Sealed cavity compressor to reduce contaminant induction

Abstract

A cam driven compressor includes a cam coupled to a plurality of cylinder and piston assemblies. Each cylinder and piston assembly comprises a piston located and movable within a respective cylinder. Each cylinder has a cylinder head. The compressor comprises a housing defining a cavity configured to receive a portion of a source gas from one or more of the cylinders in order to maintain a positive gas pressure within the cavity.

Claims

1. A cam driven compressor, wherein a cam is coupled to a plurality of cylinder and piston assemblies wherein each cylinder and piston assembly comprises a piston located and movable within a cylinder, each cylinder having a cylinder head, the compressor comprising a housing having a first block half attached to a second block half along a longitudinal plane and defining a sealed cavity therebetween, wherein each cylinder and piston assembly is located along said longitudinal plane and extends radially outwardly from the housing in spaced relation with a next successive cylinder and piston assembly of the plurality of cylinder and piston assemblies, wherein each cylinder and piston assembly is in fluid communication with the sealed cavity, and wherein the sealed cavity is configured to receive a portion of a gas exclusively from one or more of the cylinder and piston assemblies to thereby pressurize the sealed cavity of the housing.

2. The cam driven compressor of claim 1, wherein a first cylinder of the plurality of cylinder and piston assemblies is a low pressure cylinder and wherein a portion of the gas within the first cylinder is directed into the sealed cavity.

3. The cam driven compressor of claim 1, wherein the housing includes a pressure relief valve adapted to prevent over-pressurization of the housing.

4. The cam driven compressor of claim 3, wherein the pressure relief valve has a maximum pressure limit of 1 psig.

5. The cam driven compressor of claim 1 wherein the sealed cavity is filled with the portion of the gas at a flow rate of 200 scc/m.

6. The cam driven compressor of claim 1, wherein the housing is selected to have a positive cavity pressure of 1 psig.

7. A method of producing a high purity high pressure gas, comprising: a) providing a cam driven compressor, wherein a cam is coupled to a plurality of cylinder and piston assemblies wherein each cylinder and piston assembly comprises a piston located and movable within a cylinder, each cylinder having a cylinder head, the compressor comprising a housing having a first block half attached to a second block half along a longitudinal plane and defining a sealed cavity therebetween, wherein each cylinder and piston assembly is located along said longitudinal plane and extends radially outwardly from the housing in spaced relation with a next successive cylinder and piston assembly of the plurality of cylinder and piston assemblies, wherein each cylinder and piston assembly is in fluid communication with the sealed cavity, and wherein the sealed cavity is configured to exclusively receive a portion of a gas from one or more of the cylinder and piston assemblies to thereby pressurize the sealed cavity of the housing; b) allowing the source gas to be supplied to the compressor; and c) allowing a portion of the source gas to pressurize the sealed cavity of the housing.

8. The method in accordance with claim 7, wherein a first cylinder of the plurality of cylinder and piston assemblies is a low pressure cylinder and wherein the portion of the source gas is provided by the first cylinder.

9. The method in accordance with claim 7, wherein the housing includes a pressure relief valve adapted to prevent over-pressurization of the housing.

10. The method in accordance with claim 9, wherein the pressure relief valve has a maximum pressure limit of 1 psig.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention will further be described, by way of example, with reference to the accompanying drawings:

(2) FIG. 1 is a front perspective view of an embodiment of a cam driven compressor in accordance with the present invention;

(3) FIG. 2 is a side perspective view of the embodiment shown in FIG. 1; and

(4) FIG. 3 is a cross section view of the cam driven compressor taken generally along line 3-3 in FIG. 2.

DETAILED DESCRIPTION

(5) Referring to the drawings, there is seen in FIGS. 1 through 3 one embodiment of the inventive compressor assembly designated generally by the reference numeral 10. Compressor assembly 10 includes a housing 12 and is configured to connect to a motor and speed reducer (not shown) via keyed bore 14 in shaft sleeve 16. Compressor assembly 10 generally includes a housing 12 comprising a block comprised of corresponding block halves 12a and 12b. First, second and third stage cylinder 18, 20 and 22, respectively, are spaced 120° apart and radially extend along respective axes X.sub.1-X.sub.3.

(6) For the sake of clarity, the moving components of the compressor have been removed. An example of such suitable components may be found within U.S. Pat. No. 8,684,704 (the '704 patent) assigned to Carleton Like Support Systems, Inc., the entirety of which is incorporated by reference as if fully set forth herein. As recounted within the '704 patent, a compressor may include a cam positioned on shaft sleeve 16 with respective cam follower assemblies operably connected to the cam. Each cam follower assembly may include a respective roller element rotatably connected between respective roller brackets and associated end plates. Each cam follower assembly may further include a respective connecting rod connected to a respective roller element via a respective roller bracket at a first end thereof; and to a respective piston at a second end thereof. Each connecting rod telescopes within a respective linear bearing and each piston is reciprocally located in a respective cylinder 18, 20 and 22. A compressor head 18a, 20a and 22a mounts to the end of a respective cylinder opposite the end from which the respective connecting rod extends.

(7) In this manner, low pressure gas enters via an air tube 24 into first stage cylinder 18 and its included piston assembly via inlet port 26 thereof and enters cylinder 18. When the highest lobe point of the cam reaches the piston assembly, its roller rides along the lobe point of the cam resulting in a piston upstroke (toward head 18a) and a first stage compression of the gas within cylinder 18. The compressed gas exits head 18a at outlet port 26a and is directed through air tube 28 until it reaches head 20a wherein the first stage compressed gas enters through inlet port 30 into cylinder 20. At this time, the piston within cylinder 20 begins a downstroke position as the gas enters its respective compression chamber. As the cam continues to rotate, its medium point approaches the cam follower assernhly associated with cylinder 20 which then begins its upstroke. High lobe point next approaches this assembly which completes the second stage compression of the gas within cylinder 20. The compressed gas exits at outlet port 30a and is directed through air tube 32 until it reaches head 22a wherein the second stage compressed air enters through inlet port 34 into cylinder 22. Again, as the cam continues to rotate, its medium lobe point approaches roller assembly associated with cylinder 22 which begins its upstroke. This roller then rides along the lobe high point of the cam resulting in a full piston upstroke and a third stage compression of the gas within cylinder 22. The compressed then gas exits as high pressure gas (e.g., up to or exceeding 1000 psi), via outlet port 34a through air tube 36 which may be connected to an appropriate high pressure gas collection (e.g., air cylinder, not shown). As rotation of the cam continues, this cycle is repeated providing a continuous stream of high pressure gas at outlet port 34a.

(8) Returning now to FIGS. 1-3, in accordance with an aspect of the present invention, block halves 12a and 12b are adapted to be joined so as to produce a sealed compressor body such as through a seal or gasket 38. Similarly, cylinders 18, 20 and 22 may be hermitically sealed to block halves 12a, 12b. Shaft sleeve 16 may also be sealed to block halves 12a, 12b as is known in the art. In this manner, housing 12 may be fully sealed such that the cavity 40 defined by the joined block halves 12a, 12b may be pressurized so as to be slightly above ambient pressure. To pressurize cavity 40, a purge gas may enter volume 40 through leaks around the inter-stage seals between each piston and cylinder.

(9) Housing 12 may further include a pressure relief valve 42 in communication with cavity 40 to prevent over-pressurization of the cavity in the event that a seal fails during any of the compression stages. Pressure relief valve 42 may also help meter the cavity pressure. In accordance with an aspect of the invention, operational efficiencies were optimized to include a pressure relief valve 42 selected to have an upper operating limit of 1 psig with an upper purge flow rate of about 200 scc/m. Thus, cavity pressure may be metered at 1 psig due to the upper operating limit of pressure relief valve 42. In an exemplary sample, oxygen supply gas having less than 1 ppm water at 25 psig was supplied to compressor 10. The resultant high pressure outlet gas was found to contain less than 7 ppm water at 500 psig in about 95% relative humidity environment. In accordance with an aspect of the invention, the first stage cylinder 18 may be configured to receive a pure oxygen supply having greater than 99.9% oxygen, wherein cylinder 18 operates with maximum flows of about 4.0 standard liters per minute (slpm) at maximum 40 psig at ambient temperatures. Third stage cylinder 22 may output greater than 99.9% oxygen gas with maximum flows of about 4.0 slpm at maximum 3,000 psig at ambient temperatures.

(10) While the above example recited a preferred relief valve/cavity pressure and purge flow rate, it should be understood by those skilled in the art that other values may be used depending upon system tolerances and required gas outputs. For instance, increased cavity pressures and/or purge flows may result in less contaminated outlet gases. It should be noted that cavity pressure and purge flow should be controlled, and preferably minimalized, to conserve the high purity gas and improve delivery efficiencies.

(11) Although the invention has been described with reference to preferred embodiments thereof, it is understood that various modifications may be made thereto without departing from the full spirit and scope of the invention as defined by the claims which follow.