US20060104838A1 - Integrated eccentric flywheel oil slinger - Google Patents
Integrated eccentric flywheel oil slinger Download PDFInfo
- Publication number
- US20060104838A1 US20060104838A1 US11/120,151 US12015105A US2006104838A1 US 20060104838 A1 US20060104838 A1 US 20060104838A1 US 12015105 A US12015105 A US 12015105A US 2006104838 A1 US2006104838 A1 US 2006104838A1
- Authority
- US
- United States
- Prior art keywords
- oil
- main body
- generally cylindrical
- cylindrical main
- aperture
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0284—Constructional details, e.g. reservoirs in the casing
- F04B39/0292—Lubrication of pistons or cylinders
Definitions
- the present invention generally relates to the field of oil lubrication devices for compressors, and more particularly to an integrated eccentric flywheel oil slinger suitable for use in oil lubricated air compressors.
- portable pump devices such as compressors, power washers, and the like include a crankcase or housing encompassing pump components.
- a gear box often encloses an eccentric, coupled to a drive shaft of the engine or motor powering the pump, for reciprocating a piston in a cylinder.
- a counter weight and a flywheel may be mounted to the drive shaft. The use of the counter weight and flywheel allows pump vibration to be off-set (such as those caused by piston reciprocation), the overall moment of inertia to be increased and the eccentric to be generally counterbalanced.
- an oil slinger may also be coupled to the shaft to disperse oil from a reservoir or oil sump which is formed in the crankcase or the like for reducing friction and cooling the various pump components.
- an oil slinger is configured to minimize atomization of the oil, account for the pump device being disposed in a non-ideal manner (e.g., disposed on a non-level surface), while providing sufficient lubrication and cooling.
- 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 “dipstick” is attached to one or more of the moving components such that during each revolution of the crankshaft, the dipstick 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 dipstick 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 dipstick 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.
- a pump assembly with a simplified pump component configuration including a 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.
- the present invention is directed to an integrated eccentric flywheel oil slinger for an oil lubricated compressor crankcase.
- the integrated eccentric flywheel oil slinger includes a generally cylindrical main body being configured to provide oil to various components of the compressor crankcase and reduce vibrations made by such components.
- the generally cylindrical main body includes an aperture for receiving a crankshaft.
- an eccentric extension protrudes from the generally cylindrical main body and is configured to move about the crankshaft.
- the generally cylindrical main body is configured to counter balance the eccentric extension protruding from the generally cylindrical main body and when attached to the crankshaft provides the combined functions of the flywheel, the eccentric, the oil disk slinger and a counterweight.
- the generally cylindrical main body of the integrated eccentric flywheel oil slinger is configured to counter balance the eccentric extension protruding from the generally cylindrical main body by including apertures or recesses within the generally cylindrical main body.
- a first aperture in the general shape of a first tear drop which extends through the generally cylindrical main body and a second aperture in the general shape of a second tear drop which extends through the generally cylindrical main body are present to counter balance the mass of the eccentric extension protrusion.
- the first aperture is positioned on a first side of the eccentric extension and the second aperture is placed on a second side of the eccentric extension, the second side being generally opposite to the first side.
- the leading edge of the first tear drop providing the first aperture may be formed by the apex of the first tear drop and the leading edge of the second tear drop providing the second aperture may be formed by the base of the second tear drop.
- the generally cylindrical main body is partially curved so that the body is concave towards the eccentric extension so that the generally cylindrical main body counter balances the eccentric extension.
- the width of the generally cylindrical main body is approximately 0.813 (eight hundred and thirteen hundredths) inches to provide oil to the various pump components.
- an oil lubricated air compressor assembly in another aspect of the present invention, includes an air storage tank for storing air at a first pressure and an air compressor for compressing air from a second pressure to the first pressure for storage in the air storage tank.
- the air compressor includes 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 an integrated eccentric flywheel oil slinger positioned below the cylinder.
- the integrated eccentric flywheel oil slinger disk shaped oil may include a generally cylindrical main body being configured to function as a oil disk slinger and a flywheel. Moreover, the generally cylindrical main body includes an aperture for coupling with the crankshaft assembly and an eccentric extension protruding from the generally cylindrical main body being configured to move about the crankshaft assembly. Further, a motor is included for driving the crankshaft assembly for reciprocating the piston within the cylinder. Rotation of the crankshaft assembly by the motor rotates the integrated eccentric flywheel oil slinger for splashing lubricating oil from the oil sump onto the cylinder and piston.
- the oil lubricated air compressor assembly includes a generally cylindrical main body which is configured to counter balance the eccentric extension protruding from such body by including apertures or recesses within the generally cylindrical main body.
- a first aperture in the general shape of a first tear drop which extends through the generally cylindrical main body and a second aperture in the general shape of a second tear drop which extends through the generally cylindrical main body are present to counter balance the mass of the eccentric extension protrusion.
- the first aperture is positioned on a first side of the eccentric extension and the second aperture is placed on a second side of the eccentric extension, the second side being generally opposite to the first side.
- the leading edge of the first tear drop forming the first aperture includes the apex of the first tear drop and the leading edge of the second tear drop forming the second aperture includes the base of the second tear drop.
- the oil lubricated air compressor assembly includes a generally cylindrical main body partially curved so that the body is concave towards the eccentric extension so that the generally cylindrical main body counter balances the eccentric extension. Further, in an embodiment, the width of the generally cylindrical main body is approximately 0.813 inches to provide oil to various components of the air compressor assembly. Moreover, in an embodiment, the air compressor is a direct drive air compressor.
- FIG. 1 is an isometric view of an oil lubricated air compressor assembly in accordance with an exemplary embodiment of the present invention, wherein the air compressor assembly includes an integrated eccentric flywheel oil slinger;
- FIG. 2 is an exploded view of the integrated eccentric flywheel slinger shown in FIG. 1 , wherein the integrated eccentric flywheel oil slinger is mounted to the air compressor assembly via a crankshaft extending through a central aperture present within the integrated eccentric flywheel oil slinger;
- FIG. 3 is an isometric view of an integrated eccentric flywheel oil slinger in accordance with an exemplary embodiment of the present invention, wherein the integrated eccentric flywheel oil slinger includes apertures to counter balance the mass of an eccentric extension protruding from the integrated eccentric flywheel oil slinger;
- FIG. 4 is an isometric view of an integrated eccentric flywheel oil slinger in accordance with an exemplary embodiment of the present invention, wherein the integrated eccentric flywheel oil slinger includes recesses to counter balance the mass of an eccentric extension protruding from the integrated eccentric flywheel oil slinger;
- FIG. 5 a side elevational view of an integrated eccentric flywheel oil slinger in accordance with the present invention, wherein the position of the integrated eccentric flywheel oil slinger and the oil level when the air compressor assembly is not in operation is provided;
- FIG. 6 is a side elevational view of an integrated eccentric flywheel oil slinger in accordance with the present invention, wherein the position of the integrated eccentric flywheel oil slinger and the oil level when the air compressor assembly is in operation is provided;
- FIG. 7 is a side elevational view of an integrated eccentric flywheel oil slinger in accordance with the present invention, wherein the position of the integrated eccentric flywheel oil slinger and the oil level when the air compressor assembly is tilted is provided;
- FIG. 8 is an isometric view of a direct drive air compressor assembly in accordance with the present invention, wherein the direct drive air compressor assembly includes two integrated eccentric flywheel oil slingers.
- the air compressor assembly 100 includes an air storage tank 102 for storing air at a first pressure and an air compressor 104 for compressing air from a second pressure to the first pressure for storage in the air storage tank 102 .
- the air compressor 104 is a direct drive air compressor.
- an air compressor with a transmission system e.g. a belt driven air compressor
- the air compressor includes a cylinder 106 , a piston 108 disposed within the cylinder 106 , a crankcase 110 housing a crankshaft assembly 112 for reciprocating the piston 108 within the cylinder 106 , an oil sump 114 formed in the crankcase 110 for containing lubricating oil 116 for lubricating the cylinder 106 and piston 108 , and an integrated eccentric flywheel oil slinger 118 positioned below the cylinder 106 . Further, a motor 120 is included for driving the crankshaft assembly 112 for reciprocating the piston 108 within the cylinder 106 .
- crankshaft assembly 112 Rotation of the crankshaft assembly 112 by the motor 120 rotates the integrated eccentric flywheel oil slinger 118 for splashing lubricating oil 116 from the oil sump 114 onto the cylinder 106 and piston 108 .
- the integrated eccentric flywheel oil slinger 118 is mounted to the air compressor assembly 100 via a crankshaft 122 extending through a central aperture 124 present within the integrated eccentric flywheel oil slinger 118 .
- an exemplary integrated eccentric flywheel oil slinger 118 is provided whereby the integrated eccentric flywheel oil slinger 118 includes a generally cylindrical main body 126 .
- the generally cylindrical main body 126 is configured to function as an oil disk slinger and a flywheel.
- the generally cylindrical main body 126 includes the aperture 124 for receiving the crankshaft 122 (as illustrated in FIG. 2 ) powered by an engine or motor as desired.
- the aperture 124 may be constructed to form a mechanical connection such as a tongue and groove or the like interlocking structure to secure the integrated eccentric flywheel oil slinger 118 to the crankshaft 122 .
- an eccentric extension 128 protrudes from the generally cylindrical main body 126 and is configured to move about the crankshaft 122 .
- the eccentric extension may be formed as a solid extension or as a lip which forms the peripheral surface of the eccentric for connection to a piston shaft.
- the generally cylindrical main body 126 is configured to counter balance the eccentric extension 128 protruding from the generally cylindrical main body 126 and when attached to the crankshaft 122 provides the combined functions of the flywheel, the eccentric, the oil disk slinger and a counterweight.
- the integrated eccentric flywheel oil slinger 100 provides oil to components of the compressor crankcase and reduces vibrations generated by such components.
- the generally cylindrical main body 126 of the integrated eccentric flywheel oil slinger 118 is configured to counter balance the eccentric extension 128 protruding from the generally cylindrical main body 126 by including apertures within the generally cylindrical main body 126 .
- the apertures may include a first aperture 130 in the general shape of a first tear drop which extends through the generally cylindrical main body 126 and a second aperture 132 in the general shape of a second tear drop which also extends through the generally cylindrical main body 126 .
- the first aperture 130 is positioned on a first side of the eccentric extension 128 and the second aperture 132 is placed on a second side of the eccentric extension 128 , the second side being generally opposite to the first side.
- leading edge of the first tear drop providing the first aperture 130 may be formed by the apex 134 of the first tear drop and the leading edge of the second tear drop providing the second aperture 132 may be formed by the base 136 of the second tear drop.
- the resulting configuration of the apertures offsets the mass of the eccentric extension 128 of the integrated eccentric flywheel oil slinger 118 .
- the generally cylindrical main body 126 of the integrated eccentric flywheel oil slinger 118 includes a first recess 138 generally shaped as a first tear drop and a second recess 140 generally shaped as a second tear drop.
- the leading edge of the first tear drop providing the first recess 138 is formed by an apex 142 of the first tear drop and the leading edge of the second tear drop providing the second recess 140 is formed by the base 144 of the second tear drop.
- Such configuration allows the recesses to offset the mass of the eccentric extension 128 .
- the mass of the eccentric extension 128 may be counter balanced or offset by additional variations in the configuration of the generally cylindrical main body 126 including partially curvation.
- the generally cylindrical main body 126 may be partially curved towards the eccentric extension 128 (e.g., concave towards the eccentric extension) so as to optimize the effect of the counter weight along the length of the crankshaft 122 (e.g. the apparatus is generally balanced in the direction of the crankshaft), increase lubrication, or the like.
- the main body is configured (e.g. includes apertures, recesses, curvation, and the like) such that the main body portion is sufficient to counter balance the eccentric extension.
- alternative embodiments of the integrated eccentric flywheel oil slinger may include a counterweight extension formed on the generally cylindrical main body generally opposite the eccentric extension.
- the integrated eccentric flywheel oil slinger 118 includes an edge portion 146 shaped for generating additional oil flow and/or for directing the oil flow at angles to the side of the integrated eccentric flywheel oil slinger 118 , thereby distributing the oil more uniformly within the crankcase than conventional dipper type lubrication systems.
- edge portion 146 may be shaped so that it is capable of providing such advantages without unnecessarily interrupting the laminar flow of the lubricating oil around the integrated eccentric flywheel oil slinger 118 , thus preventing unnecessary atomization of lubricating oil 116 from the oil sump 114 .
- the edge portion may include various contours such as fins, slots, grooves, or the like, depending on the requirements of the particular application in which the integrated eccentric flywheel oil slinger 118 is employed.
- the integrated eccentric flywheel oil slinger 118 may be formed of powdered metal including ferrous powder metal which provides a porous surface to which oil may be absorbed allowing an increased amount of oil to be distributed within the crankcase upon the rotation of the slinger 118 compared to that dispersed by conventional dipper type lubrication systems.
- the portion of the integrated eccentric flywheel oil slinger 118 which contacts the oil 116 present within the oil sump 114 may be coated with powdered metal to impart similar advantageous properties (e.g.
- the integrated eccentric flywheel oil slinger 118 may be made of cast iron or a combination of powdered metal and cast iron or steel.
- the inner part of the integrated eccentric flywheel oil slinger 118 may be made of powdered metal while the outer rim may be made of steel.
- the position of the integrated eccentric flywheel oil slinger and the oil level when the air compressor assembly is inoperable and operable, respectively, is provided.
- the lower portion of the integrated eccentric flywheel oil slinger 118 resides in the lubricating oil 116 present within the oil sump 114 .
- a portion of the first or second apertures present within the generally cylindrical main body 126 may also contact the lubricating oil 116 .
- the supplying of electrical power to the air compressor assembly 100 results in the oil level within the oil sump 114 dropping whereby the lower portion of the integrated eccentric flywheel oil slinger 118 remains in the oil, but the apertures no longer make such contact as oil is slung.
- rotation of the crankshaft assembly 112 rotates the integrated eccentric flywheel oil slinger 118 for splashing lubricating oil 116 from the oil sump 114 onto components of the air compressor 104 being lubricated (e.g., crankshaft assembly 112 , piston 108 , cylinder/cylinder wall 106 , and the like).
- the integrated eccentric flywheel oil slinger 118 is generally centered coaxially with the center of rotation of the crankshaft assembly 112 so that rotation of the crankshaft assembly 112 causes the integrated eccentric flywheel oil slinger 118 to rotate about the center of rotation of the crankshaft.
- the lower portion of the integrated eccentric flywheel oil slinger 118 is continuously submerged in lubricating oil 116 contained in the oil sump 114 .
- the volume of oil 116 in the oil sump 114 that the integrated eccentric flywheel oil slinger 118 displaces does not change during each revolution of the crankshaft assembly 112 .
- the integrated eccentric flywheel oil slinger 118 being a continuous disk, does not have a high speed advancing edge that must pass through the lubricating oil 116 as do dipper slingers.
- the flow of lubricating oil 116 over the surface of the integrated eccentric flywheel oil slinger 118 as it advances through the oil sump 114 is substantially more laminar than is possible with intermittent dipper slingers.
- the integrated eccentric flywheel oil slinger 118 of the present invention is capable of moving lubricating oil 116 about the crankcase 110 with substantially less atomization of the oil 116 .
- 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 118 is continuously submerged in the lubricating oil 116 contained in the oil sump 114 , and the submerged surface area of the integrated eccentric flywheel oil slinger 118 is substantially larger than that of the dipper of a dipper oil slinger, the oil flow rate of the integrated eccentric flywheel oil slinger 118 of the present invention is significantly greater than that of an intermittent dipper slinger.
- the volume of oil circulated by the integrated eccentric flywheel oil slinger 118 is significantly increased by increasing the width of the generally cylindrical main body 126 .
- the width of the generally cylindrical main body is approximately 0.813 inches compared to the traditionally narrow prior art disk slingers generally 0.033 inches in width.
- the increased width increase the volume of oil circulated by the integrated eccentric flywheel oil slinger 118 which improves the cooling capability of oil flow in the crankcase 110 .
- the air compressor assembly 100 may include a direct drive air compressor.
- Such assembly may also include a piston 108 with a large diameter (e.g., two inches and seven eighths of an inch) operationally coupled to the integrated eccentric flywheel oil slinger 118 to maximize piston cooling and enable a compressor to operate at higher pressures than compared to a similar direct drive air compressor assembly including a standard/average sized piston (e.g. piston diameter ranging from two inches to two inches and three eighths of an inch).
- a standard/average sized piston e.g. piston diameter ranging from two inches to two inches and three eighths of an inch.
- Oil cooling of the piston and compression chamber is proportional to the surface area of the piston which is proportional to the piston diameter.
- a small piston diameter e.g., piston diameter ranging from two inches to two inches and three eighths of an inch
- the combination of an integrated eccentric flywheel oil slinger 118 with an increased width and a piston 108 with a large diameter may be used to maximize piston and compression chamber cooling and enable the compressor to operate at higher pressures.
- the air compressor 104 shown in FIG. 1 is illustrated as being tilted at an angle to the horizontal, for example, as if it were set on a non-level surface.
- the surface of the lubricating oil 116 in oil sump 114 remains substantially horizontal.
- the integrated eccentric flywheel oil slinger 118 is generally centered coaxially with the center of rotation of the crankshaft assembly 112 so that rotation of the crankshaft assembly 112 causes the integrated eccentric flywheel oil slinger to rotate 360° (three hundred and sixty degrees) about the center of rotation of the crankshaft 122 .
- the integrate eccentric flywheel oil slinger 118 remains at least partially submerged in the oil sump 114 if the crankcase 110 is tilted providing an increased tolerance to unit operation on non-level surfaces.
- the degree of tilt ( ⁇ ) tolerated by integrated eccentric flywheel oil slinger 118 may vary depending on the design of crankcase 110 , and is limited only by the possibility of lubricating oil 116 from the oil sump 114 entering the cylinder 106 .
- degrees of tilt ( ⁇ ) of up to or even greater than 90° (ninety degrees) are possible.
- the instant integrated eccentric flywheel oil slinger may be employed in an air compressor having two or more cylinder/piston assemblies.
- the cylinder assemblies are configured such that a single integrated eccentric flywheel oil slinger 118 is sufficient to provide lubrication to both assemblies.
- cylinder assemblies may be oriented at an angle of approximately ninety degrees to one another and spaced so that they overlap thereby allowing a single plane, generally coaxial with the integrated eccentric flywheel oil slinger 118 , to intersect both cylinder assemblies.
- air compressors may be provided having multiple cylinder/piston assemblies that are lubricated by two or more integrated eccentric flywheel oil slingers in accordance with the present invention.
- two integrated eccentric flywheel oil slingers are present to lubricate the multiple cylinder/piston assemblies present within a direct drive air compressor assembly.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
An integrated eccentric flywheel oil slinger for an oil lubricated compressor crankcase. In an exemplary embodiment, the integrated eccentric flywheel oil slinger includes a generally cylindrical main body being configured to provide oil to components of the compressor crankcase and to reduce vibrations caused by such components. The generally cylindrical main body includes an aperture for receiving a crankshaft. Further, an eccentric extension protrudes from the generally cylindrical main body and is configured to move about the crankshaft. The generally cylindrical main body is configured to counter balance the eccentric extension protruding from the generally cylindrical main body and when attached to the crankshaft provides oil to components of the compressor crankcase to cool such components and reduces vibrations generated by the components of the compressor crankcase.
Description
- The present application claims the benefit under 35 U.S.C. § 119(e) of U.S. Provisional Application Ser. No. 60/567,138, filed Apr. 30, 2004 which is herein incorporated by reference in its entirety. The present application incorporates the following United States Patent Applications by reference in their entireties: U.S. patent application Ser. No. 11/005,887, U.S. patent application Ser. No. 10/118,675, now abandoned, and U.S. patent application Ser. No. 09/861,285.
- The present invention generally relates to the field of oil lubrication devices for compressors, and more particularly to an integrated eccentric flywheel oil slinger suitable for use in oil lubricated air compressors.
- Typically, portable pump devices such as compressors, power washers, and the like include a crankcase or housing encompassing pump components. A gear box often encloses an eccentric, coupled to a drive shaft of the engine or motor powering the pump, for reciprocating a piston in a cylinder. Further, in order to dampen or reduce vibrations caused by any imbalance in the pump mechanism (such as vibrations related to the eccentric's motion) a counter weight and a flywheel may be mounted to the drive shaft. The use of the counter weight and flywheel allows pump vibration to be off-set (such as those caused by piston reciprocation), the overall moment of inertia to be increased and the eccentric to be generally counterbalanced. Additionally, an oil slinger may also be coupled to the shaft to disperse oil from a reservoir or oil sump which is formed in the crankcase or the like for reducing friction and cooling the various pump components. Preferably, an oil slinger is configured to minimize atomization of the oil, account for the pump device being disposed in a non-ideal manner (e.g., disposed on a non-level surface), while providing sufficient lubrication and cooling.
- Lower cost oil lubricated air compressors, for example, 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 “dipstick” is attached to one or more of the moving components such that during each revolution of the crankshaft, the dipstick 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 dipstick 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 dipstick 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.
- Additional concerns associated with such traditional splash oil lubrication systems are 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 dipstick splash lubricator may not reach the oil sump causing a lack of needed lubrication and cooling, possibly leading to subsequent component failure.
- Consequently, the foregoing combination of components results in complex assembly and multiple part fabrication which may diminish manufacturing efficiency, require a large number of individual components, require a relatively high level of skill to repair, and the like. Therefore, it would be desirable to provide a pump assembly with a simplified pump component configuration including a 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.
- Accordingly, the present invention is directed to an integrated eccentric flywheel oil slinger for an oil lubricated compressor crankcase. In a first aspect of the present invention, the integrated eccentric flywheel oil slinger includes a generally cylindrical main body being configured to provide oil to various components of the compressor crankcase and reduce vibrations made by such components. In such embodiment, the generally cylindrical main body includes an aperture for receiving a crankshaft. Further, an eccentric extension protrudes from the generally cylindrical main body and is configured to move about the crankshaft. In addition, the generally cylindrical main body is configured to counter balance the eccentric extension protruding from the generally cylindrical main body and when attached to the crankshaft provides the combined functions of the flywheel, the eccentric, the oil disk slinger and a counterweight.
- In further aspects of the present invention, the generally cylindrical main body of the integrated eccentric flywheel oil slinger is configured to counter balance the eccentric extension protruding from the generally cylindrical main body by including apertures or recesses within the generally cylindrical main body. For example, a first aperture in the general shape of a first tear drop which extends through the generally cylindrical main body and a second aperture in the general shape of a second tear drop which extends through the generally cylindrical main body are present to counter balance the mass of the eccentric extension protrusion. Further, in an embodiment, the first aperture is positioned on a first side of the eccentric extension and the second aperture is placed on a second side of the eccentric extension, the second side being generally opposite to the first side. Additionally, the leading edge of the first tear drop providing the first aperture may be formed by the apex of the first tear drop and the leading edge of the second tear drop providing the second aperture may be formed by the base of the second tear drop.
- In additional aspects of the present invention, the generally cylindrical main body is partially curved so that the body is concave towards the eccentric extension so that the generally cylindrical main body counter balances the eccentric extension. Further, in an embodiment, the width of the generally cylindrical main body is approximately 0.813 (eight hundred and thirteen hundredths) inches to provide oil to the various pump components.
- In another aspect of the present invention, an oil lubricated air compressor assembly is provided. In an exemplary embodiment, the oil lubricated air compressor assembly includes an air storage tank for storing air at a first pressure and an air compressor for compressing air from a second pressure to the first pressure for storage in the air storage tank. In the embodiment, the air compressor includes 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 an integrated eccentric flywheel oil slinger positioned below the cylinder. The integrated eccentric flywheel oil slinger disk shaped oil may include a generally cylindrical main body being configured to function as a oil disk slinger and a flywheel. Moreover, the generally cylindrical main body includes an aperture for coupling with the crankshaft assembly and an eccentric extension protruding from the generally cylindrical main body being configured to move about the crankshaft assembly. Further, a motor is included for driving the crankshaft assembly for reciprocating the piston within the cylinder. Rotation of the crankshaft assembly by the motor rotates the integrated eccentric flywheel oil slinger for splashing lubricating oil from the oil sump onto the cylinder and piston.
- In even further aspects of the present invention, the oil lubricated air compressor assembly, includes a generally cylindrical main body which is configured to counter balance the eccentric extension protruding from such body by including apertures or recesses within the generally cylindrical main body. For instance, a first aperture in the general shape of a first tear drop which extends through the generally cylindrical main body and a second aperture in the general shape of a second tear drop which extends through the generally cylindrical main body are present to counter balance the mass of the eccentric extension protrusion. Further, in an embodiment, the first aperture is positioned on a first side of the eccentric extension and the second aperture is placed on a second side of the eccentric extension, the second side being generally opposite to the first side. Additionally, the leading edge of the first tear drop forming the first aperture includes the apex of the first tear drop and the leading edge of the second tear drop forming the second aperture includes the base of the second tear drop.
- In additional aspects of the present invention, the oil lubricated air compressor assembly includes a generally cylindrical main body partially curved so that the body is concave towards the eccentric extension so that the generally cylindrical main body counter balances the eccentric extension. Further, in an embodiment, the width of the generally cylindrical main body is approximately 0.813 inches to provide oil to various components of the air compressor assembly. Moreover, in an embodiment, the air compressor is a direct drive air compressor.
- 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 of an oil lubricated air compressor assembly in accordance with an exemplary embodiment of the present invention, wherein the air compressor assembly includes an integrated eccentric flywheel oil slinger; -
FIG. 2 is an exploded view of the integrated eccentric flywheel slinger shown inFIG. 1 , wherein the integrated eccentric flywheel oil slinger is mounted to the air compressor assembly via a crankshaft extending through a central aperture present within the integrated eccentric flywheel oil slinger; -
FIG. 3 is an isometric view of an integrated eccentric flywheel oil slinger in accordance with an exemplary embodiment of the present invention, wherein the integrated eccentric flywheel oil slinger includes apertures to counter balance the mass of an eccentric extension protruding from the integrated eccentric flywheel oil slinger; -
FIG. 4 is an isometric view of an integrated eccentric flywheel oil slinger in accordance with an exemplary embodiment of the present invention, wherein the integrated eccentric flywheel oil slinger includes recesses to counter balance the mass of an eccentric extension protruding from the integrated eccentric flywheel oil slinger; -
FIG. 5 a side elevational view of an integrated eccentric flywheel oil slinger in accordance with the present invention, wherein the position of the integrated eccentric flywheel oil slinger and the oil level when the air compressor assembly is not in operation is provided; -
FIG. 6 is a side elevational view of an integrated eccentric flywheel oil slinger in accordance with the present invention, wherein the position of the integrated eccentric flywheel oil slinger and the oil level when the air compressor assembly is in operation is provided; -
FIG. 7 is a side elevational view of an integrated eccentric flywheel oil slinger in accordance with the present invention, wherein the position of the integrated eccentric flywheel oil slinger and the oil level when the air compressor assembly is tilted is provided; and -
FIG. 8 is an isometric view of a direct drive air compressor assembly in accordance with the present invention, wherein the direct drive air compressor assembly includes two integrated eccentric flywheel oil slingers. - 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 and 2 , an exemplary air compressor assembly including an integrated eccentric flywheel oil slinger suitable for providing lubrication to the moving components of an air compressor in accordance with the present invention is described. Theair compressor assembly 100 includes anair storage tank 102 for storing air at a first pressure and anair compressor 104 for compressing air from a second pressure to the first pressure for storage in theair storage tank 102. In the embodiment, theair compressor 104 is a direct drive air compressor. However, it is contemplated that an air compressor with a transmission system (e.g. a belt driven air compressor) may also be employed with departing from the scope and spirit of the present invention. - In the present embodiment, the air compressor includes a
cylinder 106, apiston 108 disposed within thecylinder 106, acrankcase 110 housing acrankshaft assembly 112 for reciprocating thepiston 108 within thecylinder 106, anoil sump 114 formed in thecrankcase 110 for containinglubricating oil 116 for lubricating thecylinder 106 andpiston 108, and an integrated eccentricflywheel oil slinger 118 positioned below thecylinder 106. Further, amotor 120 is included for driving thecrankshaft assembly 112 for reciprocating thepiston 108 within thecylinder 106. Rotation of thecrankshaft assembly 112 by themotor 120 rotates the integrated eccentricflywheel oil slinger 118 for splashinglubricating oil 116 from theoil sump 114 onto thecylinder 106 andpiston 108. As illustrated inFIG. 2 , the integrated eccentricflywheel oil slinger 118 is mounted to theair compressor assembly 100 via acrankshaft 122 extending through acentral aperture 124 present within the integrated eccentricflywheel oil slinger 118. - Referring to
FIG. 3 , an exemplary integrated eccentricflywheel oil slinger 118 is provided whereby the integrated eccentricflywheel oil slinger 118 includes a generally cylindricalmain body 126. The generally cylindricalmain body 126 is configured to function as an oil disk slinger and a flywheel. In such embodiment, the generally cylindricalmain body 126 includes theaperture 124 for receiving the crankshaft 122 (as illustrated inFIG. 2 ) powered by an engine or motor as desired. Theaperture 124 may be constructed to form a mechanical connection such as a tongue and groove or the like interlocking structure to secure the integrated eccentricflywheel oil slinger 118 to thecrankshaft 122. - Further, in an exemplary embodiment, an
eccentric extension 128 protrudes from the generally cylindricalmain body 126 and is configured to move about thecrankshaft 122. Those of skill in the art will appreciate that the eccentric extension may be formed as a solid extension or as a lip which forms the peripheral surface of the eccentric for connection to a piston shaft. In addition, the generally cylindricalmain body 126 is configured to counter balance theeccentric extension 128 protruding from the generally cylindricalmain body 126 and when attached to thecrankshaft 122 provides the combined functions of the flywheel, the eccentric, the oil disk slinger and a counterweight. For example, when in operation, the integrated eccentricflywheel oil slinger 100 provides oil to components of the compressor crankcase and reduces vibrations generated by such components. - With continued reference to
FIG. 3 , the generally cylindricalmain body 126 of the integrated eccentricflywheel oil slinger 118 is configured to counter balance theeccentric extension 128 protruding from the generally cylindricalmain body 126 by including apertures within the generally cylindricalmain body 126. As illustrated inFIG. 3 , the apertures may include afirst aperture 130 in the general shape of a first tear drop which extends through the generally cylindricalmain body 126 and asecond aperture 132 in the general shape of a second tear drop which also extends through the generally cylindricalmain body 126. Further, in an embodiment, thefirst aperture 130 is positioned on a first side of theeccentric extension 128 and thesecond aperture 132 is placed on a second side of theeccentric extension 128, the second side being generally opposite to the first side. Additionally, the leading edge of the first tear drop providing thefirst aperture 130 may be formed by theapex 134 of the first tear drop and the leading edge of the second tear drop providing thesecond aperture 132 may be formed by thebase 136 of the second tear drop. The resulting configuration of the apertures offsets the mass of theeccentric extension 128 of the integrated eccentricflywheel oil slinger 118. - Referring now to
FIG. 4 , additional embodiments of the present invention which include the generally cylindricalmain body 126 of the integrated eccentricflywheel oil slinger 118 formed with recesses to counter balance theeccentric extension 128 protruding from the generally cylindricalmain body 126. As illustrated inFIG. 4 , the generally cylindricalmain body 126 of the integrated eccentricflywheel oil slinger 118 includes afirst recess 138 generally shaped as a first tear drop and asecond recess 140 generally shaped as a second tear drop. In such embodiment, the leading edge of the first tear drop providing thefirst recess 138 is formed by anapex 142 of the first tear drop and the leading edge of the second tear drop providing thesecond recess 140 is formed by thebase 144 of the second tear drop. Such configuration allows the recesses to offset the mass of theeccentric extension 128. - It is contemplated that the mass of the
eccentric extension 128 may be counter balanced or offset by additional variations in the configuration of the generally cylindricalmain body 126 including partially curvation. For example, the generally cylindricalmain body 126 may be partially curved towards the eccentric extension 128 (e.g., concave towards the eccentric extension) so as to optimize the effect of the counter weight along the length of the crankshaft 122 (e.g. the apparatus is generally balanced in the direction of the crankshaft), increase lubrication, or the like. In an advantageous embodiment, the main body is configured (e.g. includes apertures, recesses, curvation, and the like) such that the main body portion is sufficient to counter balance the eccentric extension. However, alternative embodiments of the integrated eccentric flywheel oil slinger may include a counterweight extension formed on the generally cylindrical main body generally opposite the eccentric extension. - Referring to
FIGS. 3 and 4 , the additional feature of shaping the edge portion of the integrated eccentricflywheel oil slinger 118 for generating additional oil flow and/or for directing the oil flow at angles to the side of the integrated eccentricflywheel oil slinger 118 is described. The integrated eccentricflywheel oil slinger 118 includes anedge portion 146 shaped for generating additional oil flow and/or for directing the oil flow at angles to the side of the integrated eccentricflywheel oil slinger 118, thereby distributing the oil more uniformly within the crankcase than conventional dipper type lubrication systems. Further, theedge portion 146 may be shaped so that it is capable of providing such advantages without unnecessarily interrupting the laminar flow of the lubricating oil around the integrated eccentricflywheel oil slinger 118, thus preventing unnecessary atomization of lubricatingoil 116 from theoil sump 114. - It is contemplated that the edge portion may include various contours such as fins, slots, grooves, or the like, depending on the requirements of the particular application in which the integrated eccentric
flywheel oil slinger 118 is employed. Further, the integrated eccentricflywheel oil slinger 118 may be formed of powdered metal including ferrous powder metal which provides a porous surface to which oil may be absorbed allowing an increased amount of oil to be distributed within the crankcase upon the rotation of theslinger 118 compared to that dispersed by conventional dipper type lubrication systems. Alternatively, the portion of the integrated eccentricflywheel oil slinger 118 which contacts theoil 116 present within theoil sump 114 may be coated with powdered metal to impart similar advantageous properties (e.g. oil being absorbed by the slinger resulting in more oil volume to the crankcase upon the rotation of the slinger for more oil is adhering to the slinger). In additional embodiments, the integrated eccentricflywheel oil slinger 118 may be made of cast iron or a combination of powdered metal and cast iron or steel. For example, the inner part of the integrated eccentricflywheel oil slinger 118 may be made of powdered metal while the outer rim may be made of steel. - Referring to
FIGS. 5 and 6 , the position of the integrated eccentric flywheel oil slinger and the oil level when the air compressor assembly is inoperable and operable, respectively, is provided. As illustrated inFIG. 5 , at rest, the lower portion of the integrated eccentricflywheel oil slinger 118 resides in thelubricating oil 116 present within theoil sump 114. In an embodiment, a portion of the first or second apertures present within the generally cylindricalmain body 126 may also contact the lubricatingoil 116. - As illustrated in
FIG. 6 , the supplying of electrical power to theair compressor assembly 100 results in the oil level within theoil sump 114 dropping whereby the lower portion of the integrated eccentricflywheel oil slinger 118 remains in the oil, but the apertures no longer make such contact as oil is slung. During operation of theair compressor 104, rotation of thecrankshaft assembly 112 rotates the integrated eccentricflywheel oil slinger 118 for splashinglubricating oil 116 from theoil sump 114 onto components of theair compressor 104 being lubricated (e.g.,crankshaft assembly 112,piston 108, cylinder/cylinder wall 106, and the like). As shown, the integrated eccentricflywheel oil slinger 118 is generally centered coaxially with the center of rotation of thecrankshaft assembly 112 so that rotation of thecrankshaft assembly 112 causes the integrated eccentricflywheel oil slinger 118 to rotate about the center of rotation of the crankshaft. Thus, during operation, the lower portion of the integrated eccentricflywheel oil slinger 118 is continuously submerged in lubricatingoil 116 contained in theoil sump 114. - Since the lower portion of the integrated eccentric
flywheel oil slinger 118 remains in theoil 116 instead of cyclically entering and exiting theoil 116, as does a conventional dipstick or dipper oil slinger, the volume ofoil 116 in theoil sump 114 that the integrated eccentricflywheel oil slinger 118 displaces does not change during each revolution of thecrankshaft assembly 112. Further, the integrated eccentricflywheel oil slinger 118, being a continuous disk, does not have a high speed advancing edge that must pass through the lubricatingoil 116 as do dipper slingers. Thus, the flow of lubricatingoil 116 over the surface of the integrated eccentricflywheel oil slinger 118 as it advances through theoil sump 114 is substantially more laminar than is possible with intermittent dipper slingers. As a result, the integrated eccentricflywheel oil slinger 118 of the present invention is capable of movinglubricating oil 116 about thecrankcase 110 with substantially less atomization of theoil 116. - 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 118 is continuously submerged in thelubricating oil 116 contained in theoil sump 114, and the submerged surface area of the integrated eccentricflywheel oil slinger 118 is substantially larger than that of the dipper of a dipper oil slinger, the oil flow rate of the integrated eccentricflywheel oil slinger 118 of the present invention is significantly greater than that of an intermittent dipper slinger. - In addition, the volume of oil circulated by the integrated eccentric
flywheel oil slinger 118 is significantly increased by increasing the width of the generally cylindricalmain body 126. In an embodiment, the width of the generally cylindrical main body is approximately 0.813 inches compared to the traditionally narrow prior art disk slingers generally 0.033 inches in width. The increased width increase the volume of oil circulated by the integrated eccentricflywheel oil slinger 118 which improves the cooling capability of oil flow in thecrankcase 110. - In additional embodiments, the
air compressor assembly 100 may include a direct drive air compressor. Such assembly may also include apiston 108 with a large diameter (e.g., two inches and seven eighths of an inch) operationally coupled to the integrated eccentricflywheel oil slinger 118 to maximize piston cooling and enable a compressor to operate at higher pressures than compared to a similar direct drive air compressor assembly including a standard/average sized piston (e.g. piston diameter ranging from two inches to two inches and three eighths of an inch). As operating pressure and compression ratio of a compressor increase, compression chamber temperature increases and if not compensated for may lead to a thermal breakdown of the oil residue in the chamber causing unwanted oil residue deposits on compressor valves as well as on a checkvalve in the storage reservoir. Oil cooling of the piston and compression chamber is proportional to the surface area of the piston which is proportional to the piston diameter. Thus, a small piston diameter (e.g., piston diameter ranging from two inches to two inches and three eighths of an inch) reduces the effectiveness of the integrated eccentric flywheel oil slinger. Therefore, the combination of an integrated eccentricflywheel oil slinger 118 with an increased width and apiston 108 with a large diameter (e.g. two inches and seven eighths of an inch) may be used to maximize piston and compression chamber cooling and enable the compressor to operate at higher pressures. - Referring now to
FIG. 7 , theair compressor 104 shown inFIG. 1 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 thecrankcase 110 is tilted, the surface of the lubricatingoil 116 inoil sump 114 remains substantially horizontal. As shown, the integrated eccentricflywheel oil slinger 118 is generally centered coaxially with the center of rotation of thecrankshaft assembly 112 so that rotation of thecrankshaft assembly 112 causes the integrated eccentric flywheel oil slinger to rotate 360° (three hundred and sixty degrees) about the center of rotation of thecrankshaft 122. As a result, the integrate eccentricflywheel oil slinger 118 remains at least partially submerged in theoil sump 114 if thecrankcase 110 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 integrated eccentricflywheel oil slinger 118 may vary depending on the design ofcrankcase 110, and is limited only by the possibility of lubricatingoil 116 from theoil sump 114 entering thecylinder 106. However, it is contemplated that degrees of tilt (α) of up to or even greater than 90° (ninety degrees) (e.g., thecrankcase 110 is tilted on its side) are possible. - It is contemplated that the instant integrated eccentric flywheel oil slinger may be employed in an air compressor having two or more cylinder/piston assemblies. In an embodiment, the cylinder assemblies are configured such that a single integrated eccentric
flywheel oil slinger 118 is sufficient to provide lubrication to both assemblies. For example, cylinder assemblies may be oriented at an angle of approximately ninety degrees to one another and spaced so that they overlap thereby allowing a single plane, generally coaxial with the integrated eccentricflywheel oil slinger 118, to intersect both cylinder assemblies. - Moreover, in other embodiments, air compressors may be provided having multiple cylinder/piston assemblies that are lubricated by two or more integrated eccentric flywheel oil slingers in accordance with the present invention. For example, as illustrated in
FIG. 8 , two integrated eccentric flywheel oil slingers are present to lubricate the multiple cylinder/piston assemblies present within a direct drive air compressor assembly. Again, such embodiments is contemplated to be within the scope and spirit of the present invention. - It is believed that the present invention and many of its attendant advantages will be understood by the foregoing 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 (20)
1. An integrated eccentric flywheel oil slinger for an oil lubricated compressor crankcase, comprising:
a generally cylindrical main body being configured to provide oil to components of the compressor crankcase and to reduce vibrations caused by such components; and
an eccentric extension protruding from the generally cylindrical main body being configured to move about a crankshaft,
wherein the generally cylindrical main body is configured to counter balance the eccentric extension protruding from the generally cylindrical main body and when attached to the crankshaft provides oil to components of the compressor crankcase to cool such components and reduces vibrations generated by the components of the compressor crankcase.
2. The integrated eccentric flywheel oil slinger as claimed in claim 1 , wherein the generally cylindrical main body is configured to counter balance the eccentric extension protruding from the generally cylindrical main body by including a first aperture in the general shape of a first tear drop which extends through the generally cylindrical main body and a second aperture in the general shape of a second tear drop which extends through the generally cylindrical main body.
3. The integrated eccentric flywheel oil slinger as claimed in claim 2 , wherein the first aperture is positioned on a first side of the eccentric extension and the second aperture is placed on a second side of the eccentric extension, the second side being generally opposite to the first side.
4. The integrated eccentric flywheel oil slinger as claimed in claim 3 , wherein the leading edge of the first tear drop providing the first aperture is formed by an apex of the first tear drop and the leading edge of the second tear drop providing the second aperture is formed by a base of the second tear drop.
5. The integrated eccentric flywheel oil slinger as claimed in claim 1 , wherein the generally cylindrical main body is configured to counter balance the eccentric extension protruding from the generally cylindrical main body by including a first recess generally shaped as a first tear drop and a second recess generally shaped as a second tear drop.
6. The integrated eccentric flywheel oil slinger as claimed in claim 1 , wherein the width of the generally cylindrical main body is approximately 0.813 (eight hundred and thirteen hundredths) inches.
7. The integrated eccentric flywheel oil slinger as claimed in claim 1 , wherein the width of the generally cylindrical main body is approximately 2.5 times the width of an average flywheel for a standard oil lubricated compressor crankcase to provide an increase in the volume of oil circulated by the integrated eccentric flywheel oil slinger
8. The oil lubricated air compressor assembly as claimed in claim 1 , wherein the integrated eccentric flywheel oil slinger is powdered metal.
9. An oil lubricated air compressor assembly, comprising:
an air storage tank for storing air 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 an integrated eccentric flywheel oil slinger positioned below the cylinder, the integrated eccentric flywheel oil slinger disk shaped oil including:
a generally cylindrical main body being configured to provide oil to the cylinder and the piston and reduce vibrations caused by the piston, the generally cylindrical main body including an aperture for coupling with the crankshaft assembly and an eccentric extension protruding from the generally cylindrical main body being configured to move about 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 integrated eccentric flywheel oil slinger for splashing lubricating oil from the oil sump onto the cylinder and piston.
10. The oil lubricated air compressor assembly as claimed in claim 9 , wherein the generally cylindrical main body is configured to counter balance the eccentric extension protruding from the generally cylindrical main body by including a first aperture in the general shape of a first tear drop which extends through the generally cylindrical main body and a second aperture in the general shape of a second tear drop which extends through the generally cylindrical main body.
11. The oil lubricated air compressor assembly as claimed in claim 10 , wherein the first aperture is positioned on a first side of the eccentric extension and the second aperture is placed on a second side of the eccentric extension, the second side being generally opposite to the first side.
12. The oil lubricated air compressor assembly as claimed in claim 11 , wherein the leading edge of the first tear drop providing the first aperture is formed by an apex of the first tear drop and the leading edge of the second tear drop providing the second aperture is formed by a base of the second tear drop.
13. The oil lubricated air compressor assembly as claimed in claim 9 , wherein the generally cylindrical main body is configured to counter balance the eccentric extension protruding from the generally cylindrical main body by including a first recess generally shaped as a first tear drop and a second recess generally shaped as a second tear drop.
14. The oil lubricated air compressor assembly as claimed in claim 9 , wherein the generally cylindrical main body is partially curved so that the body is concave towards the eccentric extension so that the generally cylindrical main body counter balances the eccentric extension.
15. The oil lubricated air compressor assembly as claimed in claim 9 , wherein the width of the generally cylindrical main body is approximately 0.813 inches.
16. The oil lubricated air compressor assembly as claimed in claim 9 , wherein the integrated eccentric flywheel oil slinger is powdered metal.
17. The oil lubricated air compressor assembly as claimed in claim 9 , wherein the air compressor is direct drive.
18. An oil lubricated air compressor assembly, comprising:
an air storage tank for storing air 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 being direct drive and 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 an integrated eccentric flywheel oil slinger positioned below the cylinder, the integrated eccentric flywheel oil slinger disk shaped oil including:
a generally cylindrical main body being configured to provide oil to the cylinder and the piston and reduce vibrations caused by the piston, the generally cylindrical main body including a crankshaft aperture for coupling with the crankshaft assembly; an eccentric extension protruding from the generally cylindrical main body being configured to move about the crankshaft assembly; and a first aperture and a second aperture defined within the main body for counterbalancing the weight of the eccentric extension, the first aperture in the general shape of a first tear drop which extends through the generally cylindrical main body and the second aperture in the general shape of a second tear drop which extends through the generally cylindrical main body; the first aperture being positioned on a first side of the eccentric extension and the second aperture being positioned on a second side of the eccentric extension, the second side being generally opposite to the first side; 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 integrated eccentric flywheel oil slinger for splashing lubricating oil from the oil sump onto the cylinder and piston.
19. The oil lubricated air compressor assembly as claimed in claim 18 , wherein the leading edge of the first tear drop providing the first aperture is formed by the apex of the first tear drop and the leading edge of the second tear drop providing the second aperture is formed by the base of the second tear drop.
20. The oil lubricated air compressor assembly as claimed in claim 18 , wherein the integrated eccentric flywheel oil slinger is powdered metal.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/120,151 US20060104838A1 (en) | 2004-04-30 | 2005-05-02 | Integrated eccentric flywheel oil slinger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US56713804P | 2004-04-30 | 2004-04-30 | |
US11/120,151 US20060104838A1 (en) | 2004-04-30 | 2005-05-02 | Integrated eccentric flywheel oil slinger |
Publications (1)
Publication Number | Publication Date |
---|---|
US20060104838A1 true US20060104838A1 (en) | 2006-05-18 |
Family
ID=36386524
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/120,151 Abandoned US20060104838A1 (en) | 2004-04-30 | 2005-05-02 | Integrated eccentric flywheel oil slinger |
Country Status (1)
Country | Link |
---|---|
US (1) | US20060104838A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1832748A1 (en) * | 2006-03-08 | 2007-09-12 | Turanair Systems Inc. | Portable compressor |
WO2008118625A2 (en) | 2007-03-23 | 2008-10-02 | Fairfield Manufacturing Company | Lubrication system for right-angle drives used with utility vehicles |
EP1947335A3 (en) * | 2007-01-17 | 2010-03-17 | Officine Mario Dorin S.p.A | Reciprocating compressor, in particular of the semi-hermetic type |
US20110000394A1 (en) * | 2008-02-18 | 2011-01-06 | Daisuke Miki | Railway vehicle drive unit |
US20110017168A1 (en) * | 2009-07-24 | 2011-01-27 | Briggs & Stratton Corporation | Weighted centrifugal clutch |
Citations (40)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US186362A (en) * | 1877-01-16 | Aabom j | ||
US441093A (en) * | 1890-11-18 | Steam-engine lubricator | ||
US1097315A (en) * | 1913-07-07 | 1914-05-19 | William S Harley | Engine. |
US1262798A (en) * | 1916-10-07 | 1918-04-16 | R W Phelps | Lubricating means. |
US1270606A (en) * | 1917-02-12 | 1918-06-25 | Homer Laughlin Engineers Corp | Lubricating system. |
US1336076A (en) * | 1919-10-07 | 1920-04-06 | Ellmauer Josef | Automatic sealer and lubricator for refrigerating-compressors |
US1687395A (en) * | 1926-07-21 | 1928-10-09 | Delco Light Co | Refrigerating apparatus |
US1722800A (en) * | 1921-06-18 | 1929-07-30 | Sunbeam Electric Mfg Company | Rotating assembly |
US1881149A (en) * | 1931-01-06 | 1932-10-04 | Ellingwood H Towle | Hydrocarbon engine |
US2163391A (en) * | 1937-03-06 | 1939-06-20 | Westinghouse Air Brake Co | Fluid compressor |
US2280296A (en) * | 1940-06-14 | 1942-04-21 | American Brake Shoe & Foundry | Lubricating system for compressors or the like |
US2606796A (en) * | 1948-05-28 | 1952-08-12 | John H Helms | Centrifugal flow self-lubricating journal box and bearing |
US2760720A (en) * | 1953-04-28 | 1956-08-28 | Richardson Lomer Lee | Oil feeder device |
US3144097A (en) * | 1962-08-30 | 1964-08-11 | Briggs & Stratton Corp | Oil slinger |
US3258992A (en) * | 1963-02-15 | 1966-07-05 | John L Hittell | Reciprocating piston engines |
US3675630A (en) * | 1970-07-02 | 1972-07-11 | Cleo C Stratton | Engine |
US3777622A (en) * | 1972-03-24 | 1973-12-11 | Gen Motors Corp | Pumps and motors |
US4000982A (en) * | 1975-04-10 | 1977-01-04 | Taiho Kogyo Co., Ltd. | Bearing material |
US4090588A (en) * | 1976-09-17 | 1978-05-23 | Ingersoll-Rand Company | Means for lubricating machine components |
US4424772A (en) * | 1981-11-03 | 1984-01-10 | Porter Gary N | Internal combustion engine valve actuating cam |
US4741303A (en) * | 1986-10-14 | 1988-05-03 | Tecumseh Products Company | Combination counterbalance and oil slinger for horizontal shaft engines |
US5088285A (en) * | 1989-06-05 | 1992-02-18 | Wagner & Middlebrook | Internal combustion engine |
US5137434A (en) * | 1990-10-04 | 1992-08-11 | Devilbiss Air Power Company | Universal motor oilless air compressor |
US5190121A (en) * | 1991-10-31 | 1993-03-02 | General Motors Corporation | Two phase compressor lubrication |
US5261380A (en) * | 1992-07-15 | 1993-11-16 | Ford Motor Company | Crankcase ventilation system for automotive engine |
US5375564A (en) * | 1989-06-12 | 1994-12-27 | Gail; Josef | Rotating cylinder internal combustion engine |
US5588408A (en) * | 1994-12-22 | 1996-12-31 | Ryobi Limited | Engine unit |
US5638796A (en) * | 1994-06-03 | 1997-06-17 | Adams, Iii; Herbert L. | Electric supercharger |
US5724934A (en) * | 1993-10-26 | 1998-03-10 | Faraci; John A. | Modular rotary engine, and oil slinger and race seal subassemblies thereof |
US5806403A (en) * | 1990-01-04 | 1998-09-15 | Johnston; Barry | Multicylinder self-starting uniflow engine |
US5857441A (en) * | 1996-10-29 | 1999-01-12 | Honda Giken Kogyo Kabushiki Kaisha | Valve mechanism lubricator of engine |
US5860403A (en) * | 1996-10-09 | 1999-01-19 | Honda Giken Kogyo Kagushiki Kaisha | System for producing lubricating oil mist in engine |
US6216649B1 (en) * | 1999-05-19 | 2001-04-17 | Adventech Corporation | Low emission two-cycle internal combustion engine for powering a portable tool |
US6220216B1 (en) * | 1998-07-30 | 2001-04-24 | Andreas Stihl Ag & Co. | Four-stroke reciprocating internal combustion engine |
US6460656B1 (en) * | 2000-03-27 | 2002-10-08 | Flowserve Management Company | Dilating lubricant flinger |
US20020170781A1 (en) * | 2001-05-18 | 2002-11-21 | Burkholder Robert F. | Disk oil slinger assembly |
US6510829B2 (en) * | 2000-03-21 | 2003-01-28 | Honda Giken Kogyo Kabushiki Kaisha | Handheld type four-cycle engine |
US6577089B1 (en) * | 1998-10-28 | 2003-06-10 | Aspen Motion Technologies, Inc. | Pressure control system using input current sensing |
US20030116107A1 (en) * | 1999-02-05 | 2003-06-26 | Franz Laimbock | Two-stroke internal combustion engine with crankcase scavenging |
US6991574B2 (en) * | 2004-01-08 | 2006-01-31 | Arvinmeritor Technology, Llc | Dual level oil impeller for drive axle assembly |
-
2005
- 2005-05-02 US US11/120,151 patent/US20060104838A1/en not_active Abandoned
Patent Citations (40)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US186362A (en) * | 1877-01-16 | Aabom j | ||
US441093A (en) * | 1890-11-18 | Steam-engine lubricator | ||
US1097315A (en) * | 1913-07-07 | 1914-05-19 | William S Harley | Engine. |
US1262798A (en) * | 1916-10-07 | 1918-04-16 | R W Phelps | Lubricating means. |
US1270606A (en) * | 1917-02-12 | 1918-06-25 | Homer Laughlin Engineers Corp | Lubricating system. |
US1336076A (en) * | 1919-10-07 | 1920-04-06 | Ellmauer Josef | Automatic sealer and lubricator for refrigerating-compressors |
US1722800A (en) * | 1921-06-18 | 1929-07-30 | Sunbeam Electric Mfg Company | Rotating assembly |
US1687395A (en) * | 1926-07-21 | 1928-10-09 | Delco Light Co | Refrigerating apparatus |
US1881149A (en) * | 1931-01-06 | 1932-10-04 | Ellingwood H Towle | Hydrocarbon engine |
US2163391A (en) * | 1937-03-06 | 1939-06-20 | Westinghouse Air Brake Co | Fluid compressor |
US2280296A (en) * | 1940-06-14 | 1942-04-21 | American Brake Shoe & Foundry | Lubricating system for compressors or the like |
US2606796A (en) * | 1948-05-28 | 1952-08-12 | John H Helms | Centrifugal flow self-lubricating journal box and bearing |
US2760720A (en) * | 1953-04-28 | 1956-08-28 | Richardson Lomer Lee | Oil feeder device |
US3144097A (en) * | 1962-08-30 | 1964-08-11 | Briggs & Stratton Corp | Oil slinger |
US3258992A (en) * | 1963-02-15 | 1966-07-05 | John L Hittell | Reciprocating piston engines |
US3675630A (en) * | 1970-07-02 | 1972-07-11 | Cleo C Stratton | Engine |
US3777622A (en) * | 1972-03-24 | 1973-12-11 | Gen Motors Corp | Pumps and motors |
US4000982A (en) * | 1975-04-10 | 1977-01-04 | Taiho Kogyo Co., Ltd. | Bearing material |
US4090588A (en) * | 1976-09-17 | 1978-05-23 | Ingersoll-Rand Company | Means for lubricating machine components |
US4424772A (en) * | 1981-11-03 | 1984-01-10 | Porter Gary N | Internal combustion engine valve actuating cam |
US4741303A (en) * | 1986-10-14 | 1988-05-03 | Tecumseh Products Company | Combination counterbalance and oil slinger for horizontal shaft engines |
US5088285A (en) * | 1989-06-05 | 1992-02-18 | Wagner & Middlebrook | Internal combustion engine |
US5375564A (en) * | 1989-06-12 | 1994-12-27 | Gail; Josef | Rotating cylinder internal combustion engine |
US5806403A (en) * | 1990-01-04 | 1998-09-15 | Johnston; Barry | Multicylinder self-starting uniflow engine |
US5137434A (en) * | 1990-10-04 | 1992-08-11 | Devilbiss Air Power Company | Universal motor oilless air compressor |
US5190121A (en) * | 1991-10-31 | 1993-03-02 | General Motors Corporation | Two phase compressor lubrication |
US5261380A (en) * | 1992-07-15 | 1993-11-16 | Ford Motor Company | Crankcase ventilation system for automotive engine |
US5724934A (en) * | 1993-10-26 | 1998-03-10 | Faraci; John A. | Modular rotary engine, and oil slinger and race seal subassemblies thereof |
US5638796A (en) * | 1994-06-03 | 1997-06-17 | Adams, Iii; Herbert L. | Electric supercharger |
US5588408A (en) * | 1994-12-22 | 1996-12-31 | Ryobi Limited | Engine unit |
US5860403A (en) * | 1996-10-09 | 1999-01-19 | Honda Giken Kogyo Kagushiki Kaisha | System for producing lubricating oil mist in engine |
US5857441A (en) * | 1996-10-29 | 1999-01-12 | Honda Giken Kogyo Kabushiki Kaisha | Valve mechanism lubricator of engine |
US6220216B1 (en) * | 1998-07-30 | 2001-04-24 | Andreas Stihl Ag & Co. | Four-stroke reciprocating internal combustion engine |
US6577089B1 (en) * | 1998-10-28 | 2003-06-10 | Aspen Motion Technologies, Inc. | Pressure control system using input current sensing |
US20030116107A1 (en) * | 1999-02-05 | 2003-06-26 | Franz Laimbock | Two-stroke internal combustion engine with crankcase scavenging |
US6216649B1 (en) * | 1999-05-19 | 2001-04-17 | Adventech Corporation | Low emission two-cycle internal combustion engine for powering a portable tool |
US6510829B2 (en) * | 2000-03-21 | 2003-01-28 | Honda Giken Kogyo Kabushiki Kaisha | Handheld type four-cycle engine |
US6460656B1 (en) * | 2000-03-27 | 2002-10-08 | Flowserve Management Company | Dilating lubricant flinger |
US20020170781A1 (en) * | 2001-05-18 | 2002-11-21 | Burkholder Robert F. | Disk oil slinger assembly |
US6991574B2 (en) * | 2004-01-08 | 2006-01-31 | Arvinmeritor Technology, Llc | Dual level oil impeller for drive axle assembly |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1832748A1 (en) * | 2006-03-08 | 2007-09-12 | Turanair Systems Inc. | Portable compressor |
EP1947335A3 (en) * | 2007-01-17 | 2010-03-17 | Officine Mario Dorin S.p.A | Reciprocating compressor, in particular of the semi-hermetic type |
WO2008118625A2 (en) | 2007-03-23 | 2008-10-02 | Fairfield Manufacturing Company | Lubrication system for right-angle drives used with utility vehicles |
US20110000394A1 (en) * | 2008-02-18 | 2011-01-06 | Daisuke Miki | Railway vehicle drive unit |
US20110017168A1 (en) * | 2009-07-24 | 2011-01-27 | Briggs & Stratton Corporation | Weighted centrifugal clutch |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US4637786A (en) | Scroll type fluid apparatus with lubrication of rotation preventing mechanism and thrust bearing | |
CA1245199A (en) | Bearing construction for refrigeration compressor | |
US20060104838A1 (en) | Integrated eccentric flywheel oil slinger | |
KR890000628B1 (en) | Scroll type machine with tilting thrust bearing | |
US4543046A (en) | Rotary compressor | |
JP6554926B2 (en) | Scroll compressor | |
CN211144809U (en) | Main bearing seat assembly and scroll compressor with same | |
KR20050045850A (en) | Fluid compressor | |
EP1258604A1 (en) | Disk oil slinger assembly | |
US20030159888A1 (en) | Disk oil slinger assembly | |
CN111379710A (en) | Centrifugal compressor | |
JP5626041B2 (en) | Reciprocating compressor | |
WO2017183330A1 (en) | Rolling cylinder-type positive displacement compressor | |
CN112412792B (en) | Compressor and refrigeration cycle device with same | |
US6523455B1 (en) | Compressor having an oil collection groove | |
JP2003013856A (en) | Compressor | |
JP2001020864A (en) | Hermetic compressor | |
US20060104839A1 (en) | Air compressor including a disk oil slinger assembly | |
JP2017002743A (en) | Scroll compressor | |
KR100816832B1 (en) | Rotating portion for hermetic compressor | |
JP2006090180A (en) | Hermetic compressor | |
JP5372869B2 (en) | Hermetic compressor and refrigerator using the same | |
JPH09158861A (en) | Scroll compressor | |
JP2008215220A (en) | Compressor | |
JPS59226294A (en) | Oil supplying device for compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: BLACK & DECKER INC., DELAWARE Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WOOD, MARK W.;REEL/FRAME:016296/0056 Effective date: 20050509 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |