Air compressor including a disk oil slinger assembly

Abstract

A “splash” lubrication system having an oil slinger capable of providing an increased flow rate of lubricating and cooling oil to lubricated components of the system compared to conventional dip stick oil slingers while reducing oil atomization and oil loss through the crankcase vent is disclosed. In embodiments of the invention, the oil slinger is comprised of a disk coupled to the crankshaft assembly of a direct drive oil-lube air compressor. The air compressor includes a universal electric motor which drives the crankshaft assembly, thereby causing the crankshaft assembly to rotate, which in turn, rotates the disk for splashing lubricating oil from the crankcase's oil sump onto the moving parts of the air compressor being lubricated by the lubricating system.

Description

FIELD OF THE INVENTION

The present invention generally relates to the field of oil lubrication devices for air compressors, and more particularly to an air compressor including a disk oil slinger suitable for use in oil lubricated air compressors.

BACKGROUND OF THE INVENTION

Typically, lower cost oil lubricated air compressors have employed a “splash” lubrication system to distribute oil from the oil sump to the mechanical bearings, seals, valves, pistons and other parts that require lubrication and oil cooling. A small protruding piece of material or “dip stick” is attached to one or more of the moving components such that during each revolution of the crankshaft, the dip stick dips into the oil sump at sufficient velocity to cause oil to splash onto the components requiring lubrication. The size, shape and velocity of the dip stick must be engineered to assure sufficient lubrication and oil cooling for all components while minimizing atomization of the oil in the crankcase so as to reduce oil loss through the crankcase vent. A higher velocity or larger profile dip stick will improve lubrication and oil cooling but will increase oil atomization and oil loss through the crankcase vent. A less aggressive dipstick velocity or profile will reduce lubrication and oil cooling but also reduce oil loss through the vent. These conflicting phenomena require designers to compromise their design by reducing the positive benefits of lubrication and oil cooling in order to reduce the negative effects of oil loss.

Another problem with such traditional splash oil lubrication systems is that a number of the air compressors in which such systems are used are portable and are regularly moved by hand from one work site to another. If such portable air compressors are not properly leveled prior to operation, the dip stick splash lubricator may not reach the oil sump causing a lack of needed lubrication and cooling, possibly leading to subsequent component failure.

Consequently, it would be advantageous to provide a “splash” lubrication system designed to increase the flow rate of lubricating and cooling oil to lubricated components of an air compressor while reducing oil atomization and oil loss through the crankcase vent. Further, it would be desirable to provide such a lubrication system that is capable of functioning properly while the crankcase is tilted, providing an increased tolerance of operation on non-level surfaces. Further it would be desirable to provide a lubrication system for implementation within an air compressor having a universal motor, said lubrication system providing improved lubrication for the universal motor, which typically operates at higher rates of speed than other conventional air compressor motors.

SUMMARY OF THE INVENTION

Accordingly, the present invention is directed to a “splash” lubrication system having an oil slinger capable of providing an increased flow rate of lubricating and cooling oil to lubricated components of an air compressor compared to conventional dip stick oil slingers, while reducing oil atomization and oil loss through the crankcase vent. In embodiments of the invention, the oil slinger is comprised of a disk coupled to the crankshaft assembly of the air compressor being lubricated, so that rotation of the crankshaft assembly rotates the disk for splashing lubricating oil from the crankcase's oil sump onto components of the air compressor. Preferably, at least a portion of the oil slinger is continuously submerged in the lubricating oil contained in the oil sump as it is rotated by the crankshaft assembly, thereby decreasing atomization of oil from the oil sump. Further, the oil slinger may be designed to remain at least partially submerged in the oil sump even if the crankcase is tilted providing increased tolerance of operation on non-level surfaces.

In one embodiment the lubrication system may be implemented in an air compressor having two or more cylinder/piston assemblies. In such embodiments, the cylinders of the air compressor are oriented (e.g., may overlap) so that a single oil slinger may provide lubrication to both assemblies.

In a further embodiment the lubrication system may be implemented in an oil-lube direct drive air compressor having a universal motor. The lubrication system of the present invention providing an increased level of lubrication for meeting the demands of a universal motor, which typically operates at higher rates of speed than a conventional air compressor motor.

It is to be understood that both the forgoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention as claimed. The accompanying drawings, which are incorporated in and constitute a part of the specification, illustrate an embodiment of the invention and together with the general description, serve to explain the principles of the invention.

BRIEF DESCRIPTION OF THE DRAWINGS

The numerous advantages of the present invention may be better understood by those skilled in the art by reference to the accompanying figures in which:

FIG. 1 is an isometric view illustrating a lubrication system in accordance with an exemplary embodiment of the present invention;

FIG. 2 is a side elevational view illustrating the oil slinger of the lubrication system shown in FIG. 1;

FIGS. 3 and 4 are side elevational views illustrating tilting of the crankcase;

FIG. 5 is an isometric view illustrating a shaped disk oil slinger having edge and/or surface features in accordance with an exemplary embodiment of the present invention;

FIG. 6 is an isometric view illustrating an auger oil slinger in accordance with an exemplary embodiment of the present invention;

FIG. 7 is an isometric view illustrating an oil slinger in accordance with an exemplary embodiment of the present invention wherein the oil slinger is not a continuous disk;

FIG. 8 is a partial cross-sectional side elevational view illustrating an air compressor having two cylinder/piston assemblies, wherein the air compressor employs the lubrication system of the present invention;

FIG. 9 is an isometric view of a belt drive air compressor assembly including the lubrication system of the present invention;

FIG. 10 is a cross-sectional view of the lubrication system of the air compressor assembly shown in FIG. 10;

FIG. 11 is an isometric view of a direct drive air compressor assembly including the lubrication system of the present invention; and,

FIG. 12 is a cross-sectional view of the lubrication system of the air compressor assembly shown in FIG. 11.

DETAILED DESCRIPTION OF THE INVENTION

Reference will now be made in detail to the presently preferred embodiments of the invention, examples of which are illustrated in the accompanying drawings.

Referring now to FIGS. 1, 2, 3 and 4, an exemplary “splash” lubrication system suitable for providing lubrication to the moving components of an air compressor in accordance with the present invention is described. The lubrication system 100 includes an oil sump 102 formed in the crankcase 104 of the air compressor 106 in which the lubrication system 100 is employed and an oil slinger 108 coupled to the air compressor's crankshaft assembly 110.

In one embodiment, the oil slinger 108 is comprised of a continuous disk 112 attached to the crankshaft assembly 110. Rotation of the crankshaft assembly 110 rotates the disk for splashing lubricating oil 114 from the oil sump 102 onto components of the air compressor 106 being lubricated (e.g., crankshaft assembly 110, journal 116, piston 118, cylinder wall 120, and the like). Preferably, the disk 112 is positioned along the crankshaft immediately adjacent to journal 116 so that oil may be slung from the oil sump 102 onto the piston 118 and cylinder wall 120. For instance, in one embodiment, shown in FIGS. 1 and 2, the disk 112 is bolted to a counterweight 122 of the crankshaft assembly 108 so that it is centered coaxially with the center of rotation 124 of the crankshaft assembly 110. The disk 112 may have an aperture 126 sized and shaped to fit over the crankshaft assembly 110 so that the disk 112 and crankshaft assembly 110 may be assembled together. However, it will be appreciated that other fabrication methods may be employed without departing from the scope and spirit of the present invention. For example, the disk 112 may be formed as an integral part of the crankshaft assembly 110, or the crankshaft assembly 110 may be formed in two or more sections that are joined together around the disk 112, thereby clamping the disk 112 in place.

During operation of the air compressor 106, rotation of the crankshaft assembly 110 rotates the oil slinger 108 for splashing lubricating oil 114 from the oil sump 102 onto components of the air compressor 106 being lubricated (e.g., crankshaft assembly 110, journal 116, piston 118, cylinder wall 120, and the like). As shown, the disk 112 of oil slinger 108 is generally centered coaxially with the center of rotation 124 of the crankshaft assembly 110 so that rotation of the crankshaft assembly 110 causes the disk 112 to rotate 360 degrees about the center of rotation of the crankshaft 124. Thus, during operation, the lower portion of disk 112 is continuously submerged in lubricating oil 114 contained in the oil sump 102. Because the disk 112 remains in the oil 114 instead of cyclically entering and exiting the oil 114, as does a conventional dip stick or dipper oil slinger, the volume of oil 114 in the oil sump 102 that the disk 112 displaces does not change during each revolution of the crankshaft 110. Further, the oil slinger 108, being a continuous disk 112, does not have a high speed advancing edge that must pass through the lubricating oil 114 as do dipper slingers. Thus, the flow of lubricating oil 114 over the surface of the oil slinger 108 as it advances through the oil sump 102 is substantially more laminar than is possible with intermittent dipper slingers. As a result, the disk oil slinger 108 of the present invention is capable of moving lubricating oil 114 about the crankcase 104 with substantially less atomization of the oil 114.

The amount of oil flow generated by an oil slinger is proportional to the surface area of the submerged portion of the slinger, and proportional to the amount of time that the slinger is submerged during each revolution of the crankshaft. Because the lower portion of the disk oil slinger 108 is continuously submerged in the lubricating oil 114 contained in the oil sump 102, and the submerged surface area of the disk 112 is substantially larger than that of the dipper of a dipper oil slinger, the oil flow rate of the disk oil slinger 108 of the present invention is significantly greater than that of an intermittent dipper slinger. For example, lubrication systems 100 in accordance with the present invention have been found to be capable of providing oil flows that are 50 to 100 times greater than lubrication systems utilizing dipper slingers, while at the same time reducing atomization of the lubricating oil 114 from the oil sump 102.

Turning now to FIGS. 3 and 4, the air compressor 106 shown in FIGS. 1 and 2 is illustrated as being tilted at an angle to the horizontal, for example, as if it were set on a non-level surface. As shown, when the crankcase 104 is tilted, the surface of the lubricating oil 114 in oil sump 102 remains substantially horizontal. As shown, the disk 112 of oil slinger 108 is generally centered coaxially with the center of rotation 124 of the crankshaft assembly 110 so that rotation of the crankshaft assembly 110 causes the disk 112 to rotate 360 degrees about the center of rotation of the crankshaft 124. As a result, the disk 112 remains at least partially submerged in the oil sump 102 if the crankcase 104 is tilted providing an increased tolerance to unit operation on non-level surfaces. It will be appreciated that the degree of tilt (α) tolerated by lubrication system 100 may vary depending on the design of crankcase 104, and is limited only by the possibility of lubricating oil 114 from the oil sump 102 entering cylinder 118. However, it is contemplated that degrees of tilt (α) of up to or even greater than 90 degrees (i.e., the crankcase 102 is tilted on its side) are possible.

Referring now to FIG. 5, a shaped oil slinger for a lubrication system in accordance with an exemplary embodiment of the invention is described. Shaped oil slinger 128 is comprised of a disk 130 including an edge portion 132 shaped for generating additional oil flow and/or for directing the oil flow at angles to the side of the disk 130, thereby distributing the oil more uniformly within the crankcase than conventional dipper type lubrication systems. Further, the edge portion 132 may be shaped so that it is capable of providing such advantages without unnecessarily interrupting the laminar flow of the lubricating oil around the disk 130, thus preventing unnecessary atomization of lubricating oil from the oil sump (see FIG. 1). For instance, in the embodiment shown in FIG. 4, edge portion 132 may be formed so as to have a contour that is generally sinusoidal or curvilinear in shape as viewed along an edge of the disk 130. Alternately, edge portion 132 may be shaped to have other contours such as fins, slots, grooves, or the like, depending on the requirements of the particular application in which the lubrication system is employed.

In addition to (or in place of) shaped edge portion 132, features 134 may be formed on the surfaces of either or both sides of disk 130 for providing additional oil flow and/or for directing the oil flow at lateral angles to the disk 130. It will be appreciated that the shape of such surface features 134 may vary depending on the requirements (desired oil flow rate, splash pattern, etc.) of the particular air compressor in which the lubrication system is employed. However, exemplary surface features 134 include circumferential or spiraled ridges or grooves (shown), spaced bumps, indentations, or slots, vanes, and the like. Additionally, surface features 134 may be shaped so they do not create unnecessary turbulence thereby interrupting the substantially laminar flow of lubricating oil around the disk 130 and increasing atomization of lubricating oil from the oil sump (see FIG. 1).

Referring now to FIG. 6, an auger oil slinger in accordance with an exemplary embodiment of the present invention is shown. Oil slinger 136 is comprised of a disk 138 having a slit 140 radially formed therein from edge portion 142 toward the disk center 144. The ends 146 & 148 of edge portion 142 adjacent to the slit 140 are separated laterally so that edge portion 142 assumes a generally spiral shape. In this manner, disk 138 is formed into a simple auger capable of generating substantially greater oil flow than the dip stick slingers of conventional dipper lubrication systems. The spiral shape of edge portion 142 may further direct the oil flow at angles to disk 138 thereby distributing the oil more uniformly within the crank case and providing greater coverage of components of the air compressor (see FIG. 1). Because disk 138 remains substantially continuous except for leading and trailing edges 150 & 152 caused by slit 140, oil flow over the surface of the disk 138 is generally laminar. Thus, atomization of lubricating oil may be held to rates that are substantially equal to or less than that of conventional dipper lubrication systems.

Based on the discussion of the disk oil slingers shown in FIG. 1 through 6, it should now be appreciated that a substantial advantage is obtained by increasing the surface area of the oil slinger so that area of laminar flow is enlarged. In this manner, cohesion of oil to the surface of the oil slinger is improved so that the volume of oil “splashed” by the oil slinger as it rotates is increased while atomization of the oil remains substantially unchanged or is reduced. Thus, it should also be appreciated that in accordance with the present invention, lubrication systems may be provided that, while not utilizing continuous disk oil slingers, provide enhanced performance compared to conventional “dip stick” or dipper systems by substantially increasing the surface area of the oil slinger to provide for more laminar flow of the lubricating oil over the slinger as it is rotated.

Referring now to FIG. 7, an oil slinger in accordance with such an alternate embodiment of the present invention is described. Oil slinger 154 is comprised of a sector 156 of the full disk 112 of oil slinger 108 shown in FIG. 1 through 4, having curvilinear leading and trailing edges 158 & 160. Preferably, the angle (β) defining sector 156 is selected to provide sufficient surface area so that the flow of lubricating oil over the oil slinger 154 as it is rotated is substantially laminar except for turbulence at leading and trailing edges 158 & 160. In this manner, the volume of oil splashed by the oil slinger 154 is substantially increased compared to conventional dipper oil slingers, while the amount of atomization of lubricating oil remains substantially equal to or less than that of conventional dipper oil slingers.

In exemplary embodiments of the invention, the oil slinger 154 may be mounted to the crankshaft assembly 110, shown in FIG. 1, so that the disk 112 from which sector 156 is taken would be generally centered coaxially with the center of rotation 124 of the crankshaft assembly 110 if it were complete. In this manner, rotation of the crankshaft assembly 110 causes the oil slinger 154 to rotate 360 degrees about the center of rotation of the crankshaft 124. As a result, the oil slinger 154 remains capable of being at least partially submerged in the oil sump 102 as it is rotated even if the crankcase 104 is tilted. In this manner, the oil slinger 154 is capable of providing an increased tolerance to air compressor operation on non-level surfaces or in non-level orientations.

Referring now to FIG. 8, implementation of a lubrication system of the present invention in an air compressor having two or more cylinder/piston assemblies is described. The lubrication system 200 includes an oil sump 202 formed in the crankcase 204 of the air compressor 206 and an oil slinger 208 coupled to the air compressor's crankshaft assembly 210. Oil slinger 208 is comprised of a generally continuous disk 212 attached to the crankshaft assembly 210.

In the exemplary embodiment shown, air compressor 206 includes two cylinder assemblies 214 & 216 housing piston assemblies 218 & 220 coupled to crankshaft assembly 210. Preferably, cylinder assemblies 214 & 216 are oriented so that a single oil slinger 208 may provide lubrication to both assemblies. For example, as shown in FIG. 8, cylinder assemblies 214 & 216 are oriented at an angle of approximately ninety degrees to one another and spaced so that they overlap thereby allowing a single plane 222, generally coaxial with oil slinger 208, to intersect both cylinder assemblies 214 & 218. In this manner, a single oil slinger may provide lubricating oil 224 from the oil sump 202 onto each cylinder assembly for lubricating components of each piston assembly 218 & 220 (e.g., eccentric bearings, wrist pin sets, etc.).

During operation of the air compressor 206, rotation of the crankshaft assembly 210 rotates the oil slinger 208 for splashing lubricating oil 224 from the oil sump 202 for lubricating piston assemblies 218 & 220 of both cylinder assemblies 214 & 216, respectively. Like the embodiment shown in FIG. 1, the disk 212 of oil slinger 208 is generally centered coaxially with the center of rotation of the crankshaft assembly 210 so that rotation of the crankshaft assembly 210 causes the disk 212 to rotate 360 degrees about the center of rotation of the crankshaft 230.

Referring generally to FIGS. 9-12, an oil-lube air compressor assembly including a lubrication system of the present invention is shown. In a present embodiment, the air compressor assembly 900, is an oil-lube, direct-drive air compressor including an air storage tank 902 for storing compressed air. (Shown in FIGS. 11-12). In further embodiments, the air compressor assembly is a belt drive assembly. (Shown in FIGS. 9-10). For example, the air storage tank 902 holds a quantity of air at a predetermined pressure range, such as between 110 and 135 psi, said quantity of air utilized for driving air powered tools. The lubrication system of the present invention is implemented within the air compressor assembly 900, the air compressor assembly having one or more cylinder/piston assemblies. (FIGS. 9-12 illustrate an air compressor assembly with one cylinder/piston assembly). The lubrication system 200 includes an oil sump 202 formed in a crankcase 204 of the air compressor 900 and an oil slinger 208 coupled to a crankshaft assembly 210 of the air compressor. Oil slinger 208 is comprised of a generally continuous disk 212 attached to the crankshaft assembly 210.

In an exemplary embodiment, the air compressor 900 includes a cylinder assembly 214 housing a piston assembly 218 coupled to crankshaft assembly 210. The air compressor further includes an electric motor 904, which is coupled either directly (such as in a direct drive air compressor) or by a belt system (such as with a belt driven air compressor) with the crankshaft assembly, thereby causing the crankshaft assembly to rotate and drive the piston assembly. In the embodiment illustrated in FIGS. 11-12, the air compressor assembly is a direct drive air compressor assembly having a universal motor. For example, with a single stage air compressor, during the downstroke of the piston assembly 218, the piston assembly moves downward within the cylinder assemblies 214 allowing for the inlet of air into the cylinder assembly, the air being from an external environment (i.e.—atmospheric pressure). During the upstroke of the piston assembly 218, the piston assembly moves upward within the cylinder assembly 214 and causes the air to be compressed and discharged into the air storage tank 902, wherein said air is stored. The electric motor 904 continues to drive the crankshaft assembly, thereby causing the intake of air by the cylinder assembly, the compression of air by the piston assembly, and discharge of air into the tank 902 as described above until the pressure within the tank reaches a predetermined pressure or falls within a predetermined pressure range, such as between 115 and 135 psi. In a present embodiment, the air compressor includes a pressure regulator 906 for monitoring the pressure within the tank 902. The pressure regulator 906 is configured to automatically cause the electric motor 904 to cycle on and off respectively so that the compressed air stored within the air storage tank 902 is maintained at a predetermined pressure or within a predetermined pressure range. In further embodiments, the air compressor 900 may be a 2-stage compressor.

In further embodiments, the compressor assembly includes a safety valve 908 for releasing pressure within the air storage tank 902.

In further embodiments, the compressor assembly includes a check valve 910.

In further embodiments, the compressor assembly includes a drain plug 912.

In embodiments with two or more cylinder/piston assemblies, preferably, cylinder assemblies 214 & 216 are oriented so that a single oil slinger 208 may provide lubrication to both assemblies. For example, as shown in FIG. 8, cylinder assemblies 214 & 216 are oriented at an angle of approximately ninety degrees to one another and spaced so that they overlap thereby allowing a single plane 222, generally coaxial with oil slinger 208, to intersect both cylinder assemblies 214 & 218. In this manner, a single oil slinger may provide lubricating oil 224 from the oil sump 202 onto each cylinder assembly for lubricating components of each piston assembly 218 & 220 (e.g., eccentric bearings, wrist pin sets, etc.).

During operation of the air compressor 900, the electric motor 904 drives the crankshaft assembly 210 and causes rotation of the crankshaft assembly 210, which rotates the oil slinger 208 for splashing lubricating oil 224 from the oil sump 202 for lubricating piston assembly 218 of the cylinder assembly 214, respectively. Like the embodiment shown in FIG. 1, the disk 212 of oil slinger 208 is generally centered coaxially with the center of rotation of the crankshaft assembly 210 so that rotation of the crankshaft assembly 210 causes the disk 212 to rotate 360 degrees about the center of rotation of the crankshaft 230.

It will be appreciated that, based on the foregoing discussion, an air compressor may be fabricated to comprise three or more cylinder assemblies oriented to be lubricated by a single oil slinger, such as oil slinger 208, without departing from the scope and spirit of the invention. Moreover, in other embodiments, air compressors may be provided having multiple cylinder/piston assemblies that are lubricated by lubrication systems having two or more oil slinger systems in accordance with the present invention. Again, such embodiments would not depart from the scope and spirit of the present invention.

It is contemplated that, employing the principles of the invention discussed and illustrated herein, those of skill in the art may now design lubrication systems utilizing oil slingers having a wide variety of shapes (e.g., oval, eccentric, octagonal, etc.) and/or edge and surface features other than those specifically disclosed. Accordingly, such lubrication systems are considered to be well within the scope and spirit of the present invention as presently claimed. Further, it is believed that the lubrication system of the present invention and many of its attendant advantages will be understood by the forgoing description, and it will be apparent that various changes may be made in the form, construction and arrangement of the components thereof without departing from the scope and spirit of the invention or without sacrificing all of its material advantages, the form herein before described being merely an explanatory embodiment thereof. It is the intention of the following claims to encompass and include such changes.

Claims

1. An air compressor assembly, comprising: an air storage tank for storing at a first pressure; an air compressor for compressing air from a second pressure to the first pressure for storage in the air storage tank, the air compressor including a cylinder, a piston disposed within the cylinder, a crankcase housing a crankshaft assembly for reciprocating the piston within the cylinder, an oil sump formed in the crankcase for containing lubricating oil for lubricating the cylinder and piston, and a generally disk shaped oil slinger positioned below the cylinder and co-planer with a plane passing though the cylinder, the generally disk shaped oil slinger being coupled to the crankshaft assembly; and, a motor for driving the crankshaft assembly for reciprocating the piston within the cylinder; wherein rotation of the crankshaft assembly by the motor rotates the oil slinger for splashing lubricating oil from the oil sump onto the cylinder and piston.

2. The air compressor assembly as claimed in claim 1, further comprising a pressure regulator for regulating the pressure of air in the air storage tank to at least approximately the first pressure by starting and stopping the motor.

3. The air compressor assembly as claimed in claim 1, wherein the air compressor assembly is a direct drive air compressor assembly.

4. The air compressor assembly as claimed in claim 1, wherein the air compressor assembly is a belt drive air compressor assembly.

5. The air compressor assembly as claimed in claim 1, wherein the motor is a universal motor.

6. The air compressor assembly as claimed in claim 1, further comprising a safety valve for releasing pressure within the air storage tank.

7. The air compressor assembly as claimed in claim 1, further comprising a check valve.

8. The air compressor assembly as claimed in claim 1, further comprising a drain plug.

9. An air compressor assembly, comprising: an air storage tank for storing at a first pressure; an air compressor for compressing air from a second pressure to the first pressure for storage in the air storage tank, the air compressor including a cylinder, a piston disposed within the cylinder, a crankcase housing a crankshaft assembly for reciprocating the piston within the cylinder, an oil sump formed in the crankcase for containing lubricating oil for lubricating the cylinder and piston, and a generally disk shaped oil slinger positioned below the cylinder and co-planer with a plane passing though the cylinder, the generally disk shaped oil slinger being coupled to the crankshaft assembly; and, a motor for driving the crankshaft assembly for reciprocating the piston within the cylinder; wherein rotation of the crankshaft assembly by the motor rotates the oil slinger for splashing lubricating oil from the oil sump onto the cylinder and piston; wherein the air compressor assembly is a direct drive air compressor assembly.

10. The air compressor assembly as claimed in claim 9, further comprising a pressure regulator for regulating the pressure of air in the air storage tank to at least approximately the first pressure by starting and stopping the motor.

11. The air compressor assembly as claimed in claim 9, wherein the motor is a universal motor.

12. The air compressor assembly as claimed in claim 9, further comprising a safety valve for releasing pressure within the air storage tank.

13. The air compressor assembly as claimed in claim 9, further comprising a check valve.

14. The air compressor assembly as claimed in claim 9, further comprising a drain plug.

15. An air compressor assembly, comprising: an air storage tank for storing at a first pressure; an air compressor for compressing air from a second pressure to the first pressure for storage in the air storage tank, the air compressor including a cylinder, a piston disposed within the cylinder, a crankcase housing a crankshaft assembly for reciprocating the piston within the cylinder, an oil sump formed in the crankcase for containing lubricating oil for lubricating the cylinder and piston, and a generally disk shaped oil slinger positioned below the cylinder and co-planer with a plane passing though the cylinder, the generally disk shaped oil slinger being coupled to the crankshaft assembly; and, a universal motor for driving the crankshaft assembly for reciprocating the piston within the cylinder; wherein rotation of the crankshaft assembly by the motor rotates the oil slinger for splashing lubricating oil from the oil sump onto the cylinder and piston; wherein the air compressor assembly is a direct drive air compressor assembly.

16. The air compressor assembly as claimed in claim 15, further comprising a pressure regulator for regulating the pressure of air in the air storage tank to at least approximately the first pressure by starting and stopping the motor.

17. The air compressor assembly as claimed in claim 15, further comprising a safety valve for releasing pressure within the air storage tank.

18. The air compressor assembly as claimed in claim 15, further comprising a check valve.

19. The air compressor assembly as claimed in claim 15, further comprising a drain plug.

20. The air compressor assembly as claimed in claim 15, further comprising one or more gauges.