FIELD OF THE INVENTION
The present application relates to the field of pumping devices, such as gas compressors and gas vacuums.
BACKGROUND
Oxygen has many important medical uses including, for example, assisting patients that have congestive heart failure or other diseases. Supplemental oxygen allows patients to receive more oxygen than is present in the ambient atmosphere. An oxygen concentrator separates nitrogen from atmospheric air to provide a highly concentrated source of oxygen. Some existing oxygen concentrators have two cylindrical containers filled with zeolite materials that selectively adsorb the nitrogen in the air. A compressor is used to force air through one of the cylindrical containers at a pressure at which the nitrogen molecules are captured by the zeolite. While air is forced through the first cylindrical container, the contents of the other cylindrical container are vented away to dissipate the captured nitrogen.
Several existing product gas or oxygen concentrators, for example, are disclosed in U.S. Pat. Nos. 4,449,990, 5,906,672, 5,917,135, and 5,988,165 which are commonly assigned to Invacare Corporation of Elyria, Ohio and fully incorporated herein by reference.
SUMMARY OF THE INVENTION
The present application discloses embodiments of a pumping device. A pumping device compresses fluid, provides a vacuum, or both compresses fluid and provides a vacuum. A pumping device may be used to force gas through a sieve bed, draw gas out of a sieve bed, or both force gas through a sieve bed and drawing gas out of a sieve bed. However, the pumping device may be used in a wide variety of different applications. When the pumping device is used with a sieve bed, the sieve bed may be a container with an oxygen enriching material, such as zeolite. However, other oxygen enriching materials can be used. A pumping device may be operated at high speed to provide a high fluid flow rate with a small pumping device.
BRIEF DESCRIPTION OF THE DRAWINGS
Further features and advantages of the present invention will become apparent to those of ordinary skill in the art to which the invention pertains from a reading of the following description together with the accompanying drawings, in which:
FIG. 1A is a perspective view of a pumping device in accordance with an exemplary embodiment;
FIG. 1B is a view taken along lines 1B-1B in FIG. 1A;
FIG. 1C is a view taken along lines 1C-1C in FIG. 1B;
FIG. 1D is a view taken along lines 1D-1D in FIG. 1A;
FIG. 1E is a top view of the pumping device illustrated in FIG. 1A;
FIG. 1F is a view taken along lines 1F-1F in FIG. 1B;
FIG. 1G is a bottom view of the pumping device illustrated in FIG. 1A;
FIG. 2A is an exploded perspective view of the pumping device shown in FIG. 1A;
FIG. 2B is a second exploded perspective view of the pumping device shown in FIG. 1A;
FIG. 3A is a sectional view taken along the plane indicated by lines 3-3 in FIG. 1B;
FIG. 3B is a view showing some of the components shown in FIG. 3A on a larger scale;
FIG. 3C is a view similar to FIG. 3A, illustrating an embodiment where a drive pulley of the pumping device is positioned inside a housing of the pumping device;
FIG. 4 is a perspective view of the pumping device illustrated by FIG. 1A with some components removed;
FIG. 5A is a perspective view of an exemplary embodiment of a housing for a pumping device;
FIG. 5B is a second perspective view of an exemplary embodiment of a housing for a pumping device;
FIG. 6A is a perspective view illustrating a bottom portion of the housing illustrated by FIG. 5A;
FIG. 6B is a second perspective view illustrating the bottom portion of the housing illustrated by FIG. 5A;
FIG. 7A is a perspective view illustrating a top portion of the housing illustrated by FIG. 5A;
FIG. 7B is a second perspective view illustrating the top portion of the housing illustrated by FIG. 5A;
FIG. 8 is a perspective view of an exemplary embodiment of a cylinder for a pumping device;
FIG. 8A is a perspective view of an exemplary embodiment of a head cover for a pumping device;
FIG. 8B is a second perspective view of the head cover illustrated by FIG. 8A;
FIG. 9 is an exploded perspective view of an exemplary embodiment of a head assembly for a pumping device;
FIG. 10A is an exploded perspective view of an exemplary embodiment of a head and cylinder assembly for a pumping device;
FIG. 10B is a second exploded perspective view of the head and cylinder assembly illustrated by FIG. 10A;
FIG. 11A is a perspective view of an exemplary embodiment of a crank and piston a assembly for a pumping device;
FIG. 11B is a top view of the crank and piston assembly illustrated by FIG. 11A;
FIG. 11C is a front view of the piston and crank assembly illustrated by FIG. 11A;
FIG. 11D is a rear view of the piston and crank assembly illustrated by FIG. 11A;
FIG. 11E is an exploded perspective view of the piston and crank assembly illustrated by FIG. 11A;
FIG. 11F is a top view of the exploded piston and crank assembly illustrated by FIG. 11E;
FIG. 12 is a perspective view of a crankshaft in a portion of a housing;
FIG. 13A is a perspective view of a crankshaft assembly
FIG. 13B is a perspective view similar to FIG. 13A with bearings removed from the crankshaft;
FIG. 13C is an exploded perspective view of the crankshaft illustrated by FIG. 13B;
FIG. 13D is another exploded perspective view of the crankshaft illustrated by FIG. 13B;
FIG. 14A is a perspective view of an exemplary embodiment of a piston assembly;
FIG. 14B is a side view of the piston assembly illustrated by FIG. 14A;
FIG. 14C is an exploded perspective view of the piston assembly illustrated by FIG. 14A;
FIG. 14D is a sectional view taken along the plane indicated by lines 14D-14D in FIG. 14B;
FIG. 15A is a perspective view of an exemplary embodiment of a piston rod;
FIG. 15B is a side view of the piston rod illustrated by FIG. 15A;
FIG. 15C is a bottom view of the piston rod illustrated by FIG. 15A;
FIG. 15D is a top view of the piston rod illustrated by FIG. 15A;
FIG. 16A is a perspective view of an exemplary embodiment of a piston;
FIG. 16B is another perspective view of the piston illustrated by FIG. 16A;
FIG. 16C is a side view of the piston illustrated by FIG. 16A;
FIG. 16D is a bottom view of the piston illustrated by FIG. 16A;
FIG. 16E is a sectioned perspective view taken along the plane indicated by lines 16E-16E in FIG. 16D;
FIG. 16F is a sectional view taken along the plane indicated by lines 16E-16E in FIG. 16D;
FIG. 17A is a perspective view of an exemplary embodiment of a piston seal;
FIG. 17B is a sectioned perspective view taken along the plane indicated by lines 17B-17B in FIG. 17A;
FIG. 18A is a schematic illustration of a pumping device configured to provide a vacuum in a first state;
FIG. 18B is a schematic illustration of the pumping device illustrated by FIG. 18A in a second state;
FIG. 19 is a schematic illustration of an exemplary embodiment of an oxygen concentrator; and
FIG. 20 is a schematic illustration of an exemplary embodiment of an oxygen concentrator.
DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS
As described herein, when one or more components are described as being connected, joined, affixed, coupled, attached, or otherwise interconnected, such interconnection may be direct as between the components or may be indirect such as through the use of one or more intermediary components. Also as described herein, reference to a “member,” “component,” or “portion” shall not be limited to a single structural member, component, or element but can include an assembly of components, members or elements.
FIG. 1 illustrates an exemplary embodiment of a pumping device 10. In several of the illustrated embodiments, the pumping device 10 is configured as a compressor. However, as will be described in more detail below, the pumping device 10 can be configured to provide a vacuum (see FIGS. 18A and 18B) or to provide both compressed gas and draw a vacuum by changing the valve configuration of the pumping device. The pumping device 10 includes a cylinder assembly 12 and first and second cylinder head assemblies 110A, 110B.
The cylinder assembly 12 can take a wide variety of different forms. In the example illustrated by FIG. 1, the cylinder assembly includes a housing 13, a first sleeve 14A, a second sleeve 14B, a third sleeve 14C, and a fourth sleeve 14D. The illustrated sleeves 14A-14D include optional fins 15. The fins 15 increase the surface area of the cylinders to help dissipate heat. The sleeves may take a wide variety of different forms. Any configuration that provides the cylinders can be used. For example, the first and second sleeves and/or the third and fourth sleeves may be formed from a single piece or block. The sleeves 14A-14D may be made from a wide variety of different materials including, but not limited to, metals, plastics, ceramics, carbon fiber materials, any combination of these materials and the like. In one exemplary embodiment, the sleeves 14A-14D are made from aluminum.
The housing 13 can take a wide variety of different forms. Referring to FIGS. 5, 5A and 5B, the housing 13 includes openings 506. The cylinders 14A-14D are secured to the housing 13 in the openings 506. The illustrated housing 13 includes a first half 500 and a second half 502 that meet at a joint line 504. In the illustrated embodiment, the joint line 504 intersects the openings 506 for the cylinders 14A-14D. In another embodiment, the joint line 504 does not intersect the openings 506. For example, the joint line may be positioned as indicated by dashed line 504 in FIGS. 1B and 1D. The housing 13 may be made from a wide variety of different materials including, but not limited to, metals, plastics, ceramics, carbon fiber materials, any combination of these materials and the like. In one exemplary embodiment, the housing 13 is made from plastic.
Referring to FIG. 3A, the sleeves 14A-14D define cylinders 36A-36D. The cylinders 36A-36D may take a variety of different forms. In the illustrated example, the cylinder 36A is adjacent and inline with the cylinder 36B and the cylinder 36C is adjacent and inline with the cylinder 36D. Referring to FIG. 1B, the cylinders 36A, 36B are opposed to the cylinders 36C, 36D. That is, an angle θ between the cylinders 36A, 36B and the cylinders 36C, 36D is approximately 180 degrees in the exemplary embodiment. As such, the illustrated cylinders 36A-36D are in a substantially “dual boxer” configuration. However, in other embodiments, the angle θ may be different. For example, the angle θ may be any angle between 90 and 180 degrees. As can be seen in FIGS. 1A, and 3A, the cylinders 36A-36D are each axially offset from one another in the illustrated embodiment.
Referring to FIGS. 2A and 3A, the pumping device 10 includes a plurality of pistons 40A-40D that are associated in a one to one relationship with the cylinders 36A-36D. A first piston 40A is located in the first cylinder 36A and is supported for reciprocating movement in the first cylinder. A second piston 40B is located in the second cylinder 36B and is supported for reciprocating movement in the second cylinder. A third piston 40C is located in the third cylinder 36C and is supported for reciprocating movement in the third cylinder. A fourth piston 40D is located in the fourth cylinder 36D and is supported for reciprocating movement in the fourth cylinder.
The pistons 40A-40D can take a wide variety of different forms. FIGS. 14A-14D illustrate an exemplary embodiment of a piston assembly 1400 that may be used in each of the cylinders 36A-36D. The illustrated piston assembly includes a piston 40, a drive or connecting rod 52, a seal or ring 1402, an intake valve 1404, and a bearing 1406. In the illustrated embodiment, the pistons 40A-40D are fixed for movement with the corresponding drive or connecting rod 52A-52D. This arrangement is referred to as a “wobble piston,” because fixing the pistons 40A-40D to the connecting rods 52A-52D causes some amount of canting or wobbling as the pistons 40A-40D move in the cylinders 36A-36D. Alternatively, one or more of the pistons 40 could be pivotally connected to the connecting rod 52 in a conventional manner. In this embodiment, the pistons 40A-40D will slide in the cylinders 36A-36D without significant canting or wobbling.
In the illustrated exemplary embodiment, the cylinders 36A-36D and corresponding pistons 40A-40D each have the same diameter and stroke. As a result, the stroke of each piston 40A-40D in its respective cylinder results in the same displacement of gas. In other embodiments, the pistons may have different sizes and/or strokes and the pumping device may have more than four cylinders or fewer than four cylinders.
In the illustrated exemplary embodiment, the gas inlet (when the pumping device is configured as a compressor) or the gas exhaust (when the pumping device is configured as a vacuum) is through the piston 40. However, in other embodiments, the gas inlet (when the pumping device is configured as a compressor) or the gas exhaust (when the pumping device is configured as a vacuum) is defined by a head assembly 110A, 110B, or in the cylinder 36.
Referring to FIGS. 16A-16F, the illustrated piston 40 includes a disk shaped portion 1300 and a base or mounting portion 1302 having a diameter that is smaller than the diameter of the cylindrical portion 1300. A mounting hole 1304 extends through the piston 40. The mounting hole 1304 allows the valve 1404 to be secured to the piston 40 and allows the piston 40 to be connected to the connecting rod 52. Referring to FIGS. 16E and 16F, a plurality of passages 1600 extend through the disk shaped portion 1300 to channels 1602 in the side of the mounting portion 1302. These passages 1600 and channels 1602 act as the gas inlet (when the pumping device is configured as a compressor) or the gas exhaust (when the pumping device is configured as a vacuum). Four passages 1600 and channels 1602 are illustrated. However, any number of passages 1600 and/or channels 1602 can be included and can have any configuration. A plurality of valve locating projections 1610 are disposed on the disk shaped portion 1300. The valve locating projections 1610 align the intake valve 1404 with the passages 1600.
Referring to FIGS. 15A-15D, the illustrated connecting rod 52 includes a piston support portion 1500, an elongated rod portion 1502 and a ring portion 53. The illustrated piston support portion 1500 is cup shaped with a flat end 1510, an annular inner surface 1512, and an annular outer surface 1514. The annular inner surface 1512 is shaped to accept the base or mounting portion 1302 of the piston 40. A mounting hole 1524 extends into the elongated rod portion 1502 from a bottom interior surface 1526 of the piston support portion 1500. The mounting hole 1524 is in alignment with the mounting hole 1304 of the piston to facilitate connection of the piston 40 to the connecting rod 52. Referring to FIGS. 15A-15D, a plurality of passages 1560 extend through the piston support portion 1500. These passages 1560 allow gas to flow through the piston support portion 1500 to the passages 1600 and channels 1602 of the piston 40. Four passages 1560 are illustrated. However, any number of passages 1560 can be included and can have any configuration. An opening or vent 1670 (See FIG. 1A) may be provided in the housing that acts as the gas inlet (when the pumping device is configured as a compressor) and/or the gas exhaust (when the pumping device is configured as a vacuum).
The illustrated pistons 40A-40D are driven by a crankshaft 50 and connecting rods 52A-52D, as described below. The ring portion 53 pivotally connects each connecting rod 52A-52D to the crankshaft 50. The elongated rod portion 1502 connects the ring portion 53 to the piston support portion 1500. In the exemplary embodiment, a bearing 1406 is disposed inside each ring portion 53, around the crankshaft 50.
The seal or ring 1402 provides a seal between each piston 40A-40D and each cylinder 36A-36D. The seal or ring 1402 can take a wide variety of different forms. The illustrated seal or ring 1402 is cup shaped with an annular wall 1700 that meets an end wall 1702. An opening 1704 is disposed in the end wall 1702. The annular wall 1700 is sized to fit around the disk shaped portion 1300 of the piston 40. The opening 1704 is sized to fit around the mounting portion 1302 of the piston 40, with the end wall 1702 sandwiched between the disk shaped portion of the piston 40 and the piston support portion 1500 of the connecting rod 52.
The valve 1404 may take a wide variety of different forms. In the illustrated embodiment, where the pumping device 10 is configured as a compressor, the valve 1404 allows gas inside the housing 13 to flow through the support portion 1500 of the connecting rod 52 and the piston 40 into the cylinder 36, but prevents gas from flowing from the cylinder 36 back into the interior of the housing 13. In another embodiment, where the pumping device 10 is configured as a vacuum, the check valve 1404 would be configured to allow gas to flow from the cylinder, through the piston 40 and/or the support portion 1500 of the connecting rod 52, and into the housing 13, but prevent gas from flowing from the housing 13 into the cylinder 36 (See FIGS. 18A and 18B). In one exemplary embodiment, the check valve arrangements 1404 of the two pistons 40A, 40B are configured as a compressor (i.e. gas is drawn into the cylinders 36 from the housing for compression) and the check valve arrangement of the other two pistons are configured as a vacuum (i.e. force gas out of the cylinders into the housing).
Referring to FIG. 14C, the illustrated valve 1404 is a butterfly or flap valve. However, any type of check valve can be used. The illustrated valve includes a flap member 1420 and a fastener 1422. The fastener 1422 connects flap member 1420 to the piston 40. The flap member is disposed over the passages 1600 of the piston 40. When the pressure inside the housing 13 is higher than the pressure inside the cylinder 36 (i.e. during the charge stroke), flaps of the flap member 1420 flex away from the piston 40 to allow gas to flow from the housing, through the support portion 1500 of the connecting rod 52, through the piston 40, and into the cylinder 36. However, when the pressure inside the cylinder 36 is higher than the pressure inside the housing (i.e. during the compression stroke), the flap member 1420 seals against the piston 40 to prevent gas from flowing from the cylinder 36, through the piston 40, and into the housing 13. In an embodiment, where the pumping device 10 is configured as a vacuum, the valve 1404 may be positioned on the opposite side of the piston 40 or piston support portion 1500 to allow gas to flow from the cylinder, through the piston 40, and into the housing 13, but prevent gas from flowing from the housing 13 into the cylinder 40. In one exemplary embodiment, the valves 1404 of two pistons 40A, 40B are positioned on the illustrated side of the pistons, such that one side of the head plate assembly 100A is configured as a compressor (i.e. force gas out of the head plate assembly) and the valves 1404 of two pistons 40C, 40D are positioned on the opposite side of the pistons, such that the other head plate assembly 100B is configured as a vacuum (i.e. draw gas into the head plate assembly).
FIG. 14C illustrates assembly of the piston assembly 1400. The seal or ring 1402 is placed around the base or mounting portion 1302 of the piston 40. The base or mounting portion 1302 of the piston 40 is inserted into the support portion 1500 of the of the connecting rod 52, such that the seal 1402 is clamped between the piston 40 and the connecting rod 52. The valve 1404 is placed on the piston 40. The assembly is secured together with a fastener 1422. Bearings 1406 are installed in the ring portion 53 of the connecting rod 52 during installation on the crankshaft 50.
Referring to FIGS. 3A and 4, crankshaft 50 (described below in detail) is supported for rotation about a crank axis X in first and second bearings 62, 68. The first and second bearings 62, 68 are mounted to the housing 13 by first and second bearing supports 54 and 56. The illustrated bearing supports 54, 56 are molded as part of the housing 13. The illustrated supports 54, 56 and bearings 62, 68 are located between the ring portions 53A, 53C of the connecting rods 52A, 52C and between the ring portions 53B, 53D of the connecting rods 52B, 52D respectively. In another exemplary embodiment, the bearings 62, 68 are located outside the ring portions 53A of the connecting rod 52A and outside the ring portion 53D of the connecting rod 52D respectively, such that the bearings 62, 68 are positioned at either end of the housing 13.
Referring to FIG. 4, the crankshaft 50 forms part of a drive mechanism of the pumping device 10 for driving the pistons 40A-40D for movement in the cylinders 36A-36D. The drive mechanism includes a motor 81 (schematically illustrated by FIG. 1C) that drives the crankshaft 50, and the connecting rods 52A-52D. However, a wide variety of different drive mechanisms may be used. In other embodiments the crankshaft could be connected to the pistons or coupled to the pistons 40A-40D in other manners, for example with guides between the connecting rods 52A-52D and the pistons. The motor 81 may be coupled to the pulley 83 in a wide variety of different ways. For example, the motor 81 may be coupled to the pulley 83 by a belt or gears (the pulley 83 may be replaced with a gear). In the example illustrated by FIG. 1C, the motor 81 is coupled to the pulley 83 by a belt 85 and a drive pulley 87 attached to a motor output shaft. In another exemplary embodiment, an output shaft of the motor 81 may be directly connected to the crankshaft 50. For example, a motor housing may be fixed relative to the housing 13, the output shaft of the motor 81 may be aligned with and rotate about axis X, and the crank shaft portion 84A is connected to the output shaft of the motor.
In one exemplary embodiment, the drive pulley 87 is driven at a high speed. For example, the drive pulley 87 may be driven at 8,000 to 12,000 rpm, 9,000 to 11,000 rpm, or about 10,000 rpm. In the illustrated embodiment, the drive pulley 87 is much smaller than the pulley 83. This allows the crankshaft 50 to be driven with a much smaller motor 81. For example, the ratio of the diameter of the pulley 83 to the pulley 87 may be about 4:1, about 3:1, or about 2:1. The pulley 83 and crankshaft 50 may be driven at 2,000 to 4,000 rpm, 2,500 to 3,500 rpm, or about 3,000 rpm.
FIGS. 13A-13D illustrate an exemplary embodiment of a crankshaft 50. In the embodiments illustrated by FIGS. 13A-13D, the crankshaft 50 is made from multiple pieces that are assembled together and can optionally be disassembled. However, the crankshaft 50 can be made from a single piece (or welded together to form a single piece). The illustrated crankshaft 50 includes first and second support portions 70A, 70B that each have a generally cylindrical configuration defined by a cylindrical outer surface centered on a crank axis X of the pumping device 10. The crankshaft 50 rotates about the crank axis X during operation of the pumping device 10. In the illustrated embodiment, the support portions 70A, 70B are disposed in the bearings 62, 68.
Referring to FIGS. 13A-13D, in the illustrated embodiments, the crankshaft 50 also includes first, second, and third connecting rod driving shaft portions 84A, 84B, 84C that extend axially from and are eccentric to the crank axis X. Each of the eccentric shaft portions 84A, 84B, 84C has a cylindrical configuration with each cylinder having a central axis that is parallel to, but spaced apart from the crank axis X. In the illustrated embodiments, the central axis of the shaft portions 84A, 84B, 84C are positioned away from the crank axis X by the same distance. In the illustrated embodiment, the axis 85A is aligned with the axis 85C and an angle of approximately 180 degrees (See FIG. 11C) is formed between the central axes 85A/85C, the crank axis X, and the central axis 85B. However, the shaft portions 84A, 84B, 84C can be positioned with respect to the crank axis in any manner to achieve desired motions of the piston rods 52A-52D that are coupled to the shaft portions. In the illustrated embodiment, the support portions 70A, 70B that are mounted in the bearings 62, 68 have a diameter that is greater than a diameter of the cylindrical connecting rod driving shaft portions 84A, 84B, 84C.
Referring to FIG. 4, in an exemplary embodiment the first, second, and third cylindrical connecting rod driving shaft portions 84A, 84B, 84C are the only connecting rod driving bodies of the crankshaft. In this embodiment, the shaft portions 84A, 84C each drive a single connecting rod 54A, 54D, while the shaft portion 84B drives two connecting rods 54B, 54C. However, any number of connecting rod driving bodies can be included. For example, one connecting rod driving shaft portion may be included for each connecting rod.
The connecting rod driving shaft portions 84A, 84B, 84C may take a wide variety of different forms. In the embodiment illustrated by FIGS. 13A-13D, the connecting rod driving shaft portions 84A, 84C are each integrally formed with one of the support portions 70A, 70B and the shaft portion 84B is a separate shaft that is assembled with the support portions (See FIGS. 13C and 13D). However, the crankshaft 50 may be constructed in a wide variety of different ways. For example, the entire crankshaft can be integrally formed, for example, by casting or machining. In another example, the support portions 70A, 70B and the shaft portions 84A, 84B, and 84C can all be discrete parts that are assembled together.
In the embodiment illustrated by FIGS. 13A-13D, the connecting rod driving shaft portion 84A extends from the support portion 70A, the connecting rod driving shaft portion 84C extends from the support portion 70B, and the connecting rod driving shaft portion 84B extends between the support portion 70A and the support portion 70B.
Referring to FIGS. 11A-11F, a connecting rod 52A is connected between the piston 40A and the first eccentric shaft portion 84A. Connecting rods 52B, 52C are connected between the pistons 40B, 40C and the second eccentric shaft portion 84B. A connecting rod 52D is connected between the piston 40D and the third eccentric shaft portion 84C. In the illustrated embodiment, the ring 53A is disposed around the shaft portion 84A to rotatably connect the rod 52A to the shaft portion 84A. A bearing 1406 may be disposed between the ring 53A and the shaft 84A. The rings 53B, 53C are disposed around the shaft portion 84B to rotatably connect the rods 52B, 52C to the shaft portion 84B. Bearings 1406 may be disposed between the rings 53B, 53C and the shaft portion 84B. In the illustrated embodiment, the ring 53D is disposed around the shaft portion 84D to rotatably connect the rod 52D to the shaft portion 84C. A bearing 1406 may be disposed between the ring 53D and the shaft 84D.
Referring to FIGS. 3A and 4, the aligned shaft portions 84A, 84C drive the first and fourth pistons 40A, 40D. Due to the opposed or “boxer” configuration of the pistons, the motion of the fourth piston 40D follows or lags the motion of the first piston 40A by rotation of the crankshaft by 180 degrees in the illustrated embodiment. The shaft portion 84B drives both the second and third pistons 40B, 40C. Due to the angular spacing of the second shaft portion 84B with respect the first and third shaft portions 84A, 84C about the crank axis X, the motion of the second piston 40B follows or lags the motion of the first piston 40A by rotation of the crankshaft by the angle of the angular spacing (approximately 180 degrees in the illustrated embodiment). Due to the opposed or “boxer” configuration, the motion of the third piston 40C follows or lags the motion of the second piston 40B by rotation of the crankshaft by 180 degrees in the illustrated embodiment. As such, the first piston 40A is in phase with the third piston 40C and the second piston 40B is in phase with the fourth piston 40D, with the second and fourth pistons lagging the first and third pistons by 180 degrees. As such, when the first and third pistons 40A, 40C are closest to their respective head assemblies 110A, the second and fourth pistons 40B, 40D, are at their maximum distance from their respective head assemblies 110B (See FIG. 3A).
Rotation of the crankshaft 50 about the crank axis X results in reciprocating movement of pistons 40A-40D in the cylinders 36A-36D. Referring to FIG. 3A, in an exemplary embodiment the drive pulley 83 is connected to the crankshaft 50 to facilitate the application of a drive torque to reciprocate the pistons 40A-40D. The drive pulley 83 may be connected to the crankshaft 50 in a variety of different ways. The illustrated drive pulley is concentric with the support portions 70A, 70B. In the example illustrated by FIG. 3A, the drive pulley 83 is connected to an extended portion 352 of the shaft portion 84A. In this example, the pulley 83 is disposed outside the housing 13. In another embodiment, the pulley 83 may be disposed inside the housing. For example, in the example illustrated by FIG. 3C, the drive pulley 83 is connected to the shaft portion 84B. The drive pulley 83 illustrated by FIG. 3C is concentric with the axis X of the support portions 70A, 70B. With either illustrated pulley 83, rotation of the pulley 83 causes rotation of the crankshaft. In the example illustrated by FIG. 3C, a slot may be cut in the housing 13 to allow the pulley to be driven by a motor positioned outside the housing.
As shown in FIG. 1A, the pumping device 10 includes a pair of cylinder head assemblies 100A, 100B that are attached to the cylinder assembly 12. In the example illustrated by FIGS. 10A and 10B, each cylinder head assembly 100A, 100B includes a cylinder head plate 112, a check valve arrangement 114, and a sealed cover 116. The illustrated cylinder head plate 112 is configured to sealingly cover a pair of the cylinder sleeves 14A and 14B or 14C and 14D. In the illustrated embodiment, the cylinder head plate 112 includes a pair of circular projections 113 that fit within a corresponding pair of cylinder sleeves 14 (see FIG. 10B). A seal member, such as and o-ring or a gasket, may be used to provide a seal between each circular projection 113 and sleeve. A passage 115 is disposed through each projection, so that gas may selectively pass from each cylinder 36 through each head plate 112.
The illustrated cylinder head plate 112 is configured to sealingly cover a pair of the cylinder sleeves 14A and 14B or 14C and 14D. In the illustrated embodiment, the cylinder head plate 112 includes a pair of circular projections 113 that fit within a corresponding pair of cylinder sleeves. A seal member, such as and o-ring or a gasket, may be used to provide a seal between each circular projection 113 and sleeve. A passage 115 is disposed through each projection, so that gas may selectively pass from each cylinder through each head plate.
The check valve arrangement 114 may take a wide variety of different forms. In the illustrated embodiment, where the pumping device 10 is configured as a compressor, the check valve arrangement 114 allows gas to flow from each cylinder, through the head plate 112, and into an interior of the head plate assembly, but prevents gas from flowing from the head assembly 100A into the cylinders. In another embodiment, where the pumping device 10 is configured as a vacuum, the check valve arrangement 114 would be configured to allow gas to flow from the interior of the head assembly, through the head plate 112, and into the cylinders, but prevent gas from flowing from the cylinders into the head assembly 100A (see FIGS. 18A and 18B). In one exemplary embodiment, the check valve arrangement 114 of one head assembly 100A is configured as a compressor (i.e. force gas out of the head plate assembly) and the check valve arrangement of the other head assembly 100B is configured as a vacuum (i.e. draw gas into the head plate assembly).
Referring to FIGS. 10A and 10B, the illustrated check valve arrangement 114 is a butterfly or flap valve. However, any type of check valve can be used. The illustrated check valve arrangement includes a flap member 120, a fastener 122, and a retainer 124. The fastener 122 connects the retainer 124 and the flap member 120 to the head plate. The retainer 124 positions the flap member and limits the amount of movement of flaps of the flap member 120. The flaps of the flap member 120 are disposed over the passages 115 of the head plate. When the pressure inside a cylinder is higher than the pressure inside the head assembly, the flap member 120 flexes away from the head plate 112 to allow gas to flow from the cylinder 36, through the head plate 112, and into an interior of the head plate assembly. However, when the pressure inside the head plate assembly is higher than the pressure inside the cylinder, the flap member 120 seals against the head plate 112 to prevent gas from flowing from the head assembly 110A into the cylinder 36.
In an embodiment where the pumping device 10 is configured as a vacuum, the check valve arrangement 114 may be positioned on the opposite side of the head plate 112 to allow gas to flow from the interior of the head assembly, through the head plate 112, and into the cylinders 36, but prevent gas from flowing from the cylinders into the head assembly 100A. In one exemplary embodiment, the check valve arrangement 114 of one head assembly 100A is positioned on the illustrated side of the head plate, such that one head assembly 100A of the pumping device 10 is configured as a compressor (i.e. force gas out of the head assembly through port 165) and the check valve arrangement is positioned on the opposite side of the head plate, such that the other head plate assembly 100B is configured as a vacuum (i.e. draw gas into the head plate assembly through port 165).
The cover 116 can take a wide variety of different forms. Referring to FIG. 9, the illustrated cover 116 is configured to sealingly cover the cylinder head plate 112. In the illustrated embodiment, cover 116 has a shape that matches the shape of the cylinder head plate 112. A seal member 117, such as and o-ring or a gasket, may be used to provide a seal between the cover 116 and the cylinder head plate 112 (see FIG. 9). A port 165 is disposed through the cover 116, so that gas may exit the cylinder head assembly 100A, 100B when the cylinder head assembly is configured for gas compression or so that gas may enter the cylinder head assembly 100A, 100B when the cylinder head assembly is configured to provide a vacuum.
Referring to FIG. 3A, when the first and third pistons 40A, 40B are in the compression stage, the second and fourth pistons 40C, 40D are in the intake stage. In the illustrated embodiment, the cylinders 36A-36D are not staged. That is, the output gas from one cylinder does not feed another cylinder that further compresses the gas. In the illustrated embodiment, the output of the first and second cylinders 36A, 36B is provided through the port 165 of the head assembly 110A and the output of the third and fourth cylinders 36C, 36D is provided through the port 165 of the head assembly 110B.
In the illustrated exemplary embodiment, each of the pistons 40A-40D operate in the cylinders 40A-40D in the same manner. Referring to FIG. 3A, when piston 40 is on the intake phase (for example, as the piston 40B moves to the illustrated position), the pressure in the cylinder 36 is lower than the intake pressure in the housing. As a result, intake gas flows through the inlet check valve 1404 (see FIGS. 14A and 14C) and into the cylinder 36. When the piston 40 thereafter is compressing the gas in the cylinder 36 (for example, as the piston 40A moves to the position illustrated by FIG. 3A), the pressure in the cylinder becomes higher than the intake pressure. As a result, intake gas can not flow through the check valve 1404 back into the housing 13. Also, the pressure in the cylinder 36 becomes higher than the pressure in the cylinder head assembly 100 during the compression stroke. As a result, compressed gas flows through the check valve arrangement 114, into the cylinder head assembly, and out the port 165. This cycle is repeated as the piston 40 reciprocates.
FIGS. 18A and 18B schematically illustrate an embodiment where a piston 40 is operated to create a vacuum. One or more of the pistons 40 may be operated in the manner illustrated by FIGS. 18A and 18B (the head 100A would be partitioned if only one piston were used to create a vacuum). In this embodiment, when piston 40 is on a vacuum phase (see FIG. 18A) where the piston is moving toward the housing 13, the pressure in the cylinder 36 is lower than the pressure in the head assembly 100. As a result, gas is drawn by the piston 40 through the check valve 114 and into the cylinder 36. Referring to FIG. 18B, when the piston 40 thereafter is moving toward the head assembly 110, the pressure in the cylinder becomes greater than the pressure in the head assembly 110. As a result, gas cannot flow through the check valve 114 back into the head assembly 114. Also, the pressure in the cylinder 36 becomes higher than the pressure in the housing 13 during the stroke toward the housing. As a result, gas flows through the check valve 1404 and into the housing 13. This cycle is repeated as the piston 40 reciprocates.
The pumping device 10 described herein can be used in a wide variety of different applications. In one exemplary embodiment, the pumping device 10 is used to provide compressed air and/or vacuum to sieve beds of an oxygen concentrator. For example, the pumping device 10 can be used in any of the oxygen concentrators described by U.S. Pat. No. 4,449,990; 5,906,672; or 5,917,135. However, the pumping device 10 can be used in any type of oxygen concentrator. U.S. Pat. Nos. 4,449,990; 5,906,672; and 5,917,135 are incorporated herein by reference in their entirety.
FIGS. 19 and 20 illustrate exemplary embodiments of oxygen concentrators 1900, 2000. FIG. 19 corresponds to FIG. 1 of U.S. Pat. No. 4,449,990, except the pump, motor, and vacuum are replaced with a vacuum, such as a pump device 10 described by the present application provided with two vacuum ports. In FIG. 19, the reference characters from U.S. Pat. No. 4,449,990 are prefixed with “19” so the reference characters would not conflict with other reference characters of this application. The oxygen concentrator 1900 functions in much the same way as the oxygen concentrator described in U.S. Pat. No. 4,449,990, except the air is alternately drawn into the sieve beds 1910, 1912 by a vacuum 10 as indicated by arrows 1999 instead of being alternately forced into the sieve beds 1910, 1912 by a compressor. An optional assist pump or pumps (indicated by arrows P) may be provided at the exit of the sieve beds to convey oxygen enriched gas drawn through the sieve bed by the pump device 10 to the tank 1930. In one exemplary embodiment, the pump device 10 provides both a vacuum outlet and a compressed fluid outlet that are used by the oxygen concentrator. For example, the port 165 of the first head 110a may provide the vacuum indicated by arrows 1999 and the second head 110b may pump the concentrated oxygen as indicated by arrows P. In this example, the vacuum providing head 110a may be used in place of the vacuum shown in FIG. 1 of U.S. Pat. No. 4,449,990. Also in this example, the vacuum providing head 110b may be used in place of the pump shown in FIG. 1 of U.S. Pat. No. 4,449,990. A pump 10 with a head that provides a vacuum and a head that provides compressed fluid may be used in a wide variety of different oxygen concentrator arrangements.
FIG. 20 corresponds to FIG. 1 of U.S. Pat. No. 5,917,135, except the compressor is replaced with a vacuum, such as a pump device 10 of the present application. In FIG. 20, the reference characters from U.S. Pat. No. 5,917,135 are prefixed with “20” so the reference characters would not conflict with other reference characters of this application. The oxygen concentrator 2000 functions in much the same way as the oxygen concentrator described in U.S. Pat. No. 5,917,135, except the air is alternately drawn into the sieve beds 2010, 2012 by a vacuum 10 as indicated by arrows 1999 instead of being alternately forced into the sieve beds 2010, 2012 by a compressor. An optional assist pump or pumps (indicated by arrows P) may be provided to convey oxygen enriched gas drawn through the sieve bed by the pump device 10 to the tank 2030. In one exemplary embodiment, the pump device 10 provides both a vacuum outlet and a compressed fluid outlet that are used by the oxygen concentrator. For example, the port 165 of the first head 110a may provide the vacuum indicated by arrows 1999 and the second head 110b may pump the concentrated oxygen as indicated by arrows P. In this example, an inlet port may be added to each of the cylinders 14C, 14D that receives the concentrated oxygen that is pumped as indicated by arrows P.
The foregoing description relates to a four-cylinder compressor. However, the features described in this application are applicable to compressors that have different numbers of cylinders. In addition, disclosed features may be used in compressors having cylinder heads with different check valve designs.
Several exemplary embodiments of pumping devices and oxygen concentrators are disclosed by this application. Pumping devices and oxygen concentrators in accordance with the present invention may include any combination or subcombination of the features disclosed by the present application.
While the present invention has been illustrated by the description of embodiments thereof, and while the embodiments have been described in considerable detail, it is not the intention of the applicant to restrict or in any way limit the scope of the appended claims to such detail. Additional advantages and modifications will readily appear to those skilled in the art. Still further, while cylindrical components have been shown and described herein, other geometries can be used including elliptical, polygonal (e.g., square, rectangular, triangular, hexagonal, etc.) and other shapes can also be used. Therefore, the invention, in its broader aspects, is not limited to the specific details, the representative apparatus, and illustrative examples shown and described. Accordingly, departures can be made from such details without departing from the spirit or scope of the applicant's general inventive concept.
Patent Application
20130209297
