape with a rectangular cross-section ( Fig. 14-15 and the associated description apply). In another embodiment, two or more spaced-apart turbulence elements are provided, each having an arcuate shape with a rectangular cross-section ( Fig. 14-15 and the associated description apply thereto). In another embodiment, the turbulence element is a cylindrical solid body ( Fig. 16 and the associated description apply thereto). In another embodiment, two or more spaced-apart turbulence elements are provided, each of which is a cylindrical solid body ( Fig.16 and the associated description apply thereto). In another embodiment, two or more spaced-apart turbulence elements are provided which differ in shape (e.g., rectangular solid body, cylindrical solid body, wedge-shaped and / or arcuate with a rectangular cross-section).

[0070] Certain features or aspects of the invention are described herein as being annular. This may refer to the feature being entirely annular, at least generally or somewhat annular, and / or it may refer to the feature surrounding another feature (e.g., surrounding it in a circle).

[0071] In this description, references to "one embodiment" of the present invention should not be interpreted as excluding the existence of additional embodiments that also embody the recited features. Unless expressly stated to the contrary, embodiments that "comprise," "include," or "have" an element or a plurality of elements having a particular characteristic may include additional such elements that do not have that characteristic. The terms "including" and "in which" are used as the common-sense equivalents of the terms "comprising" and "wherein," respectively. Furthermore, the terms "first," "second," "second," and "third," etc., are used only as labels and are not intended to imply any numerical requirement or particular positional ordering of their objects.

Claims

[1] Turbulence element (212) for an annular sealing cavity (252) in a fluid conveying device, the turbulence element (212) comprising: an inner surface (510) having an at least partially concave arcuate profile arranged to cooperate with a seal assembly (206) in the annular seal cavity (252) to define an inner channel (514) between the inner surface (510) and the seal assembly (206). an outer surface (518) having an arcuate profile arranged to cooperate with a housing (232) to define a flow path providing outer channel (550) in the annular sealing cavity (252) between the outer surface (518) and the housing (232); a front surface (520) extending between the inner surface (510) and the outer surface (518); and a rear surface (526) spaced from the front surface (520) and extending between the inner surface (510) and the outer surface (518), wherein the inner surface (510) with the at least partially concave arcuate profile of the turbulence element (212) forms a corresponding arcuate profile in the inner channel (514), and wherein the inner channel (514) and the outer channel (530) disrupt fluid flow within the annular seal cavity (252) to inhibit the formation of an air pocket adjacent to the seal assembly (206). [2] The turbulence element (212) of claim 1, wherein the fluid conveying device comprises a rotatable member connected to a shaft (224) extending through the seal assembly (206), the seal assembly (206) having a first end (402) adjacent a feedthrough plate (248) and a second, opposite end (404) adjacent the rotatable member, the turbulence element (212) being connected to the feedthrough plate (248). [3] Turbulence element (212) according to claim 2, wherein the turbulence element (212) is detachably connected to the feedthrough plate (248). [4] The turbulence element (212) of claim 3, wherein the turbulence element (212) has a first opening (534) and the feedthrough plate (248) has a second opening (538), and a fastener (542) extends through the first opening (534) and the second opening (538) to releasably connect the turbulence element (212) to the feedthrough plate (248). [5] The turbulence element (212) of claim 2, wherein the seal assembly (206) includes a support portion (438) having an outer surface (446) defining a working height (450) of the seal assembly (206), and wherein the inner surface (510) of the turbulence element (212) extends from the feedthrough plate (248) to a position axially rearward of the outer surface (446) of the support portion (438). [6] Turbulence element (212) according to claim 1, wherein the inner channel (514) has a variable inner channel depth and the outer channel (530) has a variable outer channel depth. [7] The turbulence element (212) of claim 1, wherein the turbulence element (212) comprises a block having an upper surface (502) and an opposite, parallel lower surface (506), and wherein the inner surface (510), the outer surface (518), the front surface (520), and the rear surface (526) each extend between the upper surface (502) and the lower surface (506). [8] The turbulence element (212) of claim 7, wherein a first area of ​​the block upper surface (502) bounded by the inner surface (510), the outer surface (518), the front surface (520) and the rear surface (526) is no greater than 12.5% ​​of a second area of ​​the annular seal cavity (252) defined as an annular area created by movement of the front surface (520) of the turbulence element (212) about a radius of curvature A of 360 degrees through the annular seal cavity (252). [9] System comprising: a turbulence element according to claim 1, wherein the turbulence element is a first turbulence element (702) and the inner channel is a first inner channel (710) having a first inner diameter (714) and a first outer diameter (718); and a second turbulence element (706) spaced from the first turbulence element (702), the second turbulence element (706) being arranged to cooperate with the seal assembly (206) to define a second internal channel (722), the second internal channel (722) having a second internal diameter (726) substantially equal to the first internal diameter (714) and a second external diameter (730) substantially equal to the first external diameter (718). [10] Seal protection system (208) for a fluid conveying device, comprising: a seal assembly (206), a shaft (224) extending through the seal assembly (206), an impeller (228) mounted on the shaft (224), and a grommet plate (248) disposed around the shaft (224), the grommet plate (248), the impeller (228), the seal assembly (206), and a housing (232) cooperating to form an annular seal cavity (252); and a turbulence element (212) disposed within the annular sealing cavity (252) and connected to the feedthrough plate (248), the turbulence element (212) comprising: an inner surface (510) having an at least partially concave arcuate profile adjacent to the seal assembly (206) and arranged to cooperate with the seal assembly (206) to define an inner channel (514) between the inner surface (510) and the seal assembly (206); an outer surface (518) having an arcuate profile adjacent to the housing (232) and arranged to cooperate with the housing (232) to define an outer channel (530) in the annular sealing cavity (252); a front surface (520) extending between the inner surface (510) and the outer surface (518); and a rear surface (526) spaced from the front surface (520) and extending between the inner surface (510) and the outer surface (518), wherein the turbulence element (212) serves to disrupt fluid flow within the annular seal cavity (252) to inhibit the formation of an air pocket adjacent the seal assembly (206). [11] Seal protection system (208) according to claim 10, wherein the turbulence element (212) is releasably connected to the feedthrough plate (248). [12] The seal protection system (208) of claim 11, wherein the turbulence element (212) has a first opening (534) and the feedthrough plate (248) has a second opening (538), and a fastener extends through the first opening (534) and the second opening (538) to releasably connect the turbulence element (212) to the feedthrough plate (248). [13] The seal protection system (208) of claim 10, wherein the turbulence element is a first turbulence element (702) and further comprises a second turbulence element (706), the second turbulence element (706) being spaced from the first turbulence element (702), and the second turbulence element (706) being disposed within the annular seal cavity (252) and connected to the feedthrough plate (248). [14] The seal protection system (208) of claim 10, wherein the seal assembly (206) includes a support portion (438) having an outer surface (446) defining a working height (450) of the seal assembly (206), and wherein the inner surface (510) of the turbulence element (212) extends from the feedthrough plate (248) to a position axially rearward of the outer surface (446) of the support portion (438). [15] The seal protection system (208) of claim 10, wherein the inner channel (514) has a variable inner channel depth and the outer channel (530) has a variable outer channel depth. [16] A water pump (204) for an engine cooling system in an internal combustion engine, the water pump (204) comprising: an inlet (216) having a central axis (220); an outlet (256) fluidly connected to the inlet (216); a shaft (224) arranged downstream of the inlet (216) and rotatably arranged parallel to the central axis (200); an impeller (228) connected to the shaft (224); a seal assembly (206) disposed around the shaft (224), the seal assembly (206) including a first end (402) adjacent a grommet plate (248) and a second, opposite end (404) adjacent the impeller (228); and a turbulence element (212) connected to the feedthrough plate (248) and extending from the feedthrough plate (248) into an annular sealing cavity (252), the turbulence element (212) comprising: an inner surface (510) having an at least partially concave arcuate profile arranged to cooperate with the seal assembly (206) in the annular seal cavity (252) to define an inner channel (514) between the inner surface (510) and the seal assembly (206); and an outer surface (518) having an arcuate profile arranged to cooperate with a housing (232) to define an outer channel (530) in the annular seal cavity (252), wherein the turbulence element (212) serves to disrupt fluid flow within the annular seal cavity (252) to inhibit the formation of an air pocket adjacent the seal assembly (206). [17] Water pump (204) according to claim 16, wherein the turbulence element (212) is detachably connected to the feedthrough plate (248). [18] The water pump (204) of claim 16, wherein the inner channel (514) has a variable inner channel depth and the outer channel (530) has a variable outer channel depth. [19] The water pump (204) of claim 16, wherein the turbulence element is a first turbulence element (702), the inner channel is a first inner channel (710) having a first inner diameter (714) and a first outer diameter (718), and the water pump (204) further comprises a second turbulence element (706) spaced from the first turbulence element (702), the second turbulence element (706) arranged to cooperate with the seal assembly (206) to define a second inner channel (722), the second inner channel (722) having a second inner diameter (726) substantially equal to the first inner diameter (714) and a second outer diameter (730) substantially equal to the first outer diameter (718).

Images