Tank dampening device

Abstract

A compressor assembly having a compressed gas tank having a tank dampening device in the form of a vibration absorption member. The vibration absorption member can provide a pressure to a portion of the compressed gas tank. A method of controlling sound emitted from a compressor assembly, by using a vibration absorber which exerts a force upon the compressed gas tank. A means for controlling the sound level of a compressed gas tank by using a means for absorbing vibration from the compressed gas tank which exerts a pressure on a portion of the compressed gas tank.

Description

FIELD OF THE INVENTION

The invention relates to a compressor for air, gas or gas mixtures.

BACKGROUND OF THE INVENTION

Compressors are widely used in numerous applications. Existing compressors can generate a high noise output during operation. This noise can be annoying to users and can be distracting to those in the environment of compressor operation. Non-limiting examples of compressors which generate unacceptable levels of noise output include reciprocating, rotary screw and rotary centrifugal types. Compressors which are mobile or portable and not enclosed in a cabinet or compressor room can be unacceptably noisy. However, entirely encasing a compressor, for example in a cabinet or compressor room, is expensive, prevents mobility of the compressor and is often inconvenient or not feasible. Additionally, such encasement can create heat exchange and ventilation problems. There is a strong and urgent need for a quieter compressor technology.

When a power source for a compressor is electric, gas or diesel, unacceptably high levels of unwanted heat and exhaust gases can be produced. Additionally, existing compressors can be inefficient in cooling a compressor pump and motor. Existing compressors can use multiple fans, e.g. a compressor can have one fan associated with a motor and a different fan associated with a pump. The use of multiple fans adds cost manufacturing difficulty, noise and unacceptable complexity to existing compressors. Current compressors can also have improper cooling gas flow paths which can choke cooling gas flows to the compressor and its components. Thus, there is a strong and urgent need for a more efficient cooling design for compressors.

SUMMARY OF THE INVENTION

In an embodiment, the fastening device disclosed herein can have a compressor assembly, having: a compressed gas tank having a vibration absorption member which dampens sound, and a sound level when in a compressing state which has a value of 75 dBA or less.

The compressor assembly can have a vibration absorption member that applies a pressure to an internal portion of the compressed gas tank. The compressor assembly can have a vibration absorption member that applies a pressure to an external portion of the compressed gas tank. The compressor assembly can have a vibration absorption member in the form of a ring that applies a force against a portion of the compressed gas tank. The compressor assembly can have a vibration absorption member in the form of a ring that applies a constant force against a portion of the compressed gas tank. The vibration dampening material in the compressor assembly can be disposed between the tank and the ring.

The compressor assembly disclosed herein can have a method of controlling sound emitted from a compressor assembly, having the steps of: providing a compressor assembly having a compressed gas tank, providing a vibration absorber which exerts a force upon the compressed gas tank, and controlling the sound level of the compressor assembly when in a compressing state to a value in a range of from 65 dBA to 75 dBA.

The method of controlling sound emitted from a compressor assembly can have a step of compressing a gas at a rate in a range of from 2.4 SCFM to 3.5 SCFM.

The method of controlling sound emitted from a compressor assembly can have a step of operating a motor which drives a pump assembly at a pump speed at a rate in a range of from 1500 rpm to 3000 rpm.

The method of controlling sound emitted from a compressor assembly can have a step of cooling the compressor assembly with a cooling gas at a rate in the range of from 50 CFM to 100 CFM.

The method of controlling sound emitted from a compressor assembly can have a step of compressing a gas to a pressure in a range of from 150 psig to 250 psig.

In an aspect, the compressor assembly can have a means for controlling the sound level of a compressed gas tank which has a means for absorbing vibration from the compressed gas tank, and a means for exerting a pressure on a portion of the compressed gas tank.

The compressor can have a means for absorbing vibration from the compressed gas tank which exerts a pressure on an inside portion of the compressed gas tank.

The compressor can have a means for absorbing vibration from the compressed gas tank which exerts a pressure on an internal portion of the compressed gas tank in a range of from 45 psi to 60 psi. The compressor can have a means for absorbing vibration from the compressed gas tank which exerts a pressure on an external portion of the compressed gas tank in a range of from 45 psi to 60 psi.

The compressor can have a means for absorbing vibration from the compressed gas tank which has a cushion member. The compressor can have a means for absorbing vibration from the compressed gas tank which has a multi-layered cushion member

The compressor can have a means for absorbing vibration from the compressed gas tank which has a dampening ring. The compressor can have a means for absorbing vibration from the compressed gas tank which has a coiled spring absorber

The compressor can have a means for absorbing vibration from the compressed gas tank which can have a dampening band surrounding at least a portion of the compressed gas tank.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention in its several aspects and embodiments solves the problems discussed above and significantly advances the technology of compressors. The present invention can become more fully understood from the detailed description and the accompanying drawings, wherein:

FIG. 1 is a perspective view of a compressor assembly;

FIG. 2 is a front view of internal components of the compressor assembly;

FIG. 3 is a front sectional view of the motor and fan assembly;

FIG. 4 is a pump-side view of components of the pump assembly;

FIG. 5 is a fan-side perspective of the compressor assembly;

FIG. 6 is a rear perspective of the compressor assembly;

FIG. 7 is a rear view of internal components of the compressor assembly;

FIG. 8 is a rear sectional view of the compressor assembly;

FIG. 9 is a top view of components of the pump assembly;

FIG. 10 is a top sectional view of the pump assembly;

FIG. 11 is an exploded view of the air ducting shroud;

FIG. 12 is a rear view of a valve plate assembly;

FIG. 13 is a cross-sectional view of the valve plate assembly;

FIG. 14 is a front view of the valve plate assembly;

FIG. 15A is a perspective view of sound control chambers of the compressor assembly;

FIG. 15B is a perspective view of sound control chambers having optional sound absorbers;

FIG. 16A is a perspective view of sound control chambers with an air ducting shroud;

FIG. 16B is a perspective view of sound control chambers having optional sound absorbers;

FIG. 17 is a first table of embodiments of compressor assembly ranges of performance characteristics;

FIG. 18 is a second table of embodiments of compressor assembly ranges of performance characteristics;

FIG. 19 is a first table of example performance characteristics for an example compressor assembly;

FIG. 20 is a second table of example performance characteristics for an example compressor assembly;

FIG. 21 is a table containing a third example of performance characteristics of an example compressor assembly;

FIG. 22 is a perspective view of a tank shell of a compressed gas tank having a dampening ring;

FIG. 23 is a dampening ring having multi-layered pad;

FIG. 24 is a side view of a shell of a compressed gas tank having a dampening ring;

FIG. 25A is a side view of a dampening ring in an uncompressed state;

FIG. 25B is a side view of a dampening ring in an installed state;

FIG. 25C is a perspective view of a dampening ring in an uncompressed state;

FIG. 25D is an end view of a dampening ring in an uncompressed state;

FIG. 26 is a first open end view of the compressed gas tank with a coiled spring absorber;

FIG. 27 is a second open end view of the compressed gas tank with a coiled spring absorber;

FIG. 28 is a plurality of felt pads between the coiled spring absorber and tank inner surface;

FIG. 29 is a perspective view of a compressed gas tank with an over-molded dampening ring;

FIG. 30 is an example of an over-molded dampening ring;

FIG. 31 is a first perspective view of a compressed gas tank shell with a dampening band;

FIG. 32 is a second perspective view of a compressed gas tank shell with a dampening band;

FIG. 33 is a detail of FIG. 27;

FIG. 34A is a perspective view of a grooved pad;

FIG. 34B is a groove-side view of a grooved pad;

FIG. 34C is an end view of a grooved pad;

FIG. 34D is a side view of a grooved pad;

FIG. 35A is a perspective view of example of a grooved pad in an installed state; and

FIG. 35B is a grooved pad attached to a dampening ring or coil.

Herein, like reference numbers in one figure refer to like reference numbers in another figure.

DETAILED DESCRIPTION OF THE INVENTION

The invention relates to a compressor assembly which can compress air, or gas, or gas mixtures, and which has a low noise output, effective cooling means and high heat transfer. The inventive compressor assembly achieves efficient cooling of the compressor assembly 20 (FIG. 1) and/or pump assembly 25 (FIG. 2) and/or the components thereof (FIGS. 3 and 4). In an embodiment, the compressor can compress air. In another embodiment, the compressor can compress one or more gases, inert gases, or mixed gas compositions. The disclosure herein regarding compression of air is also applicable to the use of the disclosed apparatus in its many embodiments and aspects in a broad variety of services and can be used to compress a broad variety of gases and gas mixtures.

FIG. 1 is a perspective view of a compressor assembly 20 shown according to the invention. In an embodiment, the compressor assembly 20 can compress air, or can compress one or more gases, or gas mixtures. In an embodiment, the compressor assembly 20 is also referred to hearing herein as “a gas compressor assembly” or “an air compressor assembly”.

The compressor assembly 20 can optionally be portable. The compressor assembly 20 can optionally have a handle 29, which optionally can be a portion of frame 10.

In an embodiment, the compressor assembly 20 can have a value of weight between 15 lbs and 100 lbs. In an embodiment, the compressor assembly 20 can be portable and can have a value of weight between 15 lbs and 50 lbs. In an embodiment, the compressor assembly 20 can have a value of weight between 25 lbs and 40 lbs. In an embodiment, the compressor assembly 20 can have a value of weight of, e.g. 38 lbs, or 29 lbs, or 27 lbs, or 25 lbs, or 20 lbs, or less. In an embodiment, frame 10 can have a value of weight of 10 lbs or less. In an embodiment, frame 10 can weigh 5 lbs, or less, e.g. 4 lbs, or 3 lbs, of 2 lbs, or less.

In an embodiment, the compressor assembly 20 can have a front side 12 (“front”), a rear side 13 (“rear”), a fan side 14 (“fan-side”), a pump side 15 (“pump-side”), a top side 16 (“top”) and a bottom side 17 (“bottom”).

The compressor assembly 20 can have a housing 21 which can have ends and portions which are referenced herein by orientation consistently with the descriptions set forth above. In an embodiment, the housing 21 can have a front housing 160, a rear housing 170, a fan-side housing 180 and a pump-side housing 190. The front housing 160 can have a front housing portion 161, a top front housing portion 162 and a bottom front housing portion 163. The rear housing 170 can have a rear housing portion 171, a top rear housing portion 172 and a bottom rear housing portion 173. The fan-side housing 180 can have a fan cover 181 and a plurality of intake ports 182. The compressor assembly can be cooled by air flow provided by a fan 200 (FIG. 3), e.g. cooling air stream 2000 (FIG. 3).

In an embodiment, the housing 21 can be compact and can be molded. The housing 21 can have a construction at least in part of plastic, or polypropylene, acrylonitrile butadiene styrene (ABS), metal, steel, stamped steel, fiberglass, thermoset plastic, cured resin, carbon fiber, or other material. The frame 10 can be made of metal, steel, aluminum, carbon fiber, plastic or fiberglass.

Power can be supplied to the motor of the compressor assembly through a power cord 5 extending through the fan-side housing 180. In an embodiment, the compressor assembly 20 can comprise one or more of a cord holder member, e.g. first cord wrap 6 and second cord wrap 7 (FIG. 2).

In an embodiment, power switch 11 can be used to change the operating state of the compressor assembly 20 at least from an “on” to an “off” state, and vice versa. In an “on” state, the compressor can be in a compressing state (also herein as a “pumping state”) in which it is compressing air, or a gas, or a plurality of gases, or a gas mixture.

In an embodiment, other operating modes can be engaged by power switch 11 or a compressor control system, e.g. a standby mode, or a power save mode. In an embodiment, the front housing 160 can have a dashboard 300 which provides an operator-accessible location for connections, gauges and valves which can be connected to a manifold 303 (FIG. 7). In an embodiment, the dashboard 300 can provide an operator access in non-limiting example to a first quick connection 305, a second quick connection 310, a regulated pressure gauge 315, a pressure regulator 320 and a tank pressure gauge 325. In an embodiment, a compressed gas outlet line, hose or other device to receive compressed gas can be connected the first quick connection 305 and/or second quick connection 310. In an embodiment, as shown in FIG. 1, the frame can be configured to provide an amount of protection to the dashboard 300 from the impact of objects from at least the pump-side, fan-side and top directions.

In an embodiment, the pressure regulator 320 employs a pressure regulating valve. The pressure regulator 320 can be used to adjust the pressure regulating valve 26 (FIG. 7). The pressure regulating valve 26 can be set to establish a desired output pressure. In an embodiment, excess air pressure can be can vented to atmosphere through the pressure regulating valve 26 and/or pressure relief valve 199 (FIG. 1). In an embodiment, pressure relief valve 199 can be a spring loaded safety valve. In an embodiment, the air compressor assembly 20 can be designed to provide an unregulated compressed air output.

In an embodiment, the pump assembly 25 and the compressed gas tank 150 can be connected to frame 10. The pump assembly 25, housing 21 and compressed gas tank 150 can be connected to the frame 10 by a plurality of screws and/or one or a plurality of welds and/or a plurality of connectors and/or fasteners.

The plurality of intake ports 182 can be formed in the housing 21 adjacent the housing inlet end 23 and a plurality of exhaust ports 31 can be formed in the housing 21. In an embodiment, the plurality of the exhaust ports 31 can be placed in housing 21 in the front housing portion 161. Optionally, the exhaust ports 31 can be located adjacent to the pump end of housing 21 and/or the pump assembly 25 and/or the pump cylinder 60 and/or cylinder head 61 (FIG. 2) of the pump assembly 25. In an embodiment, the exhaust ports 31 can be provided in a portion of the front housing portion 161 and in a portion of the bottom front housing portion 163.

The total cross-sectional open area of the intake ports 182 (the sum of the cross-sectional areas of the individual intake ports 182) can be a value in a range of from 3.0 in^2 to 100 in^2. In an embodiment, the total cross-sectional open area of the intake ports 182 can be a value in a range of from 6.0 in^2 to 38.81 in^2. In an embodiment, the total cross-sectional open area of the intake ports 182 can be a value in a range of from 9.8 in^2 to 25.87 in^2. In an embodiment, the total cross-sectional open area of the intake ports 182 can be 12.936 in^2.

In an embodiment, the cooling gas employed to cool compressor assembly 20 and its components can be air (also known herein as “cooling air”). The cooling air can be taken in from the environment in which the compressor assembly 20 is placed. The cooling air can be ambient from the natural environment, or air which has been conditioned or treated. The definition of “air” herein is intended to be very broad. The term “air” includes breathable air, ambient air, treated air, conditioned air, clean room air, cooled air, heated air, non-flammable oxygen containing gas, filtered air, purified air, contaminated air, air with particulates solids or water, air from bone dry (i.e. 0.00 humidity) air to air which is supersaturated with water, as well as any other type of air present in an environment in which a gas (e.g. air) compressor can be used. It is intended that cooling gases which are not air are encompassed by this disclosure. For non-limiting example, a cooling gas can be nitrogen, can comprise a gas mixture, can comprise nitrogen, can comprise oxygen (in a safe concentration), can comprise carbon dioxide, can comprise one inert gas or a plurality of inert gases, or comprise a mixture of gases.

In an embodiment, cooling air can be exhausted from compressor assembly 20 through a plurality of exhaust ports 31. The total cross-sectional open area of the exhaust ports 31 (the sum of the cross-sectional areas of the individual exhaust ports 31) can be a value in a range of from 3.0 in^2 to 100 in^2. In an embodiment, the total cross-sectional open area of the exhaust ports can be a value in a range of from 3.0 in^2 to 77.62 in^2. In an embodiment, the total cross-sectional open area of the exhaust ports can be a value in a range of from 4.0 in^2 to 38.81 in^2. In an embodiment, the total cross-sectional open area of the exhaust ports can be a value in a range of from 4.91 in^2 to 25.87 in^2. In an embodiment, the total cross-sectional open area of the exhaust ports can be 7.238 in^2.

Numeric values and ranges herein, unless otherwise stated, also are intended to have associated with them a tolerance and to account for variances of design and manufacturing, and/or operational and performance fluctuations. Thus, a number disclosed herein is intended to disclose values “about” that number. For example, a value X is also intended to be understood as “about X” Likewise, a range of Y-Z, is also intended to be understood as within a range of from “about Y-about Z”. Unless otherwise stated, significant digits disclosed for a number are not intended to make the number an exact limiting value. Variance and tolerance, as well as operational or performance fluctuations, are an expected aspect of mechanical design and the numbers disclosed herein are intended to be construed to allow for such factors (in non-limiting e.g., ±10 percent of a given value). This disclosure is to be broadly construed. Likewise, the claims are to be broadly construed in their recitations of numbers and ranges.

The compressed gas tank 150 can operate at a value of pressure in a range of at least from ambient pressure, e.g. 14.7 psig to 3000 psig (“psig” is the unit lbf/in^2 gauge), or greater. In an embodiment, compressed gas tank 150 can operate at 200 psig. In an embodiment, compressed gas tank 150 can operate at 150 psig.

In an embodiment, the compressor has a pressure regulated on/off switch which can stop the pump when a set pressure is obtained. In an embodiment, the pump is activated when the pressure of the compressed gas tank 150 falls to 70 percent of the set operating pressure, e.g. to activate at 140 psig with an operating set pressure of 200 psig (140 psig=0.70*200 psig). In an embodiment, the pump is activated when the pressure of the compressed gas tank 150 falls to 80 percent of the set operating pressure, e.g. to activate at 160 psig with an operating set pressure of 200 psig (160 psig=0.80*200 psig). Activation of the pump can occur at a value of pressure in a wide range of set operating pressure, e.g. 25 percent to 99.5 percent of set operating pressure. Set operating pressure can also be a value in a wide range of pressure, e.g. a value in a range of from 25 psig to 3000 psig. An embodiment of set pressure can be 50 psig, 75 psig, 100 psig, 150 psig, 200 psig, 250 psig, 300 psig, 500 psig, 1000 psig, 2000 psig, 3000 psig, or greater than or less than, or a value in between these example numbers.

The compressor assembly 20 disclosed herein in its various embodiments achieves a reduction in the noise created by the vibration of the air tank while the air compressor is running, in its compressing state (pumping state) e.g. to a value in a range of from 60-75 dBA, or less, as measured by ISO3744-1995. Noise values discussed herein are compliant with ISO03744-1995. ISO3744-1995 is the standard for noise data and results for noise data, or sound data, provided in this application. Herein “noise” and “sound” are used synonymously.

The pump assembly 25 can be mounted to an air tank and can be covered with a housing 21. A plurality of optional decorative shapes 141 can be formed on the front housing portion 161. The plurality of optional decorative shapes 141 can also be sound absorbing and/or vibration dampening shapes. The plurality of optional decorative shapes 141 can optionally be used with, or contain at least in part, a sound absorbing material.

FIG. 2 is a front view of internal components of the compressor assembly.

The compressor assembly 20 can include a pump assembly 25. In an embodiment, pump assembly 25 which can compress a gas, air or gas mixture. In an embodiment in which the pump assembly 25 compresses air, it is also referred to herein as air compressor 25, or compressor 25. In an embodiment, the pump assembly 25 can be powered by a motor 33 (e.g. FIG. 3).

FIG. 2 illustrates the compressor assembly 20 with a portion of the housing 21 removed and showing the pump assembly 25. In an embodiment, the fan-side housing 180 can have a fan cover 181 and a plurality of intake ports 182. The cooling gas, such as air, can be fed through an air inlet space 184 which feeds air into the fan 200 (e.g. FIG. 3). In an embodiment, the fan 200 can be housed proximate to an air intake port 186 of an air ducting shroud 485.

Air ducting shroud 485 can have a shroud inlet scoop 484. As illustrated in FIG. 2, air ducting shroud 485 is shown encasing the fan 200 and the motor 33 (FIG. 3). In an embodiment, the shroud inlet scoop 484 can encase the fan 200, or at least a portion of the fan and at least a portion of motor 33. In this embodiment, an air inlet space 184 which feeds air into the fan 200 is shown. The air ducting shroud 485 can encase the fan 200 and the motor 33, or at least a portion of these components.

FIG. 2 is an intake muffler 900 which can receive feed air for compression (also herein as “feed air 990”; e.g. FIG. 8) via the intake muffler feed line 898. The feed air 990 can pass through the intake muffler 900 and be fed to the cylinder head 61 via the muffler outlet line 902. The feed air 990 can be compressed in pump cylinder 60 by piston 63. The piston can be provided with a seal which can function, such as slide, in the cylinder without liquid lubrication. The cylinder head 61 can be shaped to define an inlet chamber 81 (e.g. FIG. 9) and an outlet chamber 82 (e.g. FIG. 8) for a compressed gas, such as air (also known herein as “compressed air 999” or “compressed gas 999”; e.g. FIG. 10). In an embodiment, the pump cylinder 60 can be used as at least a portion of an inlet chamber 81. A gasket can form an air tight seal between the cylinder head 61 and the valve plate assembly 62 to prevent a leakage of a high pressure gas, such as compressed air 999, from the outlet chamber 82. Compressed air 999 can exit the cylinder head 61 via a compressed gas outlet port 782 and can pass through a compressed gas outlet line 145 to enter the compressed gas tank 150.

As shown in FIG. 2, the pump assembly 25 can have a pump cylinder 60, a cylinder head 61, a valve plate assembly 62 mounted between the pump cylinder 60 and the cylinder head 61, and a piston 63 which is reciprocated in the pump cylinder 60 by an eccentric drive 64 (e.g. FIG. 9). The eccentric drive 64 can include a sprocket 49 which can drive a drive belt 65 which can drive a pulley 66. A bearing 67 can be eccentrically secured to the pulley 66 by a screw, or a rod bolt 57, and a connecting rod 69. Preferably, the sprocket 49 and the pulley 66 can be spaced around their perimeters and the drive belt 65 can be a timing belt. The pulley 66 can be mounted about pulley centerline 887 and linked to a sprocket 49 by the drive belt 65 (FIG. 3) which can be configured on an axis which is represent herein as a shaft centerline 886 supported by a bracket and by a bearing 47 (FIG. 3). A bearing can allow the pulley 66 to be rotated about an axis 887 (FIG. 10) when the motor rotates the sprocket 49. As the pulley 66 rotates about the axis 887 (FIG. 10), the bearing 67 (FIG. 2) and an attached end of the connecting rod 69 are moved around a circular path.

The piston 63 can be formed as an integral part of the connecting rod 69. A compression seal can be attached to the piston 63 by a retaining ring and a screw. In an embodiment, the compression seal can be a sliding compression seal.

A cooling gas stream, such as cooling air stream 2000 (FIG. 3), can be drawn through intake ports 182 to feed fan 200. The cooling air stream 2000 can be divided into a number of different cooling air stream flows which can pass through portions of the compressor assembly and exit separately, or collectively as an exhaust air steam through the plurality of exhaust ports 31. Additionally, the cooling gas, e.g. cooling air stream 2000, can be drawn through the plurality of intake ports 182 and directed to cool the internal components of the compressor assembly 20 in a predetermined sequence to optimize the efficiency and operating life of the compressor assembly 20. The cooling air can be heated by heat transfer from compressor assembly 20 and/or the components thereof, such as pump assembly 25 (FIG. 3). The heated air can be exhausted through the plurality of exhaust ports 31.

In an embodiment, one fan can be used to cool both the pump and motor. A design using a single fan to provide cooling to both the pump and motor can require less air flow than a design using two or more fans, e.g. using one or more fans to cool the pump, and also using one or more fans to cool the motor. Using a single fan to provide cooling to both the pump and motor can reduce power requirements and also reduces noise production as compared to designs using a plurality of fans to cool the pump and the motor, or which use a plurality of fans to cool the pump assembly 25, or the compressor assembly 20.

In an embodiment, the fan blade 205 (e.g. FIG. 3) establishes a forced flow of cooling air through the internal housing, such as the air ducting shroud 485. The cooling air flow through the air ducting shroud can be a volumetric flow rate having a value of between 25 CFM to 400 CFM. The cooling air flow through the air ducting shroud can be a volumetric flow rate having a value of between 45 CFM to 125 CFM.

In an embodiment, the outlet pressure of cooling air from the fan can be in a range of from 1 psig to 50 psig. In an embodiment, the fan 200 can be a low flow fan with which generates an outlet pressure having a value in a range of from 1 in of water to 10 psi. In an embodiment, the fan 200 can be a low flow fan with which generates an outlet pressure having a value in a range of from 2 in of water to 5 psi.

In an embodiment, the air ducting shroud 485 can flow 100 CFM of cooling air with a pressure drop of from 0.0002 psi to 50 psi along the length of the air ducting shroud. In an embodiment, the air ducting shroud 485 can flow 75 CFM of cooling air with a pressure drop of 0.028 psi along its length as measured from the entrance to fan 200 through the exit from conduit 253 (FIG. 7).

In an embodiment, the air ducting shroud 485 can flow 75 CFM of cooling air with a pressure drop of 0.1 psi along its length as measured from the outlet of fan 200 through the exit from conduit 253. In an embodiment, the air ducting shroud 485 can flow 100 CFM of cooling air with a pressure drop of 1.5 psi along its length as measured from the outlet of fan 200 through the exit from conduit 253. In an embodiment, the air ducting shroud 485 can flow 150 CFM of cooling air with a pressure drop of 5.0 psi along its length as measured from the outlet of fan 200 through the exit from conduit 253.

In an embodiment, the air ducting shroud 485 can flow 75 CFM of cooling air with a pressure drop in a range of from 1.0 psi to 30 psi across as measured from the outlet of fan 200 across the motor 33.

Depending upon the compressed gas (e.g. compressed air 999) output, the design rating of the motor 33 and the operating voltage. In an embodiment, the motor 33 can operate at a value of rotation (motor speed) between 5,000 rpm and 20,000 rpm. In further embodiments, the motor 33 can operate at a value in a range of between 7,500 rpm and 12,000 rpm. In an embodiment, the motor 33 can operate at e.g.: 11,252 rpm; or 11,000 rpm; or 10,000 rpm; or 9,000 rpm; or 7,500 rpm; or 6,000 rpm; or 5,000 rpm. The pulley 66 and the sprocket 49 can be sized to achieve reduced pump speeds (also herein as “reciprocation rates”, or “piston speed”) at which the piston 63 is reciprocated. For example, if the sprocket 49 can have a diameter of 1 in and the pulley 66 can have a diameter of 4 in, then a motor 33 speed of 14,000 rpm can achieve a reciprocation rate, or a piston speed, of 3,500 strokes per minute. In an embodiment, if the sprocket 49 can have a diameter of 1.053 in and the pulley 66 can have a diameter of 5.151 in, then a motor 33 speed of 11,252 rpm can achieve a reciprocation rate, or a piston speed (pump speed), of 2,300 strokes per minute.

FIG. 3 is a front sectional view of the motor and fan assembly.

FIG. 3 illustrates the fan 200 and motor 33 covered by air ducting shroud 485. The fan 200 is shown proximate to a shroud inlet scoop 484.

The motor can have a stator 37 with an upper pole 38 around which upper stator coil 40 is wound and/or configured. The motor can have a stator 37 with a lower pole 39 around which lower stator coil 41 is wound and/or configured. A shaft 43 can be supported adjacent a first shaft end 44 by a bearing 45 and is supported adjacent to a second shaft end 46 by a bearing 47. A plurality of fan blades 205 can be secured to the fan 200 which can be secured to the first shaft end 44. When power is applied to the motor 33, the shaft 43 rotates at a high speed to in turn drive the sprocket 49 (FIG. 2), the drive belt 65 (FIG. 4), the pulley 66 (FIG. 4) and the fan blade 200. In an embodiment, the motor can be a non-synchronous universal motor. In an embodiment, the motor can be a synchronous motor used.

The compressor assembly 20 can be designed to accommodate a variety of types of motor 33. The motors 33 can come from different manufacturers and can have horsepower ratings of a value in a wide range from small to very high. In an embodiment, a motor 33 can be purchased from the existing market of commercial motors. For example, although the housing 21 is compact, In an embodiment, it can accommodate a universal motor, or other motor type, rated, for example, at ½ horsepower, at ¾ horsepower or 1 horsepower by scaling and/or designing the air ducting shroud 485 to accommodate motors in a range from small to very large.

FIG. 3 and FIG. 4 illustrate the compression system for the compressor which is also referred to herein as the pump assembly 25. The pump assembly 25 can have a pump 59, a pulley 66, drive belt 65 and driving mechanism driven by motor 33. The connecting rod 69 can connect to a piston 63 (e.g. FIG. 10) which can move inside of the pump cylinder 60.

In one embodiment, the pump 59 such as “gas pump” or “air pump” can have a piston 63, a pump cylinder 60, in which a piston 63 reciprocates and a cylinder rod 69 (FIG. 2) which can optionally be oil-less and which can be driven to compress a gas, e.g. air. The pump 59 can be driven by a high speed universal motor, e.g. motor 33 (FIG. 3), or other type of motor.

FIG. 4 is a pump-side view of components of the pump assembly 25. The “pump assembly 25” can have the components which are attached to the motor and/or which serve to compress a gas; which in non-limiting example can comprise the fan, the motor 33, the pump cylinder 60 and piston 63 (and its driving parts), the valve plate assembly 62, the cylinder head 61 and the outlet of the cylinder head 782. Herein, the feed air system 905 system (FIG. 7) is referred to separately from the pump assembly 25.

FIG. 4 illustrates that pulley 66 is driven by the motor 33 using drive belt 65.

FIG. 4 (also see FIG. 10) illustrates an offset 880 which has a value of distance which represents one half (½) of the stroke distance. The offset 880 can have a value between 0.25 in and 6 in, or larger. In an embodiment, the offset 880 can have a value between 0.75 in and 3 in. In an embodiment, the offset 880 can have a value between 1.0 in and 2 in, e.g. 1.25 in. In an embodiment, the offset 880 can have a value of about 0.796 in. In an embodiment, the offset 880 can have a value of about 0.5 in. In an embodiment, the offset 880 can have a value of about 1.5 in.

A stroke having a value in a range of from 0.50 in and 12 in, or larger can be used. A stroke having a value in a range of from 1.5 in and 6 in can be used. A stroke having a value in a range of from 2 in and 4 in can be used. A stroke of 2.5 in can be used. In an embodiment, the stroke can be calculated to equal two (2) times the offset, for example an offset 880 of 0.796 produces a stroke of 2(0.796)=1.592 in. In another example, an offset 880 of 2.25 produces a stroke of 2(2.25)=4.5 in. In yet another example, an offset 880 of 0.5 produces a stroke of 2(0.5)=1.0 in.

The compressed air passes through valve plate assembly 62 and into the cylinder head 61 having a plurality of cooling fins 89. The compressed gas is discharged from the cylinder head 61 through the outlet line 145 which feeds compressed gas to the compressed gas tank 150.

FIG. 4 also identifies the pump-side of upper motor path 268 which can provide cooling air to upper stator coil 40 and lower motor path 278 which can provide cooling to lower stator coil 41.

FIG. 5 illustrates tank seal 600 providing a seal between the housing 21 and compressed gas tank 150 viewed from fan-side 14. FIG. 5 is a fan-side perspective of the compressor assembly 20. FIG. 5 illustrates a fan-side housing 180 having a fan cover 181 with intake ports 182. FIG. 5 also shows a fan-side view of the compressed gas tank 150. Tank seal 600 is illustrated sealing the housing 21 to the compressed gas tank 150. Tank seal 600 can be a one piece member or can have a plurality of segments which form tank seal 600.

FIG. 6 is a rear-side perspective of the compressor assembly 20. FIG. 6 illustrates a tank seal 600 sealing the housing 21 to the compressed gas tank 150.

FIG. 7 is a rear view of internal components of the compressor assembly. In this sectional view, in which the rear housing 170 is not shown, the fan-side housing 180 has a fan cover 181 and intake ports 182. The fan-side housing 180 is configured to feed air to air ducting shroud 485. Air ducting shroud 485 has shroud inlet scoop 484 and conduit 253 which can feed a cooling gas, such as air, to the cylinder head 61 and pump cylinder 60.

FIG. 7 also provides a view of the feed air system 905. The feed air system 905 can feed a feed air 990 through a feed air port 952 for compression in the pump cylinder 60 of pump assembly 25. The feed air port 952 can optionally receive a clean air feed from an inertia filter 949 (FIG. 8). The clean air feed can pass through the feed air port 952 to flow through an air intake hose 953 and an intake muffler feed line 898 to the intake muffler 900. The clean air can flow from the intake muffler 900 through muffler outlet line 902 and cylinder head hose 903 to feed pump cylinder head 61. Noise can be generated by the compressor pump, such as when the piston forces air in and out of the valves of valve plate assembly 62. The intake side of the pump can provide a path for the noise to escape from the compressor which intake muffler 900 can serve to muffle.

The filter distance 1952 between an inlet centerline 1950 of the feed air port 952 and a scoop inlet 1954 of shroud inlet scoop 484 can vary widely and have a value in a range of from 0.5 in to 24 in, or even greater for larger compressor assemblies. The filter distance 1952 between inlet centerline 1950 and inlet cross-section of shroud inlet scoop 484 identified as scoop inlet 1954 can be e.g. 0.5 in, or 1.0 in, or 1.5 in, or 2.0 in, or 2.5 in, or 3.0 in, or 4.0 in, or 5.0 in or 6.0 in, or greater. In an embodiment, the filter distance 1952 between inlet centerline 1950 and inlet cross-section of shroud inlet scoop 484 identified as scoop inlet 1954 can be 1.859 in. In an embodiment, the inertia filter can have multiple inlet ports which can be located at different locations of the air ducting shroud 485. In an embodiment, the inertial filter is separate from the air ducting shroud and its feed is derived from one or more inlet ports.

FIG. 7 illustrates that compressed air can exit the cylinder head 61 via the compressed gas outlet port 782 and pass through the compressed gas outlet line 145 to enter the compressed gas tank 150. FIG. 7 also shows a rear-side view of manifold 303.

FIG. 8 is a rear sectional view of the compressor assembly 20. FIG. 8 illustrates the fan cover 181 having a plurality of intake ports 182. A portion of the fan cover 181 can be extended toward the shroud inlet scoop 484, e.g. the rim 187. In this embodiment, the fan cover 181 has a rim 187 which can eliminate a visible line of sight to the air inlet space 184 from outside of the housing 21. In an embodiment, the rim 187 can cover or overlap an air space 188. FIG. 8 illustrates an inertia filter 949 having an inertia filter chamber 950 and air intake path 922.

In an embodiment, the rim 187 can extend past the air inlet space 184 and overlaps at least a portion of the shroud inlet scoop 484. In an embodiment, the rim 187 does not extend past and does not overlap a portion of the shroud inlet scoop 484 and the air inlet space 184 can have a width between the rim 187 and a portion of the shroud inlet scoop 484 having a value of distance in a range of from 0.1 in to 2 in, e.g. 0.25 in, or 0.5 in. In an embodiment, the air ducting shroud 485 and/or the shroud inlet scoop 484 can be used to block line of sight to the fan 200 and the pump assembly 25 in conjunction with or instead of the rim 187.

The inertia filter 949 can provide advantages over the use of a filter media which can become plugged with dirt and/or particles and which can require replacement to prevent degrading of compressor performance. Additionally, filter media, even when it is new, creates a pressure drop and can reduce compressor performance.

Air must make a substantial change in direction from the flow of cooling air to become compressed gas feed air to enter and pass through the feed air port 952 to enter the air intake path 922 from the inertia filter chamber 950 of the inertia filter 949. Any dust and other particles dispersed in the flow of cooling air have sufficient inertia that they tend to continue moving with the cooling air rather than change direction and enter the air intake path 922.

FIG. 8 also shows a section of a dampening ring 700. The dampening ring 700 can optionally have a cushion member 750, as well as optionally a first hook 710 and a second hook 720.

FIG. 9 is a top view of the components of the pump assembly 25.

Pump assembly 25 can have a motor 33 which can drive the shaft 43 which causes a sprocket 49 to drive a drive belt 65 to rotate a pulley 66. The pulley 66 can be connected to and can drive the connecting rod 69 which has a piston 63 (FIG. 2) at an end. The piston 63 can compress a gas in the pump cylinder 60 pumping the compressed gas through the valve plate assembly 62 into the cylinder head 61 and then out through a compressed gas outlet port 782 through an outlet line 145 and into the compressed gas tank 150.

FIG. 9 also shows a pump 91. Herein, pump 91 collectively refers to a combination of parts including the cylinder head 61, the pump cylinder 60, the piston 63 and the connecting rod having the piston 63, as well as the components of these parts.

FIG. 10 is a top sectional view of the pump assembly 25. FIG. 10 also shows a shaft centerline 886, as well as pulley centerline 887 and a rod bolt centerline 889 of a rod bolt 57. FIG. 10 illustrates an offset 880 which can be a dimension having a value in the range of 0.5 in to 12 in, or greater. In an embodiment, the stroke can be 1.592 in, from an offset 880 of 0.796 in. FIG. 10 also shows air inlet chamber 81.

FIG. 11 illustrates an exploded view of the air ducting shroud 485. In an embodiment, the air ducting shroud 485 can have an upper ducting shroud 481 and a lower ducting shroud 482. In the example of FIG. 11, the upper ducting shroud 481 and the lower ducting shroud 482 can be fit together to shroud the fan 200 and the motor 33 and can create air ducts for cooling pump assembly 25 and/or the compressor assembly 20. In an embodiment, the air ducting shroud 485 can also be a motor cover for motor 33. The upper air ducting shroud 481 and the lower air ducting shroud 482 can be connected by a broad variety of means which can include snaps and/or screws.

FIG. 12 is a rear-side view of a valve plate assembly. A valve plate assembly 62 is shown in detail in FIGS. 12, 13 and 14.

The valve plate assembly 62 of the pump assembly 25 can include air intake and air exhaust valves. The valves can be of a reed, flapper, one-way or other type. A restrictor can be attached to the valve plate adjacent the intake valve. Deflection of the exhaust valve can be restricted by the shape of the cylinder head which can minimize valve impact vibrations and corresponding valve stress.

The valve plate assembly 62 has a plurality of intake ports 103 (five shown) which can be closed by the intake valves 96 (FIG. 14) which can extend from fingers 105 (FIG. 13). In an embodiment, the intake valves 96 can be of the reed or “flapper” type and are formed, for example, from a thin sheet of resilient stainless steel. Radial fingers 113 (FIG. 12) can radiate from a valve finger hub 114 to connect the plurality of valve members 104 of intake valves 96 and to function as return springs. A rivet 107 secures the hub 106 (e.g. FIG. 13) to the center of the valve plate 95. An intake valve restrictor 108 can be clamped between the rivet 107 and the hub 106. The surface 109 terminates at an edge 110 (FIGS. 13 and 14). When air is drawn into the pump cylinder 60 during an intake stroke of the piston 63, the radial fingers 113 can bend and the plurality of valve members 104 separate from the valve plate assembly 62 to allow air to flow through the intake ports 103.

FIG. 13 is a cross-sectional view of the valve plate assembly and FIG. 14 is a front-side view of the valve plate assembly. The valve plate assembly 62 includes a valve plate 95 which can be generally flat and which can mount a plurality of intake valves 96 (FIG. 14) and a plurality of outlet valves 97 (FIG. 12). In an embodiment, the valve plate assembly 62 (FIGS. 10 and 12) can be clamped to a bracket by screws which can pass through the cylinder head 61 (e.g. FIG. 2), the gasket and a plurality of through holes 99 in the valve plate assembly 62 and engage a bracket. A valve member 112 of the outlet valve 97 can cover an exhaust port 111. A cylinder flange and a gas tight seal can be used in closing the cylinder head assembly. In an embodiment, a flange and seal can be on a cylinder side (herein front-side) of a valve plate assembly 62 and a gasket can be between the valve plate assembly 62 and the cylinder head 61.

FIG. 14 illustrates the front side of the valve plate assembly 62 which can have a plurality of exhaust ports 111 (three shown) which are normally closed by the outlet valves 97. A plurality of a separate circular valve member 112 can be connected through radial fingers 113 (FIG. 12) which can be made of a resilient material to a valve finger hub 114. The valve finger hub 114 can be secured to the rear side of the valve plate assembly 62 by the rivet 107. Optionally, the cylinder head 61 can have a head rib 118 (FIG. 13) which can project over and can be spaced a distance from the valve members 112 to restrict movement of the exhaust valve members 112 and to lessen and control valve impact vibrations and corresponding valve stress.

FIG. 15A is a perspective view of a plurality of sound control chambers of an embodiment of the compressor assembly 20. FIG. 15A illustrates an embodiment having four (4) sound control chambers. The number of sound control chambers can vary widely in a range of from one to a large number, e.g. 25, or greater. In a non-limiting example, in an embodiment, a compressor assembly 20 can have a fan sound control chamber 550 (also herein as “fan chamber 550”), a pump sound control chamber 491 (also herein as “pump chamber 491”), an exhaust sound control chamber 555 (also herein as “exhaust chamber 555”), and an upper sound control chamber 480 (also herein as “upper chamber 480”).

FIG. 15B is a perspective view of sound control chambers having optional sound absorbers. The optional sound absorbers can be used to line the inner surface of housing 21, as well as both sides of partitions which are within the housing 21 of the compressor assembly 20.

FIG. 16A is a perspective view of sound control chambers with an air ducting shroud 485. FIG. 16A illustrates the placement of air ducting shroud 485 in coordination with such as the fan chamber 550, the pump sound control chamber 491, the exhaust sound control chamber 555, and the upper sound control chamber 480.

FIG. 16B is a perspective view of sound control chambers having optional sound absorbers. The optional sound absorbers can be used to line the inner surface of housing 21, as well as both sides of partitions which are within the housing 21 of compressor assembly 20.

FIG. 17 is a first table of embodiments of compressor assembly range of performance characteristics. The compressor assembly 20 can have values of performance characteristics as recited in FIG. 17 which are within the ranges set forth in FIG. 17.

FIG. 18 is a second table of embodiments of ranges of performance characteristics for the compressor assembly 20. The compressor assembly 20 can have values of performance characteristics as recited in FIG. 18 which are within the ranges set forth in FIG. 18.

The compressor assembly 20 achieves efficient heat transfer. The heat transfer rate can have a value in a range of from 25 BTU/min to 1000 BTU/min. The heat transfer rate can have a value in a range of from 90 BTU/min to 500 BTU/min. In an embodiment, the compressor assembly 20 can exhibit a heat transfer rate of 200 BTU/min. The heat transfer rate can have a value in a range of from 50 BTU/min to 150 BTU/min. In an embodiment, the compressor assembly 20 can exhibit a heat transfer rate of 135 BTU/min. In an embodiment, the compressor assembly 20 exhibited a heat transfer rate of 84.1 BTU/min.

The heat transfer rate of a compressor assembly 20 can have a value in a range of 60 BTU/min to 110 BTU/min. In an embodiment of the compressor assembly 20, the heat transfer rate can have a value in a range of 66.2 BTU/min to 110 BTU/min; or 60 BTU/min to 200 BTU/min.

The compressor assembly 20 can have noise emissions reduced by, for example, slower fan and/or slower motor speeds, use of a check valve muffler, use of tank vibration dampeners, use of tank sound dampeners, use of a tank dampening ring, use of tank vibration absorbers to dampen noise to and/or from the tank walls which can reduce noise. In an embodiment, a two stage intake muffler can be used on the pump. A housing having reduced or minimized openings can reduce noise from the compressor assembly. As disclosed herein, the elimination of line of sight to the fan and other components as attempted to be viewed from outside of the compressor assembly 20 can reduce noise generated by the compressor assembly. Additionally, routing cooling air through ducts, using foam lined paths and/or routing cooling air through tortuous paths can reduce noise generation by the compressor assembly 20.

Additionally, noise can be reduced from the compressor assembly 20 and its sound level lowered by one or more of the following, employing slower motor speeds, using a check valve muffler and/or using a material to provide noise dampening of the housing 21 and its partitions and/or the compressed air tank 150 heads and shell. Other noise dampening features can include one or more of the following and be used with or apart from those listed above, using a two-stage intake muffler in the feed to a feed air port 952, elimination of line of sight to the fan and/or other noise generating parts of the compressor assembly 20, a quiet fan design and/or routing cooling air routed through a tortuous path which can optionally be lined with a sound absorbing material, such as a foam. Optionally, fan 200 can be a fan which is separate from the shaft 43 and can be driven by a power source which is not shaft 43.

In an example, an embodiment of compressor assembly 20 achieved a decibel reduction of 7.5 dBA. In this example, noise output when compared to a pancake compressor assembly was reduced from about 78.5 dBA to about 71 dBA.

Example 1

FIG. 19 is a first table of example performance characteristics for an example embodiment. FIG. 19 contains combinations of performance characteristics exhibited by an embodiment of compressor assembly 20.

Example 2

FIG. 20 is a second table of example performance characteristics for an example embodiment. FIG. 20 contains combinations of further performance characteristics exhibited by an embodiment of compressor assembly 20.

Example 3

FIG. 21 is a table containing a third example of performance characteristics of an example compressor assembly 20. In the Example of FIG. 21, a compressor assembly 20 having an air ducting shroud 485, a dampening ring 700, an intake muffler 900, four sound control chambers, a fan cover, four foam sound absorbers and a tank seal 600 exhibited the performance values set forth in FIG. 21.

An internal or external vibration absorber, such as a dampening ring, a spring or a band can provide a constant force against the walls of the compressed gas tank 150 and thereby dampen the vibration of the tank in operation. Dampening of the tank reduces the sound level of the compressor assembly. Optionally, a resilient material can be placed between the tank wall and the vibration absorber. In an embodiment, the resilient material can be formed in the shape of a pad, cushion or sheet. In an embodiment, the resilient material can have the shape of a pad which is generally longer and wider than it is thick, but can have a variety of shapes. Optionally, multiple resilient materials can be used which can form multiple pads and/or layers between a surface or portion of a vibration absorber and a surface of the compressed gas tank 150. In an embodiment, the absorber can be a dampening ring.

FIG. 22 is a perspective view of a shell 155 of a compressed gas tank 150 having a dampening ring. The shell 155 has a compressed gas inlet port 780, a compressed gas outlet port 782 and a tank drain port 784. In an embodiment, the compressed gas tank 150 can have a dampening ring 700. Dampening ring 700 can be a member which is under compression and which applies an expansive pressure to the compressed gas tank 150 and which can absorb and/or dampen vibration and/or reduce noise emitted from the compressed gas tank 150. Optionally, dampening ring 700 can be in contact with tank inner surface 151 at least in part. Optionally, one or a plurality of cushion members 750 can be used as a dampening ring and disposed between at least a portion of the dampening ring 700 and tank inner surface 151.

The dampening ring 700 can be made from a broad variety of materials. In an embodiment, the dampening ring 700 can be made from steel. In a non-limiting example, the dampening ring 700 can have a spring steel at least in part. A non-limiting example of a spring steel is AISI 1075 spring steel. The thickness 718 (FIG. 25A) of the dampening ring 700 can be a value in a wide range, e.g. from 0.01 in to 0.5 in. For example, the thickness can be 0.025 in, or 0.04 in, or 0.05 in, or 0.1 in, or 0.2 in. In a non-limiting example, the dampening ring 700 can be 13 gauge (0.090 inch).

In an embodiment, the dampening ring 700 can have one or a plurality of hooks by which the dampening ring 700 can be compressed for insertion into and removal from the compressed gas tank 150. FIG. 22 illustrates a dampening ring 700 having a first hook 710 and a second hook 720.

In an embodiment, the dampening ring 700 can exert an outward pressure against a compressed gas tank 150 and/or against the tank inner surface 151 and/or against one or a plurality of a cushion member 750, having a value between 30 psi and 300 psi. In further embodiments, the pressure exerted by the dampening ring 700 against the compressed gas tank 150 and/or tank inner surface 151 and/or against at least a portion of cushion member 750. can have a value in a range of from 30 psi to 200 psi; or 30 psi to 150 psi; or between 50 psi to 150 psi; or between 40 psi to 80 psi; or between 45 psi to 60 psi.

The one or a plurality of cushion members 750 can be made of a broad variety of materials. In an embodiment, the cushion member 750 can be a resilient member. In a non-limiting example, the cushion member 750 can be a silicone, a high temperature silicone, rubber, felt, cloth, polymer, vinyl, plastic, foam molded plastic, cured resin or metal. Other materials which can be used to form at least a part of the cushion member 750 can be a paint, a coating or a wood.

In an embodiment, the cushion member 750 can withstand a temperature in a range of from −40° F. to 600° F. without experiencing any permanent negative changes to essential physical properties related to cushioning when the stopper or cushion is returned from an elevated temperature to an ambient temperature. The cushion member can withstand an elevated temperature in a range of from 380° F. to 410° F.; or from 400° F. to 450° F.; or from 380° F. to 500° F.; or from −40° F. to 750° F.

In an embodiment, pads or partial pads which have the same or different durometers can be used as a cushion member 750. In an embodiment, a pad under a pressure of 100 psig or less can have a thickness having a value in a range of from 0.05 in to 6 in. In an embodiment, a pad can have a 70 durometer and 0.125 inch thick silicone. In an embodiment, a pad can have a 70 durometer and 0.25 in thick silicone.

FIG. 23 illustrates a dampening ring having multi-layered pad 751 between the dampening ring 700 and the tank inner surface 151. This disclosure is not limited to a number of layers. The pad can be from 1 . . . n layers with n being a large number, e.g. 100. The multi-layered pad can be a laminate of layers and/or a number of layers of materials stacked upon one another, or optionally can be one or more materials adhered together.

FIG. 23 illustrates a non-limiting embodiment of a pad between the dampening ring 700 and the tank inner surface 151 having three layers, pad layer 756, pad layer 754 and pad layer 752. The layers can be of the same material, or different materials.

The material of the pads can be resilient or non resilient. In an embodiment, multi-layered pad 751 can have a combination of resilient and non-resilient materials. Optionally, a multi-layered pad 751 can have layers one or more of which is resilient. Optionally, a multi-layered pad 751 can have layers one or more of which is non-resilient.

FIG. 24 is a side view of a shell 155 of a compressed gas tank 150 having a dampening ring 700. In an embodiment, the installed chord length 717 can accommodate the thickness of the cushion member 750 or multiple cushion members, such as a multi-layered pad 751. In FIG. 24 the thickness of the cushioning layer is illustrated as 718. FIG. 24 also illustrates the inner radius of the dampening ring 700 as radius 725. The outer radius of the dampening ring 700 is illustrated as radius 727, which can abut the inner radius 729 of the cushion member 750. The outer radius 731 of the cushion member 750 can abut the inner radius 733 of compressed gas tank 150 which has an outer radius 735.

When installed, the dampening ring 700 can have an installed chord length 717, which is equal to or less than the ID of the compressed gas tank 150 into which it is inserted.

FIG. 25A is a side view of a dampening ring 700 in an uncompressed state. In this example, the dampening ring 700 can have an uncompressed chord length 715. The uncompressed chord length can have a value which can be significantly larger than the ID of the compressed gas tank 150 into which the dampening ring 700 is to be installed. In an embodiment, the uncompressed chord length can have a value in a range of from 100 percent to 150 percent of a compressed gas tank 150 inner diameter 714 (FIG. 24).

FIG. 25B is a side view of a dampening ring 700 in an installed state. In an embodiment, the dampening ring 700 can be compressed for insertion into position in compressed gas tank 150, for example, as illustrated in FIG. 25B by applying a force to the hooks, the first hook 710 and the second hook 720, sufficient to overcome resistance and change the state of the dampening ring 700 from an expanded state as illustrated in FIG. 25A to a compressed state, then the first hook 710 and the second hook 720 can be released to achieve an installed state of dampening ring 700 as shown in FIG. 25B.

For example, the dampening ring 700 having a first hook 710 and a second hook 720 can be compressed by applying a force to the first hook 710 and the second hook 720 which reduces the distance between the first hook 710 and the second hook 720 and configures the dampening ring 700 to a compressed state. A vibration absorber, such as dampening ring 700 can exert an expansive pressure in a range of from 5 lbs to the maximum design pressure of the compressed gas tank 150 into which it is placed. The vibration absorber can exhibit an expansive pressure of, e.g. 30 psi, or 45 psi, or 50 psi, or 75 psi, or 150 psi, or 200 psi, or 3000 psi, or a value in between these pressures.

In non-limiting example, if the dampening ring 700 can be designed with an upper limit of compression of 60 psi, then a force of greater than 60 psi can be applied to the first hook 710 and/or the second hook 720 to configure the dampening ring 700 from a uncompressed state 791 to a compressed state 793. Upon insertion of the dampening ring 700 into position in compressed gas tank 150, the compression pressure of greater than 60 psi can be removed allowing the dampening ring 700 to expand to an installed state 795 in which it exerts pressure against the compressed gas tank 150 and/or tank inner surface 151 and/or against a cushion member 750.

The installed chord length 717 as illustrated in FIG. 25B can be equal to the inner diameter of compressed gas tank 150. In an embodiment, the installed chord length 717 can be less than the inner diameter 714 (FIG. 24) allowing for the use of one or a plurality of cushion members 750 which can be placed between the dampening ring 700 and the tank inner surface 151. Optionally, the dampening ring 700 can exert pressure against the tank inner surface 151 and/or against the one or the plurality of a cushion member 750.

FIG. 25C is a perspective view of a dampening ring in an uncompressed state.

FIG. 25D is an end view of a dampening ring in an uncompressed state.

FIG. 26 is a first open end view of the compressed gas tank 150 having a dampening coil 761 in the form of a coiled spring steel band 760. This can dampen vibration of the compressed gas tank 150. In an embodiment, the coiled spring steel band 760 can have dimensions which can be in wide ranges, for example a width having a value in a range from 0.015 in 6.0 in, a thickness having a value in a range from 0.01 in to 0.1 in, and a length having a value in a range of from 2.5 in to 100 in or greater. These dimensions can be varied in conjunction with the size of the compressed gas tank 150 and its vibration and noise characteristics and service or design characteristics. In an embodiment, the coiled spring steel band 760 can have dimensions of 1.0 inch wide, 0.05 in thick and 50 inch length. In an embodiment, the coiled spring steel band 760 can have dimensions of 0.75 inch wide, 0.040 in thick and 40 inch length. In an embodiment, the coiled spring steel band 760 can have dimensions of 0.025 inch wide, 0.025 in thick and 30 inch length. The thickness the coiled spring steel band 760 can be a value in a range, e.g. from 0.01 in to 0.5 in. Optionally, one or a plurality of felt pads can be placed between the coiled steel band and the inner wall of the compressed gas tank 150.

FIG. 27 is a second open end view of the compressed gas tank 150 with a dampening coil 761 which e.g. in the figure is a coiled spring steel band 760. In an embodiment, multiple coiled spring steel band 760 can be installed in a compressed gas tank 150.

In this embodiment, one or a plurality of felt pads 762 and/or other dampening material(s) and/or other resilient material(s) can be placed between the coiled spring steel band 760 and the tank inner surface 151 of the compressed gas tank 150.

FIG. 28 illustrates a plurality of felt pads 762 between the coiled spring steel band 760 and tank inner surface 151.

In this embodiment, felt pads can be placed between the coiled spring steel band 760 and the tank inner surface 151, of the compressed gas tank 150.

FIG. 29 is a perspective view of a compressed gas tank 150 with an over-molded dampening ring 769. In the example of FIG. 29 the over-molded dampening ring 769 can be an over-molded spring steel ring 770. The over-molded spring steel ring 770 can have a spring steel ring 772 and over-molded cushion 774. In this embodiment, wrapped around a spring steel ring (also herein as dampening ring 700) in an over-molded material which can be a vibration dampening material and/or cushioning material and/or resilient material, or other material which can reduce sound emitted from the compressed gas tank 150.

FIG. 30 illustrates full view of the over-molded spring steel ring 770 having the spring steel ring 772 and over-molded cushion 774. Optionally, the over-molded spring steel ring 770 can have a plurality of protruding pads 776. FIG. 30 also illustrates the over-molded spring steel ring 770 having a first hooked portion 777 and a second hooked portion 779. The first hooked portion 777 and second hooked portion 779, on the ends of the spring steel ring can be used for a compression tool attachment that compress the spring steel ring 770 for installation inside the compressed gas tank 150.

FIG. 31 is a first perspective view of a shell 155 of a compressed gas tank 150 having a dampening band 810 and optionally a plurality of a band cushion 812, the dampening band 810, being placeable around the exterior of the compressed gas tank 150. In an embodiment, the dampening band 810 can be used to compress a vibration dampening material, such as the plurality of band cushions 812 having one or more of the cushioning materials disclosed herein, against the outer surface of the compressed gas tank 150 wall.

FIG. 32 is a second perspective view of the shell 155 with a dampening band 780.

FIG. 33 is a detail view of FIG. 27 showing the coiled spring steel band 760 on the tank inner surface 151, of the compressed gas tank 150, with one or a plurality felt pads 762 and/or one or a plurality of cushioning materials between them.

FIG. 34A is a perspective view of a grooved pad 830.

FIG. 34B is a groove-side view of a grooved pad 830.

FIG. 34C is an end view of a grooved pad 830.

FIG. 34D is a side view of a grooved pad 830.

FIG. 35A is a perspective view of an exemplary grooved pad 830 in an installed state.

FIG. 35B illustrates a grooved pad 830 attached to a dampening ring or coil.

The scope of this disclosure is to be broadly construed. It is intended that this disclosure disclose equivalents, means, systems and methods to achieve the devices, designs, operations, control systems, controls, activities, mechanical actions, fluid dynamics and results disclosed herein. For each mechanical element or mechanism disclosed, it is intended that this disclosure also encompasses within the scope of its disclosure and teaches equivalents, means, systems and methods for practicing the many aspects, mechanisms and devices disclosed herein. Additionally, this disclosure regards a compressor and its many aspects, features and elements. Such an apparatus can be dynamic in its use and operation. This disclosure is intended to encompass the equivalents, means, systems and methods of the use of the compressor assembly and its many aspects consistent with the description and spirit of the apparatus, means, methods, functions and operations disclosed herein. The claims of this application are likewise to be broadly construed.

The description of the inventions herein in their many embodiments is merely exemplary in nature and, thus, variations that do not depart from the gist of the invention are intended to be within the scope of the invention and the disclosure herein. Such variations are not to be regarded as a departure from the spirit and scope of the invention.

It will be appreciated that various modifications and changes can be made to the above described embodiments of a compressor assembly as disclosed herein without departing from the spirit and the scope of the following claims.

Claims

1. A compressor assembly, comprising: a compressed gas tank having a tank body and a vibration absorption member within the tank body, the vibration absorption member being in the form of a ring having opposing ends in a longitudinal direction of the ring, which dampens sound; anda sound level when in a compressing state which has a value of 75 dBA or less.

2. The compressor assembly of claim 1, wherein the ring applies a force against a portion of the compressed gas tank.

3. The compressor assembly of claim 1, wherein the ring applies a constant force against a portion of the compressed gas tank.

4. The compressor assembly of claim 2, further comprising a vibration dampening material between the tank and the ring.

5. A compressor assembly, comprising: a compressed gas tank having a vibration absorption member in the form of a ring having opposing ends in a longitudinal direction of the ring, which dampens sound; anda sound level when in a compressing state which has a value of 75 dBA or lesswherein the vibration absorption member applies a force to an internal portion of the compressed gas tank.

6. A method of controlling sound emitted from a compressor assembly, comprising the steps of: providing a compressor assembly having a compressed gas tank;providing a vibration absorber, which exerts a force upon the compressed gas tank; andcontrolling the sound level of the compressor assembly when in a compressing state to a value in a range of from 65 dBA to 75 dBA,wherein the step of providing a vibration absorber comprises providing a vibration absorber in the form of a ring, which exerts a force upon an internal portion of the compressed gas tank.

7. The method of controlling sound emitted from a compressor assembly according to claim 6, further comprising the step of: compressing a gas at a rate in a range of from 2.4 SCFM to 3.5 SCFM.

8. The method of controlling sound emitted from a compressor assembly according to claim 6, further comprising the step of: operating a motor which drives a pump assembly at a pump speed at a rate in a range of from 1500 rpm to 3000 rpm.

9. The method of controlling sound emitted from a compressor assembly according to claim 6, further comprising the step of: cooling the compressor assembly with a cooling gas at a rate in the range of from 50 CFM to 100 CFM.

10. The method of controlling sound emitted from a compressor assembly according to claim 6, further comprising the step of: compressing a gas to a pressure in a range of from 150 psig to 250 psig.