阅读说明：本技术 用于泵的动态润滑 (Dynamic lubrication for pumps ) 是由 格斯·亚历山大 理查德·J·吉尔帕特里克 于 2020-11-25 设计创作，主要内容包括：一种泵,包括凸轮盘和用于旋转地驱动所述凸轮盘的输入轴。泵壳体至少部分地围绕所述凸轮盘,并且限定围绕所述凸轮盘的至少一部分的凸轮盘储油器。轴承支撑件被至少部分地设置在所述凸轮盘储油器内。所述轴承支撑件限定至少部分地围绕所述输入轴的一部分的轴承储油器。至少一个通道在所述轴承储油器与所述凸轮盘储油器之间延伸。施加于所述凸轮盘储油器内的油的动态运动促进油从所述凸轮盘储油器迁移通过至少部分地由所述轴承支撑件支撑的轴承进入所述轴承储油器中、以及通过所述至少一个通道进入所述凸轮盘储油器中。(A pump includes a cam plate and an input shaft for rotationally driving the cam plate. A pump housing at least partially surrounds the cam plate and defines a cam plate reservoir surrounding at least a portion of the cam plate. A bearing support is at least partially disposed within the cam plate reservoir. The bearing support defines a bearing reservoir at least partially surrounding a portion of the input shaft. At least one passage extends between the bearing reservoir and the cam plate reservoir. Dynamic movement of oil applied within the cam plate reservoir promotes migration of oil from the cam plate reservoir through a bearing at least partially supported by the bearing support into the bearing reservoir and through the at least one passage into the cam plate reservoir.)

1. An axial cam piston pump comprising:

a cam plate;

an input shaft for rotationally driving the cam plate;

a pump housing at least partially surrounding the cam plate and defining a cam plate reservoir surrounding at least a portion of the cam plate;

a bearing support disposed at least partially within the cam plate reservoir, the bearing support defining a bearing reservoir at least partially surrounding a portion of the input shaft; and

at least one passage extending between the bearing reservoir and the cam plate reservoir, the at least one passage configured such that dynamic movement of oil applied within the cam plate reservoir promotes migration of oil from the cam plate reservoir, through a bearing at least partially supported by the bearing support, into the bearing reservoir, and through the at least one passage into the cam plate reservoir.

2. The axial cam piston pump of claim 1, further comprising at least one piston reciprocally driven by rotation of the cam plate for pumping fluid.

3. The axial cam piston pump of claim 1, wherein the cam plate includes one or more features that facilitate imparting dynamic motion to oil within the cam plate reservoir as a result of rotation of the cam plate.

4. The axial cam piston pump of claim 3, wherein the one or more features include one or more of a recess in an outer surface of the cam plate, a fin on the outer surface of the cam plate, a channel through at least a portion of the cam plate, a protrusion from a portion of the outer surface of the cam plate.

5. The axial cam piston pump of claim 1, wherein the cam plate reservoir has a generally cylindrical configuration.

6. The axial cam piston pump of claim 1, wherein at least a portion of the bearing support within the cam plate reservoir has a generally cylindrical outer configuration.

7. The axial cam piston pump of claim 1, wherein the bearing reservoir has a generally cylindrical configuration.

8. The axial cam piston pump of claim 1 wherein the bearing reservoir is at least partially defined by an input shaft seal spaced from the bearing, and wherein the at least one passage extends between the bearing reservoir and the cam plate reservoir in a portion of the bearing support between the bearing and the input shaft seal.

9. The axial cam piston pump of claim 1, wherein the bearing supports at least a portion of the input shaft.

10. The axial cam piston pump of claim 9, wherein the bearing is a thrust bearing configured to support axial thrust loads exerted on the cam plate.

11. The axial cam piston pump of claim 1, wherein the dynamic motion imparted to the oil comprises rotational motion of the oil within the cam plate reservoir.

12. The axial cam piston pump of claim 1, wherein the at least one passage is oriented at a non-radial angle relative to a longitudinal axis of the input shaft.

13. The axial cam piston pump of claim 12, wherein the dynamic motion imparted to the oil within the cam plate reservoir includes rotational motion of the oil within the cam plate reservoir, and wherein the at least one passage is oriented at an angle to the direction of rotational motion of the oil within the cam plate reservoir.

14. The axial cam piston pump of claim 11, wherein the outer surface of the bearing support includes a flow disrupter located at a leading edge of an opening of the at least one channel on the outer surface of the bearing support relative to a direction of rotation of the oil.

15. The axial cam piston pump of claim 14, wherein the flow disrupter comprises one or more of bumps, lips, and protrusions.

16. The axial cam piston pump of claim 1, wherein rotation of the input shaft within the bearing reservoir imparts a dynamic rotational motion to oil within the bearing reservoir.

17. The axial cam piston pump of claim 1, further comprising an oil fill passage into the cam plate oil reservoir, wherein the oil fill passage is oriented at a non-radial angle relative to an axis of rotation of the cam plate.

18. An axial cam piston pump comprising:

a cam plate configured to be rotationally driven by an input shaft and reciprocally drive one or more piston pumps;

a housing defining a cam plate reservoir, the cam plate being disposed within the cam plate reservoir;

a bearing support holding a thrust bearing proximate the cam plate and including an input shaft seal spaced from the bearing to define a bearing reservoir between the thrust bearing and the input shaft seal, the bearing support being disposed at least partially within the cam plate reservoir and including one or more passages extending between the bearing reservoir and the cam plate reservoir, the one or more passages being oriented at a non-radial angle relative to an axis of a longitudinal axis of the input shaft.

19. The axial cam piston pump of claim 18, wherein the one or more piston pumps are radially spaced about an axis of rotation of the cam plate.

20. The axial cam piston pump of claim 18, wherein the exterior of the bearing support includes a flow disrupter located proximate an opening of the one or more channels.

21. The axial cam piston pump of claim 20, wherein the flow disrupter comprises one or more of a lip and a tab protruding from an exterior of the bearing support.

22. A pump, comprising:

a housing defining a main reservoir, at least one rotating component of the pump being at least partially disposed within the main reservoir; and

a bearing support disposed at least partially within the main reservoir, the bearing support retaining a bearing proximate to the rotating component and at least partially defining a bearing reservoir, the bearing support including one or more passages extending between the bearing reservoir and the main reservoir, the one or more passages each being oriented at a non-radial angle relative to a longitudinal axis of the bearing;

wherein dynamic rotational motion imparted to oil within the main reservoir by rotation of the at least one rotating component causes oil to migrate through the bearing into the bearing reservoir and from the bearing reservoir back into the main reservoir through at least one of the one or more passages.

23. The pump of claim 22, further comprising one or more of a lip and a tab on an exterior of the bearing support proximate an opening associated with at least one of the one or more channels.

24. The pump of claim 22, wherein the at least one rotating component comprises an input shaft.

25. The pump of claim 24, wherein the bearing at least partially supports the input shaft.

26. The pump of claim 22, further comprising an oil seal at least partially supported by the bearing support and spaced apart from the bearing to at least partially define the bearing reservoir.

Technical Field

The present invention relates generally to pumps and more particularly to dynamic lubrication for pumps.

Background

Many domestic and commercial water applications may require relatively high pressures, which may exceed the capabilities of residential and/or municipal water distribution and supply systems. For example, heavy duty cleaning applications may benefit from increased spray pressures that are greater than those available from ordinary residential and/or municipal water distribution and supply systems. In some cases, various nozzles may be used to restrict the flow of water to provide increased pressure to the resulting water stream. However, many tasks may benefit from even greater pressures that may be achieved with a common pressure nozzle that may be attached to a hose. In such ambient pressures, gaskets may be used, where a power pump may be employed to increase the pressure, which is thus significantly higher than the pressure that is readily available using a hose attachment. Such elevated pressures may increase the efficiency and/or effectiveness of some cleaning and spraying tasks.

Disclosure of Invention

According to an embodiment, an axial cam-piston pump may comprise a cam plate and an input shaft for rotationally driving said cam plate. The axial lobe pump also includes a pump housing at least partially surrounding the cam plate and defining a cam plate reservoir surrounding at least a portion of the cam plate. A bearing support may be at least partially disposed within the cam plate reservoir. The bearing support may define a bearing reservoir at least partially surrounding a portion of the input shaft. The axial cam-piston pump may further comprise at least one channel extending between the bearing reservoir and the cam plate reservoir. The at least one passage may be configured such that dynamic movement of oil imparted into the cam plate reservoir promotes migration of oil from the cam plate reservoir, through a bearing at least partially supported by the bearing support, into the bearing reservoir, and through the at least one passage into the cam plate reservoir.

One or more of the following features may be included. The axial cam-piston pump may also include at least one piston reciprocally driven by rotation of the cam plate to pump fluid. The cam plate may include one or more features that facilitate dynamic motion imparted to oil within the cam plate reservoir caused by rotation of the cam plate. The one or more features may include one or more of a recess in an outer surface of the cam plate, a fin on the outer surface of the cam plate, a channel through at least a portion of the cam plate, a protrusion protruding from a portion of the outer surface of the cam plate. The cam plate reservoir may have a generally cylindrical configuration. At least a portion of the bearing support within the cam plate reservoir may have a generally cylindrical outer configuration. The bearing reservoir may have a generally cylindrical configuration.

The bearing reservoir may be at least partially defined by an input shaft seal spaced from the bearing. The at least one passage may extend between the bearing reservoir and the cam plate reservoir in a portion of the bearing support between the bearing and the input shaft seal. The bearing may support at least a portion of the input shaft. The bearing may comprise a thrust bearing configured to support axial thrust loads exerted on the cam plate.

The dynamic motion imparted to the oil may include rotational motion of the oil within the cam plate reservoir. The at least one channel may be oriented at a non-radial angle relative to a longitudinal axis of the input shaft. The dynamic motion imparted to the oil within the cam plate reservoir may include rotational motion of the oil within the cam plate reservoir, and the at least one passage may be oriented at an angle to the direction of rotational motion of the oil within the cam plate reservoir. The outer surface of the bearing support may comprise a flow disrupter located at a leading edge of the opening of the at least one channel on the outer surface of the bearing support relative to the direction of rotation of the oil. The flow disrupter may comprise one or more of a nub, lip and protrusion. Rotation of the input shaft within the bearing reservoir may impart dynamic rotational motion to the oil within the bearing reservoir.

The axial cam-piston pump may further comprise an oil filling channel into the cam plate oil reservoir. The oil fill passage may be oriented at a non-radial angle relative to the axis of rotation of the cam plate.

According to another embodiment, an axial cam piston pump may include a cam plate configured to be rotationally driven by an input shaft and reciprocally drive one or more piston pumps. The axial cam-piston pump may include a housing defining a cam plate reservoir. The cam plate may be disposed within the cam plate reservoir. Bearing supports may hold thrust bearings adjacent to the cam plate. The bearing support may include an input shaft seal spaced from the bearing to define a bearing reservoir located between the thrust bearing and the input shaft seal. The bearing support may be at least partially disposed within the cam plate reservoir. The bearing support may include one or more passages extending between the bearing reservoir and the cam plate reservoir. The one or more channels may be oriented at a non-radial angle relative to a longitudinal axis of the input shaft.

One or more of the following features may be included. The one or more piston pumps may be radially spaced about the axis of rotation of the cam plate. The exterior of the bearing support may include a flow disruptor located near the opening of the one or more channels. The flow disrupter may comprise one or more of a lip and a nub protruding from an exterior of the bearing support.

According to yet another embodiment, the pump may include a housing defining a main reservoir. At least one rotating component of the pump may be at least partially disposed within the main reservoir. The pump may also include a bearing support at least partially disposed within the main reservoir. The bearing support may hold a bearing close to the rotating member. The bearing support may at least partially define a bearing reservoir. The bearing support may include one or more passages extending between the bearing reservoir and the main reservoir. Each of the one or more channels may be oriented at a non-radial angle relative to a longitudinal axis of the bearing. Dynamic rotational motion imparted to oil within the main reservoir by rotation of the at least one rotating component may cause oil to migrate through the bearing into the bearing reservoir and from the bearing reservoir back into the main reservoir through at least one of the one or more passages.

One or more of the following features may be included. The pump may include one or more of a lip and a tab on an exterior of the bearing support proximate an opening associated with at least one of the one or more channels. The at least one rotating member may comprise an input shaft. The bearing may at least partially support the input shaft. The pump may also include an oil seal at least partially supported by the bearing support and spaced apart from the bearing to at least partially define the bearing reservoir.

Drawings

FIG. 1 shows an illustrative example consistent with an exemplary embodiment;

FIG. 2 shows the pump of FIG. 1 from an alternative advantageous aspect;

FIG. 3 shows a cross-sectional view of an illustrative example pump consistent with an example embodiment;

FIG. 4 shows an illustrative example embodiment of the pump of FIG. 3 with the pump housing removed;

FIG. 5 shows an illustrative example embodiment of a bearing support consistent with an example embodiment;

FIG. 6 shows a cross-sectional view of an illustrative example bearing support, cam plate, and input shaft consistent with an example embodiment;

FIG. 7 shows a cross-sectional view of an illustrative example bearing support consistent with an example embodiment;

FIG. 8 shows a cross-sectional view of an illustrative example pump through a bearing reservoir and one or more passages consistent with an example embodiment;

FIG. 9 shows an illustrative example cam plate and input shaft consistent with an example embodiment;

FIG. 10 schematically shows an illustrative example bearing support and bearing consistent with an example embodiment;

FIG. 11 schematically shows an illustrative example arrangement of one or more channels of an example bearing support consistent with an example embodiment;

12A-12C schematically illustrate illustrative examples of flow disruptors consistent with some example embodiments.

Fig. 13A and 13B show an illustrative example pump mounting flange and engine mounting flange, respectively, consistent with an example embodiment.

Detailed Description

In general, the present disclosure may provide a pump configured to dynamically lubricate one or more bearings or other features associated with the pump. That is, during operation, movement of one or more components of the pump may impart dynamic motion to oil within a main oil reservoir (e.g., which may be used for overall lubrication of various components of the pump). The dynamic motion of oil located within the main reservoir may cause and/or promote migration of oil through the bearing and back into the main reservoir. A dynamic lubrication system consistent with the present disclosure may be used in conjunction with a wide variety of pumps and/or any mechanism that includes a rotating component that is at least partially disposed within an oil reservoir and that may impart dynamic motion to oil within the oil reservoir to cause, facilitate, assist, or encourage dynamic flow of the oil through a bearing. Examples of pumps that may be used with the present disclosure may include, but are not limited to, axial cam piston pumps, crank driven pumps, centrifugal pumps, lobe pumps, gear pumps, and the like. For example, in one illustrative embodiment, the pump may comprise an axial cam piston pump, which may be used in conjunction with a pressure washer, for example, or may be used in conjunction with other pumping applications. The cam plate of the axial piston pump may be rotationally driven by an input shaft, which in turn may be driven by a suitable engine (e.g., a gasoline engine, a diesel engine, a propane engine, etc.) or motor, for example. The input shaft (and/or the cam plate itself) may be supported by main bearings, which may for example support the input shaft and/or the cam plate for rotation and/or support any thrust loads borne by the cam plate. At least a portion of the cam plate and/or the input shaft may be located at least partially (and/or entirely) within the main oil reservoir and may be in contact with oil within the main oil reservoir. During operation of the pump, the cam plate and the input shaft may be rotated (e.g., to cause a pumping action). Rotation of the cam plate and/or the input shaft may impart dynamic motion to the oil when in contact with the oil within the main reservoir. The dynamic motion may be caused by, for example, frictional interaction between the cam plate and the oil. The dynamic motion imparted to the oil may include rotational motion of oil within the main reservoir. The bearing may be retained and/or supported by a bearing support, which may be at least partially disposed within the main oil reservoir. The bearing support may include one or more passages located behind the bearing (e.g., distal with respect to the cam plate), which may be arranged to allow oil to migrate from the main oil reservoir through the bearing and out of the bearing support through the one or more passages. In this way, the dynamic motion of oil within the main reservoir may cause and/or promote oil migration through the bearing.

Consistent with such a configuration, oil may constantly migrate and/or flow through the bearing during operation. Thus, there may not be a generally fixed volume of oil within the bearing, such as is the case with conventional systems where there may be limited exchange of oil within the bearing with oil in the main oil reservoir. Thus, in some embodiments, consistent with the present disclosure, the constant migration of oil through the bearing may serve to renew the oil within the bearing space. In this way, the oil within the bearing may be less susceptible to overheating (e.g., due to heat conducted from the engine via the input shaft and/or pump housing, and/or due to frictional heat accumulated within the bearing itself). This may reduce oil decomposition, reduce degradation of the resulting lubrication characteristics, and/or reduce the accumulation of decomposition byproducts (such as carbon, etc.). Additionally, during operation of the pump, the constant migration of oil through the bearing may help transfer any decomposition byproducts from the bearing and into the main reservoir. In this way, the decomposition byproducts may be diluted within the volume of oil within the main oil reservoir, which may reduce and/or delay any damage caused by the decomposition byproducts, for example, and/or may allow for at least partial removal of the decomposition byproducts through periodic maintenance of the pump, which may include replacing oil within the main oil reservoir. Various additional and/or alternative features may be implemented consistent with the present disclosure.

Referring to fig. 1 and 2, an illustrative example embodiment of a pump 10 is generally shown. Consistent with the exemplary embodiment illustrated, the pump 10 may comprise an axial cam piston pump. For example, referring also to fig. 3 and 4, the pump 10 may include a cam plate 12 and an input shaft 14 for rotationally driving the cam plate 12. The input shaft 14 may be configured to couple with an internal combustion engine (e.g., a gasoline engine, a diesel engine, a propane engine, etc.), a motor, or other suitable power device for rotationally driving the input shaft 14. In various embodiments, the input shaft 14 may be keyed (e.g., as shown in fig. 1) to rotationally couple with an engine or motor. It will be appreciated that other arrangements for rotational coupling (e.g., splines, bolted flange connections, friction fits, etc.) may also be used. Additionally, the input shaft 14 may be configured to couple with the cam plate 12 such that when the input shaft 14 is rotationally driven by the engine, motor, etc., the input shaft 14 may rotationally drive the cam plate 12. For example, the cam plate 12 and the input shaft 14 may be integrally formed, may be coupled via a keyed coupling, a splined coupling, a friction fit, and/or any other suitable coupling.

As shown and as is generally known, the cam plate 12 may be oriented at an angle relative to the longitudinal axis of the input shaft 14 (and wherein the angle is relative to the rotational axis of the cam plate 12 and drive shaft 14). The angle of the cam plate 12 relative to the longitudinal axis of the input shaft 14 may be any suitable angle greater than perpendicular and less than parallel. As shown, the pump 10 may also include one or more pistons (e.g., pistons 16a, 16b, and additional pistons not readily visible in fig. 3 and 4) that may be radially spaced about the longitudinal axis of the input shaft 14 (and wherein also are radially spaced about the axis of rotation of the cam plate 12). While the illustrative example embodiment is generally shown and described as including three pistons, it will be appreciated that a suitable pump may include one or more pistons depending on various design considerations. In line with the above, the angular arrangement of the cam plate 12 relative to the longitudinal axis of the input shaft 14 may be: such that rotation of the cam plate 12 (as a result of rotation of the input shaft 14) may reciprocally drive the one or more pistons (e.g., within respective bores or cylinders) to pump fluid (in association with various additional components such as inlet and/or outlet valves as is commonly known). In some embodiments, the angle of the cam plate 12 may be variable, i.e. may be changeable such that the axial stroke of the one or more pistons may be varied (e.g. this may vary the volume pumped by each piston for each revolution of the cam plate). In some embodiments, the cam plate 12 may comprise a multi-component assembly, for example, including a cam body 18 and a bearing surface 20 (e.g., the cam body 18 and bearing surface 20 may be coupled with the cam body 18 via a bearing, such as a ball bearing, as generally shown in fig. 3). Such an arrangement, although perhaps not necessary, may reduce the frictional interaction between the cam plate 12 and the pistons.

Continuing with the illustrative embodiment consistent with the present disclosure, the pump 10 may further include a pump housing 24. The pump housing 24 may at least partially surround the cam plate 12 and may define a cam plate reservoir 26 that surrounds at least a portion of the cam plate 12. The pump housing 24 may also generally surround one or more pistons 16a, 16b, as shown. The cam plate reservoir 26 may generally be configured to contain lubrication oil for the pump 10, for example, to provide lubrication for one or more of the cam plate/piston interaction and the piston/bearing interaction. Additionally, the oil may provide some degree of cooling/heat transfer to the pump 10. In some embodiments, the cam plate reservoir 26 may have a generally cylindrical configuration. That is, for example, in some embodiments, the pump housing 24 may have an inner surface with a generally circular cross-sectional shape perpendicular to the axis of rotation of the cam plate 12, at least in the region of the cam plate 12. In some embodiments, the entire cam plate reservoir may comprise a generally cylindrical configuration. In some embodiments, the cam plate reservoir may have a different configuration away from/different from the area of the cam plate. In the illustrated example embodiment, as shown in fig. 3, the cam plate reservoir 26 may be tapered to some extent in the area of the piston bore, although other configurations may be equivalently used.

The pump 10 may also include a bearing support 28. As shown, for example in fig. 3 and 5-7, the bearing support 28 may be at least partially disposed within the cam plate reservoir 26. In illustrative embodiments consistent with the present disclosure, the bearing support 28 may at least partially support and/or retain a bearing 30. For example, in some embodiments, the bearing support may include a shaft opening 32, and generally, the shaft opening 32 may be configured to receive at least a portion of the input shaft 14 therethrough. In some embodiments consistent with the present disclosure, the bearing 30 may support at least a portion of the input shaft. For example, in the illustrated embodiment, the outer race of the bearing 30 may be disposed in a recess or cap formed in the end of the bearing support 28 proximate the cam plate 12 (e.g., around the perimeter of the shaft opening). In such an embodiment, the outer race of the bearing 30 may be press fit into the recess or cap formed in the shaft opening 32 of the bearing support 28. However, it will be appreciated that other arrangements for supporting and/or retaining the bearing may be used.

As noted above, in some embodiments consistent with the present disclosure, the bearing 30 may support at least a portion of the input shaft 14. For example, as shown in the illustrated exemplary embodiment, the input shaft 14 may extend through the bearing 30 and be at least partially supported by the bearing 30. In some embodiments, the bearing 30 may support at least a portion of the input shaft 14 for rotation. Additionally, in some embodiments, the bearings may include thrust bearings that may be configured to support axial thrust loads applied to the cam plate 12. For example, during operation of the pump 10, the cam plate 12 may reciprocally drive one or more pistons (e.g., pistons 16a, 16b, etc.), which may result in thrust loads being applied to the cam plate 12 generally axially with respect to the axis of rotation of the cam plate 12. Consistent with such embodiments, in addition to supporting the input shaft 14 (and thus the cam plate 12) for rotation, the bearings 30 may also support axial thrust loads experienced by the cam plate 12 (e.g., support the cam plate against axial movement caused by the thrust loads experienced). Consistent with such exemplary embodiments, the bearing 30 may comprise a suitable bearing, such as a tapered roller bearing, a tapered needle bearing, and/or any other suitable bearing configuration.

Consistent with some embodiments of the present disclosure, and with particular reference to fig. 6, the bearing support 28 may define a bearing reservoir 34 at least partially surrounding a portion of the input shaft 14. In the illustrated example embodiment, the bearing reservoir 34 may be at least partially defined by an input shaft seal 36, and the input shaft seal 36 may be spaced apart from the bearing 30. For example, consistent with typical pump configurations, a primary seal may generally be disposed proximate to the bearing, e.g., to prevent oil from migrating from the pump, through the bearing, and leaking from the pump. In some conventional configurations, the seal may even contact a rear portion of the bearing (e.g., the side of the bearing opposite the cam plate). Consistent with the present disclosure, in some embodiments, the input shaft seal 36 may be spaced apart from the bearing 30 to define the bearing reservoir 34 between the bearing 30 and the input shaft seal 36. In some embodiments, the area of the bearing support 28 between the bearing 30 and the input shaft seal 36 may be enlarged to increase the size of the bearing reservoir 34 (e.g., by providing more play, or spacing between the inner portion of the bearing support defining the bearing reservoir and the input shaft), however such enlargement is not required.

Consistent with the present disclosure, the bearings 30 may be lubricated, at least in part, by oil from the cam plate reservoir 26. For example, as shown generally in fig. 3, for example, the bearing 30 may be exposed to the cam plate reservoir 26. Consistent with conventional pump configurations, the main seal may be generally positioned proximate to the bearing. In this way, there may typically be minimal exchange between the oil in the bearings of the pump and the oil in the oil reservoir. Additionally, the oil within the bearing may be subjected to heat (e.g., the heat may be transferred from an engine driving the pump), frictional heating due to rotation of the input shaft, and/or shearing of the oil in the bearing due to rotation of the input shaft and/or the bearing itself. Such heating and/or shearing may result in degradation and/or decomposition of the oil in the bearing, which may cause, for example, the oil in the bearing to accumulate decomposed components of the oil (e.g., carbon, metallic wear components, and/or other decomposed components), which may result in thickening (e.g., coking the oil), and/or a reduction in the lubricating properties of the oil within the bearing, as well as chemical attack of the oil on some materials, such as the seal (e.g., caused by the oil being heated, and/or the presence of decomposed components). Consistent with the present disclosure, and as will be discussed in greater detail below, the dynamic motion imparted to the oil, and the configuration of the pump 10, may facilitate and/or induce oil migration through the bearing 30, which may reduce heat accumulation of the oil in the bearing, and/or allow decomposition components to be at least partially removed from the bearing. Thus, the oil in the bearings can be replenished and/or replaced with new oil from the cam plate reservoir 26. Replenishment and/or replacement of oil in the bearings may reduce heat build-up in the bearings, and/or remove at least a portion of the decomposition components from the bearings, for example, which may allow the decomposition components to be diluted in the volume of oil in the cam plate reservoir 26 (e.g., in some embodiments, which may also allow for removal of at least a portion of the decomposition components diluted in the volume of oil within the cam plate reservoir when the oil in the cam plate reservoir changes during maintenance or servicing of the pump).

Consistent with the above, in some embodiments, the pump 10 may include at least one passage (e.g., passages 38a, 38b, 38c, 38d) extending between the bearing reservoir 34 and the cam plate reservoir 26, for example, as shown in fig. 8. Although the illustrated exemplary embodiment shows four channels, a greater or lesser number of channels (e.g., one or more channels) may be included. As shown, consistent with some embodiments of the present disclosure, the at least one passage may extend between the bearing reservoir 34 and the cam plate reservoir 26 in a portion of the bearing support 28 between the bearing 30 and the input shaft seal 36. Consistent with the present disclosure, the at least one passage (e.g., passages 38a, 38b, 38c, 38d) may be configured such that dynamic movement of oil applied within the cam plate reservoir 26 facilitates migration of oil from the cam plate reservoir 26, through the bearing 30 at least partially supported by the bearing support 28, into the bearing reservoir 34, and through the at least one passage 38a, 38b, 38c, 38d into the cam plate reservoir 26. In this way, the bearings may be subjected to dynamic lubrication, wherein oil from the cam plate reservoir 26 passes through the bearings into the bearing reservoir 34 and back into the cam plate reservoir 26. As generally discussed above, dynamic lubrication of the bearings may reduce heat buildup within the bearings, remove decomposition and/or metal wear components within the bearings, and/or replace oil within the bearings that may have degraded lubrication capabilities with fresh oil from the cam plate reservoir.

Continuing with the above, the dynamic motion of the oil within the cam plate reservoir 26 may be due at least in part to the rotation of the cam plate 12 within the cam plate reservoir 26. For example, the cam plate 12 may be at least partially disposed within oil contained within the cam plate reservoir 26. As the cam plate 12 is rotationally driven during operation of the pump 10, the cam plate 12 may interact with oil within the cam plate oil reservoir 26 and may impart dynamic motion to the oil (e.g., based at least in part on frictional and/or resistive interaction of the cam plate moving within the oil). Consistent with some embodiments, the dynamic motion imparted to the oil by the cam plate 12 may include rotational motion of the oil within the cam plate reservoir 26. For example, the oil may be caused to swirl and/or swirl around the interior of the cam plate reservoir 26 as a result of the rotational energy applied to the oil by the rotating cam plate 12. In such embodiments, the rotation of the oil within the cam plate reservoir may be in the same direction as the rotation of the cam plate 12. It will be appreciated that although the dynamic motion of the oil may include rotational motion, the dynamic motion may include other components as well (e.g., the dynamic motion may not just rotate).

In some embodiments, the cam plate 12 may include one or more features that may facilitate imparting dynamic motion to the oil within the cam plate reservoir 26 caused by rotation of the cam plate 12. For example, referring to fig. 9, the one or more features may include one or more recesses (e.g., recesses 40a, 40b, 40c) in an outer surface of the cam plate 12. Consistent with the illustrated exemplary embodiment, the recesses 40a, 40b, 40c may increase the frictional and/or resistive interaction between the cam plate 12 and the oil, which may facilitate and/or increase the ability, rate, or amount the cam plate 12 may impart dynamic motion to the oil. While three recesses are shown in the illustrated example embodiment, it will be understood that a greater or lesser number of recesses may be used. In addition to/as an alternative to a recess, the cam plate may include other features that may facilitate the application of dynamic motion to the oil by the cam plate, such as, but not limited to, one or more fins located on an outer surface of the cam plate, one or more channels through at least a portion of the cam plate, one or more protrusions from a portion of the outer surface of the cam plate, and the like.

As discussed above, in some embodiments consistent with the present disclosure, at least a portion of the bearing support 28 may be disposed within the cam plate reservoir 26. Additionally, one or more passages (e.g., passages 38a, 38b, 38c, 38d) may extend between the bearing reservoir 34 and the cam plate reservoir 26. Additionally, the dynamic motion imparted to the oil within the cam plate reservoir 26 by the rotation of the cam plate 12 may cause and/or promote migration and/or flow of oil from the cam plate reservoir 26 through the bearing 30 into the bearing reservoir 34, and from the bearing reservoir 34 back into the cam plate reservoir 26 through one or more passages (e.g., passages 38a, 38b, 38c, 38 d).

Without intending to be limited to any particular theory or theory of operation, one mechanism or combination of mechanisms may cause, assist and/or promote dynamic lubrication of the bearing. For example, in some embodiments, the pump 10 may be oriented in a generally horizontal position during operation (i.e., the axis of the input shaft and the axis of rotation of the cam plate may be generally horizontal). It should be noted that the designation "horizontal" position is not intended to limit the operating position of the pump, but rather to deviate from a substantially vertical position, the designation covering deviations from strictly horizontal by up to 45 degrees. Referring also to fig. 10, an illustrative example static oil level 42 (e.g., an oil level when no dynamic motion is applied to the oil) and an illustrative example dynamic oil level 44 (e.g., an oil level when dynamic motion is applied to the oil) are generally shown. It should be understood that the illustrated oil levels are intended to be illustrative and non-limiting. As shown, the dynamic oil level 44 may be at least at a lower level of the bearing 30 (e.g., by reference to a generally horizontal position of the pump). As such, the dynamic oil level 44 may allow oil to migrate from the cam plate reservoir 26 into the bearings 30 during operation of the pump 10 (i.e., when dynamic motion is imparted to the oil). It will be appreciated that the viscous and/or adhesive properties of the oil may cause at least a portion of the oil to be transferred around the diameter of the bearing 30. Additionally, when the pump 10 is oriented such that at least one passage (e.g., passage 38c in fig. 10) is below the dynamic oil level 44, oil entering through the bearing 30 may drain back into the cam plate reservoir 26.

According to additional and/or alternative and non-limiting possible operating mechanisms, the rotational dynamic motion imparted to the oil by the rotating cam plate 12 may impart centrifugal force to the oil, thereby urging at least a portion of the oil against the inner wall of the pump housing 24, defining the cam plate reservoir 26. For example, as the centrifugal force causes the oil to be pushed toward the inner wall of the pump housing 24 and cause the oil to flow longitudinally, the centrifugal force driving the oil toward the inner wall of the pump housing 24 may also result in a longitudinal force being applied to the oil (i.e., a force that is generally parallel to the axis of rotation of the cam plate and thus the axis of rotation of the oil). Since the dynamic oil level 44 of oil within the cam plate reservoir 26 may be at least at the bearings 30, longitudinal forces applied to the oil (e.g., caused at least in part by centrifugal forces applied to the oil) may cause and/or promote migration of the oil through the bearings 30. Oil that migrates through the bearing 30 into the bearing reservoir 34 may exit via one or more passages (e.g., passages 38a, 38b, 38c, 38 d).

Consistent with the possible operating mechanisms above, in some embodiments, the centrifugal force applied to the oil may result in a radially dynamic oil level around at least a portion and/or all of the inner wall of the pump housing 24 (e.g., the dynamic oil level in the pump housing 24 defines the "thickness" of the body of oil around the inner wall of the pump housing 24). In some such embodiments, the entire circumference of the bearing may be covered by oil, and the oil may be pushed around the entire circumference of the bearing due to longitudinal forces applied to the oil as the oil is pushed towards the inner wall of the pump housing by centrifugal forces applied to the oil. In a similar manner as discussed above, oil migrating through the bearing 30 into the bearing reservoir 34 may exit via one or more of the passages (e.g., passages 38a, 38b, 38c, 38 d).

According to an additional and/or alternative mechanism, the rotation and/or swirl of the oil within the cam disc reservoir 26 may rotate around at least a portion of the bearing support 28. In some such embodiments, as shown generally in fig. 5 and 8, at least a portion of the bearing support 28 within the cam plate reservoir 26 may have a generally cylindrical outer configuration. That is, for example, at least a portion of the outer portion of the bearing support may have a generally circular cross-section perpendicular to the axis of rotation of the cam plate 12 (e.g., and thus perpendicular to the axis of rotation of the oil within the cam plate reservoir 26). Consistent with some such embodiments, at least the generally cylindrical outer configuration of the bearing support 28 may exhibit relatively low perturbations in the dynamic motion of the portion of the oil within the cam plate reservoir that flows through the bearing support (e.g., as compared to at least some alternative cross-sectional profiles).

Consistent with the above, in some embodiments, with additional reference to fig. 11, the rotation and/or swirl of oil within the cam plate reservoir 26 may rotate through the respective openings (e.g., openings 46a, 46b shown in fig. 5) of the one or more passages (passages 38a, 38b, 38c, 38 d). In some embodiments, oil spinning through the openings of the one or more passages may create a slip flow, which may, for example, facilitate and/or cause oil to migrate from the bearing reservoir 34 through the one or more passages and back into the cam plate reservoir. In some embodiments, the at least one channel may be oriented at a non-radial angle relative to a longitudinal axis of the input shaft. For example, as shown in fig. 8 and 11, the one or more passages (e.g., passages 38a, 38b, 38c, 38d) may extend through the bearing support 28 at an angle that does not intersect the longitudinal axis of the input shaft 14 and/or the center of the bearing reservoir 34. The orientation of the passages may, but need not, be tangential to the bearing reservoir 34. In some such embodiments, the orientation of the one or more channels may facilitate creating a slipstream through the openings of the one or more channels. As generally discussed above, the dynamic motion imparted to the oil within the cam plate reservoir 26 may include rotational motion of the oil within the cam plate reservoir 26. In some such embodiments, and with particular reference to fig. 11, the at least one passage may be oriented at an angle to the direction of rotational movement of oil within the cam plate reservoir (indicated by arrow 48 in fig. 11).

Consistent with the above, in some such embodiments, the orientation of the one or more channels may, for example, reduce the occurrence of scooping (scooping) of oil from the cam plate reservoir into the one or more channels. Additionally/alternatively, in some embodiments, the viscous properties of the oil may promote migration of oil through the one or more passages into the cam plate reservoir 26. For example, oil within the one or more passages may be attached to the flow of swirling oil flowing through the respective openings of the one or more passages, and may be drawn from the one or more passages into the cam plate reservoir 26. In some embodiments, oil within the bearing reservoir 34 may be similarly attached to oil within the one or more passages and may be similarly drawn through the one or more passages into the cam plate reservoir 26. Additionally, in some embodiments, drawing oil from the one or more passages and/or the bearing reservoir 34 may create a lower pressure within the bearing reservoir, which may, for example, facilitate, assist and/or cause oil to migrate from the cam plate reservoir 26 through the bearing.

According to additional and/or alternative mechanisms, creating a reduced pressure near each opening of one or more passages by the rotating oil flow in the cam plate reservoir 26 with or without oil within the one or more passages being viscously attached to the oil flow through the respective opening may cause, assist and/or promote oil migration through the bearing 30 into the bearing reservoir 34, and from the bearing reservoir 34 back through the one or more passages into the cam plate reservoir 26. For example, the dynamic flow of oil across the respective openings may induce a reduced pressure in the vicinity of the respective openings individually (and/or in conjunction with other mechanisms). In some such embodiments, the reduced pressure near the respective openings may cause, assist and/or promote migration of oil from the bearing reservoir 34 through the one or more passages and into the cam plate reservoir 26, and cause, assist and/or promote migration of oil from the cam plate reservoir 26 through the bearing 30.

In some embodiments, the outer surface of the bearing support 28 may include a flow disrupter located at a leading edge of the opening of the at least one channel on the outer surface of the bearing support, relative to the direction of rotation of the oil. The flow disrupter may cause and/or help to induce a reduced pressure in the vicinity of the opening of the at least one channel. For example, the flow perturbator may alter the velocity of the rotating oil within the cam plate reservoir as it flows through the opening of the at least one passage. Additionally/alternatively, the flow disruptor may generate vortices and/or turbulence in the rotating oil as it flows through the opening of the at least one channel. Such disturbances in the flow of dynamically spinning oil through the opening of the at least one passage may cause, facilitate and/or help induce a reduced pressure near the opening of the at least one passage, which, as discussed above, may cause, facilitate and/or help oil to migrate from the bearing reservoir 34 through the one or more passages and into the cam plate reservoir 26, and cause, facilitate and/or help oil to migrate from the cam plate reservoir 26 through the bearing 30.

The flow disrupter may comprise one or more of a nub, lip and protrusion. 12A-12C, an illustrative example embodiment of a flow disrupter is shown. Referring to FIG. 12A, a first illustrative example embodiment of a flow perturber 39a is shown having a generally ramp configuration extending from the exterior of the bearing support 28 into the cam plate reservoir 26. Referring to fig. 12B, the second illustrative example embodiment of the flow disruptor 39B is shown as having a generally sloped configuration in which the channel 38a is generally flat near its opening (e.g., as compared to the peak or lip shown with respect to the first illustrative example flow disruptor 39 a). Referring to FIG. 12C, a third illustrative example embodiment of a flow disruptor 39C is shown in a generally ramp configuration with a step near the opening of the channel 38 a.

As shown, and as generally described hereinabove, for generally counterclockwise rotational movement of oil within the cam plate reservoir 26, the flow disrupters (e.g., flow disrupters 39a, 39b, 39c) may be generally positioned to the right hand side of the opening of the passage (e.g., passage 38a) between the bearing reservoir 34 and the cam plate reservoir 26. As generally shown in the figures, each of the flow disrupters 39a, 39b, 39c may create turbulence in the oil flow entering the opening of the passage 38a of the cam plate reservoir 26. The turbulence created by the flow disruptors 39a, 39b, 39C may create a reduced pressure near (e.g., on or above) the opening of the passage 38a, which may cause, promote, and/or assist oil migration from the bearing reservoir 34 through the passage 38a and into the slipstream of dynamically moving oil within the cam plate reservoir 26 (e.g., as generally shown by the arrows in fig. 12A-12C). In some example embodiments, the height of the flow disrupter may be on the order of the diameter of the at least one channel. However, it will be understood that other flow disrupter heights may be equally used.

It will be appreciated that various additional and/or alternative flow perturbator configurations may be used for creating a pressure reduction zone adjacent to and/or over the opening into the one or more passages in the cam plate reservoir. Additionally, it will be appreciated that the relative size and/or proportions of the flow disruptors may vary depending on the configuration of the flow disruptors, the desired pressure reduction, and/or other design criteria. For example, certain flow disrupter configurations may provide the desired performance in different sizes and/or proportions than other flow disrupter configurations. Thus, the illustrated embodiments should not be viewed as limiting the configuration of possible flow disruptors or the size or scale of possible flow disruptors.

Consistent with some embodiments, rotation of the input shaft 14 within the bearing reservoir 34 may impart dynamic rotational motion to the oil within the bearing reservoir 34, for example, in a manner generally similar to that discussed with respect to the cam plate 12 imparting dynamic rotational motion to the oil within the cam plate reservoir 26. In some embodiments, the dynamic rotational motion of oil within the bearing reservoir 34 may at least partially cause, facilitate, and/or facilitate oil migration through the bearing 30, and/or oil migration from the bearing reservoir 34 through the one or more passages and into the cam plate reservoir 26. Still without intending to be limited to a particular mechanism or principle of operation, in a similar manner as discussed above, the dynamic rotation of the oil within the bearing reservoir 34 may impart a centrifugal force to the oil within the bearing reservoir, which may, for example, cause and/or promote oil migration to the walls of the bearing support 28 defining the bearing reservoir 34. Additionally, centrifugal forces on the oil within the bearing reservoir may cause, promote, and/or facilitate oil migration through the one or more channels (e.g., caused at least in part by centrifugal forces on the oil) and into the cam plate reservoir 26. In some such embodiments, the bearing reservoir 34 may have a generally cylindrical configuration, which may facilitate dynamic rotational movement of oil within the bearing reservoir 34, for example. For example, the interior of the bearing reservoir 34 may have a generally circular cross-section perpendicular to the axis of rotation of the input shaft 14 (and, therein, perpendicular to the dynamic rotational motion imparted to the oil within the bearing reservoir 34).

As noted above, in some embodiments, the orientation of the one or more passages may facilitate oil flow within the cam plate reservoir 26 through the respective openings of the one or more passages, e.g., while reducing the incidence and/or amount of oil that may be scooped into the one or more passages. Referring to fig. 11, in some embodiments, the one or more channels may generally sweep in the direction of the dynamic rotation of oil within the bearing reservoir 34. In such embodiments, the angled orientation of the one or more passages may cause, facilitate and/or facilitate oil migration from the bearing reservoir 34 through the one or more passages and into the cam plate reservoir 26. For example, the orientation of the one or more passages may be swept in the direction of dynamic rotation of the oil within the bearing reservoir 34, and the centrifugal forces experienced by the oil as it flows through the internal openings of the one or more passages may cause, promote, and/or facilitate migration of oil through the one or more passages to the cam plate reservoir 26. Additionally and/or alternatively, the orientation of the one or more passages may tend to scoop dynamic rotating oil into the bearing reservoir 34 to cause, facilitate, and/or facilitate migration of the oil through the one or more passages to the cam plate reservoir 26.

In some embodiments, the bottom surface of the cam plate 12 may develop some degree of hydraulic pressure relative to the vicinity of the abutment surface of the bearing 30. In some embodiments, positive hydraulic pressure between the bottom surface of the cam plate 12 and the bearing 30 may cause, promote, and/or facilitate oil migration from the cam plate reservoir 26 through the bearing 30.

Consistent with some embodiments, such as shown in fig. 3 and 6 of the illustrated exemplary embodiment, the bearing support 28 may include a seal, such as an O-ring 48, which O-ring 48 may be configured to sealingly engage an inner surface of the pump housing 24. In some such embodiments, the sealing engagement between at least a portion of bearing support 28 and the pump housing 24 may at least partially enclose and/or define the cam plate reservoir 26. It will be understood that other configurations may be equally used.

In some embodiments, the dynamic motion of oil within the cam plate reservoir 26 may additionally and/or alternatively be used to reduce oil leakage and/or migration out of the pump 10 through vent holes or fill caps from the pump 10. For example, referring also to fig. 8, the pump 10 may include an oil fill/vent cap 50, and an oil fill passage 52 into the cam plate reservoir 28. As is generally understood, the oil fill passage 52 and the oil fill/vent cap 52 may allow oil to be added to the pump 10 (e.g., by adding the oil to the cam plate reservoir 26), and/or allow any accumulated pressure within the cam plate reservoir 26 to be vented. Consistent with the illustrated exemplary embodiment, the oil fill passage 52 may be positioned and/or oriented with respect to dynamic motion of oil that may be imparted within the cam plate reservoir 26 to reduce and/or prevent oil leakage and/or migration from the oil fill/vent cover 50. As shown in fig. 8, the oil fill passage 52 may be oriented at a non-radial angle with respect to the axis of rotation of the cam plate. Although not required, in some embodiments, the oil fill passage 52 may be oriented substantially tangential to the interior of the cam plate reservoir 26. Additionally, in some embodiments, the oil fill passage 52 may be located on the pump 10 to be positioned to reside on the retrograde flow of dynamic spin oil within the cam plate reservoir 26, for example, where the dynamic spin oil may rotate generally in a counterclockwise direction in fig. 8. Consistent with the above, the dynamic rotational motion of the oil within the cam plate reservoir 26 may reduce oil migration into the oil fill passage 52 and reduce any resulting leakage of oil from the oil fill/vent cap 50.

With additional reference to fig. 13A and 13B, according to an embodiment, the pump 10 may include a pump body (e.g., shown generally as a pump housing in fig. 1 and 2) and a pump mounting flange 54, the pump mounting flange 54 being configured to mount the pump 10 to an engine flange (e.g., an engine flange 56) that includes four clock-oriented (clocked) mounting holes (e.g., mounting holes 58a, 58B, 58c, 58 d). The pump mounting flange 54 may include a first set of four mounting holes (e.g., 60a, 60B, 60c, 60d) corresponding to the four clock-oriented mounting holes in a first orientation (e.g., the orientation shown in fig. 13B). The pump mounting flange 54 may also include a second set of four mounting holes (62a, 62b, 62c, 62d) corresponding to the four clock-oriented mounting holes in a second orientation (e.g., flipped about the horizontal centerline 64). It should be understood that while the above features are shown in conjunction with the pump 10, mounting arrangements consistent with the present disclosure may be equivalently used in conjunction with pumps that may not include a dynamic lubrication system as described above.

As generally shown above, the four clock-oriented mounting holes (e.g., 58a, 58b, 58c, 58d) define an asymmetric arrangement, for example, about a horizontal centerline 64. For example, while the four clock-oriented mounting holes 58a, 58b, 58c, 58d may be located on a common mounting ring (e.g., a mounting ring that is concentric about an output shaft of a motor associated with the engine mounting flange V), two of the four clock-oriented mounting holes (e.g., mounting holes 58a, 58b) have a first angular spacing relative to a centerline (e.g., vertical centerline 68) of the mounting ring and two of the four clock-oriented mounting holes (e.g., mounting holes 58c, 58d) have a second angular spacing relative to the centerline 68 of the mounting ring 66.

For example, as shown in the illustrated embodiment of fig. 13B, the first angular interval may be different than the second angular interval. In an example embodiment, the first angular interval may be about 30 degrees, and the second angular interval may be about 45 degrees. Consistent with the above, the first set of mounting holes 60a, 60b, 60c, 60d and the second set of mounting holes 62a, 62b, 62c, 62d may provide a pattern that is symmetrical across a center line of an input shaft (not shown) of the pump. For example, the first and second sets of mounting holes may be symmetrical across the horizontal centerline 70 and/or the vertical centerline 72.

Consistent with the above arrangement, the engine mounting flange may be clock-oriented (e.g., asymmetric), for example, to implement a particular mounting location (and/or to prevent incorrect mounting arrangements). However, depending on the engine configuration, (e.g., positioning of intake and exhaust components, design preferences, etc.), the clock-oriented mounting holes may generally have one of two relationships with respect to the upward direction of the engine (e.g., the intended operating orientation of the engine). In some embodiments, the pump may require a particular orientation for proper operation, and as such, the pump may not be suitable for use with some engine configurations (e.g., where the engine mounting flange may be clocked in an orientation designed to be the opposite of that required for proper operation of the pump). For example, the pump may include features that may require a particular orientation for proper and/or intended operation of the pump, such as oil through holes (e.g., pump housing vent holes), drain holes, and the like. Consistent with embodiments of the present disclosure, the pump mounting flange 54 may provide a symmetrical bolt hole arrangement (e.g., achieved by two sets of four mounting holes), which may allow the pump to be mounted to an engine having either of two mutually exclusive clocking orientations. In this way, the mounting flange consistent with embodiments of the present disclosure may allow for greater versatility in power plant selection for driving the pump, as either of the two conventional clocking orientations of the engine mounting flange may be used while still maintaining the correct operating orientation of the pump.

While the present disclosure has been generally described in the context of a pump assembly for a pressure gasket, such description is also presented for purposes of illustration. It will be appreciated that a pump assembly consistent with the present disclosure may be used for various purposes. As such, the present disclosure is considered broadly directed to any pumping application.

Various features have been described herein. However, it will be understood that various additional features and structures may be implemented in connection with pumps according to the present disclosure. Furthermore, additional features and details may be shown in the drawings that may not be explicitly described in the detailed description. However, such features and details are to be understood as being included within the scope of the present disclosure. In addition, the various features described herein can be implemented in various combinations and subcombinations, including fewer than all of the described features, and/or combinations of some or all of the described features in combination with additional features not specifically recited in the present disclosure. As such, the features and attributes described herein should not be viewed as limiting on the present disclosure.