US20050069431A1 - Piston mounting and balancing system - Google Patents
Piston mounting and balancing system Download PDFInfo
- Publication number
- US20050069431A1 US20050069431A1 US10/995,726 US99572604A US2005069431A1 US 20050069431 A1 US20050069431 A1 US 20050069431A1 US 99572604 A US99572604 A US 99572604A US 2005069431 A1 US2005069431 A1 US 2005069431A1
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- United States
- Prior art keywords
- piston
- assembly
- pistons
- mass
- drive shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B27/0404—Details, component parts specially adapted for such pumps
- F04B27/0414—Cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7879—Resilient material valve
- Y10T137/7888—With valve member flexing about securement
- Y10T137/7891—Flap or reed
- Y10T137/7892—With stop
Definitions
- the present invention relates to pumps and in particular to compact piston pumps.
- Pumps for medical applications such as used in oxygen concentrators, generally need to be compact and quiet to operate discreetly in homes and hospitals. It is thus important to properly muffle the working air as well as reduce vibration during operation of the pump.
- pistons may be coupled to the drive shaft by a single retainer or eccentric element between the connecting rods of the piston.
- an eccentric element is mounted to the drive shaft and two nibs or bosses extend axially from each side of the eccentric element to mount the pistons to the drive shaft.
- a moment, or shaking couple arises as the drive shaft is turn because of the axial spacing between the pistons.
- crankcase and cylinder(s) Another problem with conventional pumps is sealing the crankcase and cylinder(s). Improper sealing of the cylinders to the crankcase or the valve head(s) can cause pressurized air to leak to the outside of the pump, which both reduces pumping efficiency and makes noise. Typical sealing arrangements are either prone to leakage or require costly machining operations on the valve plate.
- many crankcases are made with open necks to allow the pistons to be slid into the crankcase easily during assembly. Typically, the openings in the neck terminate at the cylinders, which have curved exterior surfaces. This makes sealing the crankcase difficult and typically requires separate seals in addition to that sealing the end of the crankcase, thus increasing assembly complexity and creating a potential leak path between the neck seals and the end seal.
- valve stops can create excessive noise during operation.
- thin flapper valves are used to control the intake and exhaust ports of the valve heads. Because of the exhaust port opens under the force of the compressed air, a valve stop is used to support the valve and prevent it from being hyper-extended beyond its elastic range.
- the stops have undersides that ramp up from the valve plate to support the tip of the valve farther from the valve plate than the neck of the valve.
- the valves are usually metal and the stops can be metal or plastic, however, in either case the rapid contact between the two surfaces can generate tapping or clicking sounds that are unacceptable in medical applications.
- the thin flat flapper valve can succumb to surface attraction between the flapper and the stop and essentially “stick” to the stop and thus remain open.
- the invention provides a piston and drive shaft assembly for a pump or compressor.
- the invention includes two piston assemblies each having a head and a connecting rod.
- the connecting rods have openings in which fit open center bearings that mount to the drive shaft on eccentric elements.
- the piston assemblies each have a mass member of a different mass than that of the other mass member. The mass difference of the mass members is essentially equal to the mass difference of the two pistons so as to essentially equalize the total mass of each piston assembly.
- the invention further provides a pump or compressor having a motor with a drive shaft housed in a crankcase having a pair of cylinders. At least two mass balanced piston assemblies as described above are mounted to the drive shaft.
- the eccentric elements are separate disk shaped parts that having axial bores that allow them to fit onto the drive shaft.
- the eccentrics each have an axial dimension no more than substantially the axial dimension of the connecting rods, and the connecting rods are mounted to the drive shaft spaced apart no more than ⁇ fraction (1/16) ⁇ ′′.
- the eccentric elements are preferably press-fit into centers of inner races of the bearings.
- the mass members can be cup retainers mounted to the piston heads and weighted so that the moments effected on the drive shaft by the pistons are the about the same. For example, when one piston has a larger piston head and is thus heavier, a lighter would be mounted to the larger piston to equalize the total mass of each piston assembly.
- One way to accomplish this is to make the retainers of different sizes and/or materials. Different density metals or polymers could be used. For example, one retainer could be zinc and the other magnesium or aluminum, or both could be plastics of different densities or sizes or one could be a plastic and the other a metal.
- FIG. 1 is a perspective view an opposed piston pump of the present invention
- FIG. 2 is a perspective view of the pump showing its piston assemblies exploded
- FIG. 3 is another perspective view of the pump showing one of its cylinder and valve head assemblies exploded
- FIG. 4 is an exploded perspective view showing one valve assembly in isolation
- FIG. 5 is an enlarged partial cross-sectional view taken along arc 5 - 5 of FIG. 9 showing a cylinder seal in a circumferential groove in an angled end of the cylinder;
- FIG. 6 is an enlarged partial cross-sectional view taken along line 6 - 6 of FIG. 9 showing an assembly for sealing the open neck of the pump housing;
- FIG. 7 is a cross-sectional view taken along line 7 - 7 of FIG. 1 showing the pump (without the intake and exhaust valves) with its pistons 180° out of phase and one piston at top dead center and the other at bottom dead center and with the valve heads coupled;
- FIG. 8 is a cross-sectional view similar to FIG. 7 albeit with the pistons in a position 180° from that of FIG. 7 ;
- FIG. 9 is a cross-sectional similar to FIG. 7 showing the pump with its pistons in phase at bottom dead center and with one valve head exhausted to the crankcase and the other exhausted to the load;
- FIG. 10 is a cross-sectional view similar to FIG. 9 albeit showing the pistons at top dead center;
- FIG. 11 is a cross-sectional view taken along line 11 - 11 of FIG. 9 ;
- FIG. 12 is a cross-sectional view taken along line 12 - 12 of FIG. 9 ;
- FIG. 13 is an enlarged partial cross-sectional view showing one valve assembly
- FIG. 14 is a cross-sectional view taken along line 14 - 14 of FIG. 9 ;
- FIG. 15 is a cross-sectional view taken along line 15 - 15 of FIG. 14 with an exhaust side flapper valve closed;
- FIG. 16 is a view similar to FIG. 15 albeit with the valve shown open;
- FIG. 17 is a cross-sectional view taken along line 17 - 17 of FIG. 12 ;
- FIG. 18 is an enlarged partial cross-sectional view taken along arc 18 - 18 of FIG. 17 ;
- FIGS. 19-21 are enlarged partial cross-sectional view taken along line 19 - 19 of FIG. 17 showing various alternate constructions of a transfer tube;
- FIG. 22 is a perspective view of an alternate embodiment of the pump of the present invention with different sized cylinders and pistons;
- FIG. 23 is a cross-sectional view taken along line 23 - 23 of FIG. 22 showing the pump (without the intake and exhaust valves) operating as a pressure-vacuum pump with its pistons in phase at bottom dead center and with the larger valve head exhausted to the crankcase;
- FIG. 24 is a cross-sectional view similar to FIG. 23 albeit showing the pistons at top dead center;
- FIG. 25 is a cross-sectional view taken along line 25 - 25 of FIG. 22 .
- FIGS. 1-4 illustrate a pump 30 according to the present invention.
- the pump 30 has a motor 32 mounted in an inverted manner in a top opening 34 of a housing or crankcase 36 containing two piston assemblies 38 and 39 .
- Two cylinders 40 and 41 are mounted to the crankcase 36 in respective side openings 42 and 43 .
- Valve plates 44 and 45 and valve heads 46 and 47 are mounted to the outer ends of the respective cylinders 40 and 41 .
- a cover/seal assembly 48 is mounted to the open neck 50 of the crankcase 36 over a bottom end opening 52 so that the interior of the crankcase is completely enclosed when the pump is assembled.
- each cylinder is tapered radially inward to define an angled surface 54 (one shown in FIG. 5 ) with a circumferential groove 56 therein sized to a retain seal 58 , preferably a resilient o-ring.
- Each of the valve plates 44 and 45 have an underside with a circular angled surface 60 against which the seal 58 can seat when the pump is assembled.
- the cylinders 40 and 41 are clamped to the crankcase 36 by fasteners 63 connecting the valve heads 46 and 47 to the crankcase 36 which compresses the seals between the grooves and the respective seats of the valve plates.
- This assembly provides a good seal as well as promotes serviceability in that the angled surfaces reduce the occurrence of the o-ring sticking to the valve plate over time and locking the valve plate to the cylinder. Also, the inwardly angled seat can be formed during casting of the valve plate without the need for additional machining.
- the cover/seal assembly 48 improves the seal at the bottom opening 52 and open neck 50 of the crankcase 36 .
- the unique cover/seal assembly 48 includes a resilient seal 64 and a rigid backing plate 66 .
- the seal 64 is a generally ring shaped structure defining a central opening 68 and sized to fit onto the open end 52 of the crankcase 36 .
- the seal 64 defines two axially extending neck plugs 70 and 71 at opposite locations on the ring, for example at the 12 and 6 o'clock positions.
- the neck plugs 70 and 71 are sized and shaped to fit into the openings 72 and 73 in the neck 50 of the crankcase 36 .
- the neck plugs 70 and 71 define concave sealing surfaces 74 and 75 shaped to fit against the convex contour of the outside of the cylinders 40 and 41 .
- the sealing surfaces 74 and 75 have pointed ends that fit snugly against the intersecting surfaces of the neck 50 and the cylinders 40 and 41 (see FIG. 6 ).
- the seal 64 also defines two channel plugs 76 and 77 extending radially outward from the ring at the 3 and 9 o'clock positions. These channel plugs 76 and 77 fit into the end of channels 78 and 79 formed in the crankcase 36 (as discussed below).
- the seal 64 is retained by the backing plate 66 , which is generally a circular plate with four openings 80 through which four fasteners 82 are disposed to fasten the cover/seal assembly 48 to the crankcase 36 .
- the backing plate 66 has axially extending plug supports 84 and 85 aligned with the neck plugs 70 and 71 with curved edges 86 and 87 contacting ledges 88 and 89 defined by the neck plugs 70 and 71 .
- the backing plate 66 also has two tabs 57 and 59 located and sized to support respective channel plugs 76 and 77 of the seal 68 .
- the plug supports 84 and 85 help maintain the seal of the neck plugs 70 and 71 .
- the pointed corners of the neck plugs 70 and 71 can flex away from the crankcase and cylinders somewhat to allow a leak path to relieve transient high pressure situations.
- the seal is designed primarily for low pressure applications to seal off air leaks for noise reductions.
- the corners of the neck plugs will unseat slightly when the internal pressure reaches about 15 psi as a pressure relief.
- the assembly could, of course, be used in higher pressure applications by using a more rigid elastomer or modifying the backing plate to prevent the seal from unseating.
- the piston assemblies 38 and 39 each include pistons 90 and 91 and with heads 92 and 93 , forming pan sections having pistons seals 94 and 95 mounted by retainers 96 and 97 (shown in phantom), and connecting rods 98 and 99 defining circular openings 100 and 101 , respectively.
- Bearings 102 and 103 (having inner races 104 and 105 rotatable with respect to outer races 106 and 107 , respectively) press-fit into the respective openings 100 and 101 to fix the outer races to the connecting rods 98 and 99 .
- Circular eccentric elements 108 and 109 are then press-fit into respective openings 110 and 111 of the bearings to fix them to the respective inner races 104 and 105 .
- the eccentric elements 108 and 109 have through bores 112 and 113 radially offset from their centers.
- the piston assemblies 38 and 39 are press-fit onto a drive shaft 114 of the motor 32 one at a time in the through bores 112 and 113 of the eccentric elements 108 and 109 , respectively.
- the drive shaft 114 is journalled to the crankcase 36 by bearing 116 .
- the crankcase openings 42 and 43 and cylinders 40 and 41 are offset somewhat to account for the different axial locations of each piston assembly 38 and 39 so that piston 90 reciprocates along the centerline of cylinder 40 and piston 91 reciprocates along the centerline of cylinder 41 allowing the piston seals 94 and 95 of each assembly creating a sliding seal with the inner surfaces of the cylinders.
- the connecting rods 98 and 99 of the pistons 90 and 91 are mounted on the drive shaft 114 so that the connecting rods 98 and 99 are substantially adjacent to one another, that is within 1 ⁇ 8 inches (preferably less than ⁇ fraction (1/16) ⁇ ′′) or as close as possible.
- the pistons are mounted on the drive shaft as close as possible with only air space between the connecting rods. This is to reduce the moment or shaking couple about the drive shaft 114 caused by the axial displacement of the piston assemblies 38 and 39 . While some moment remains, this arrangement provides a significant improvement over the prior art in that there is no other element (eccentric or otherwise) on the shaft between the pistons so that their axial displacement is minimized.
- the pump 30 can operate as a parallel pressure or parallel vacuum pump in which the pistons reciprocate 180 degrees out of phase.
- FIG. 5 shows piston 90 at top dead center while piston 91 is at bottom dead center.
- FIG. 6 shows the pistons when the drive shaft is rotated 180 degrees so that piston 90 is at bottom dead center when piston 91 is at top dead center.
- This configuration of the pump results from the eccentric elements 108 and 109 being mounted to the drive shaft 114 so that the through bores 112 and 113 in positions opposite 180 degrees with respect to their pistons.
- the through bore 112 would be at a 12 o'clock position (toward the piston head) and the through bore 113 would be at a 6 o'clock position.
- FIGS. 9 and 10 show an alternate configuration in which the pump operates as a pressure-vacuum pump with the pistons reciprocating in phase (i.e., moving in and out of the cylinders in unison).
- the eccentric elements would be mounted to the drive shaft when both are in the same orientation with respect to their piston, for example, both through bores being at 12 o'clock.
- This version of the pump can be otherwise identical to that shown in FIGS. 1-4 .
- Air flow through the cylinders is controlled by the valving on the valve plates 44 and 45 .
- the valve plate 44 includes pairs of intake ports 120 and exhaust ports 122 .
- the pairs of intake 120 and exhaust 122 ports are separated by a partition 124 of the valve head 46 defining two intake 126 and exhaust 128 chambers.
- a specially shaped head seal 130 lies between the valve plate 44 and the valve head 46 to seal and isolate the two chambers 126 and 128 .
- the intake 120 and exhaust 122 ports are controlled by respective flapper valves 130 and 132 .
- the flapper valves 130 and 132 are identically shaped thin, metal valves.
- the valves 130 and 132 each have a middle section 134 defining an opening 136 and an alignment tab 139 as well as two identical paddles 140 extending from the middle section 130 in opposite directions approximately 30 degrees from vertical.
- the paddles 140 have narrow necks 142 and relative large flat heads 144 .
- the heads are sized slightly larger than the intake and exhaust ports and the necks are narrow to let the valves flex more easily under the force of the pressurized air, and thus reduce power consumption.
- Each flapper valve 130 and 132 is mounted to the valve plate 44 by a fastener 146 inserted through the opening 136 in the middle section 134 of the valve and threaded into bores in the valve plate.
- the intake valve 130 is mounted at the inside of the cylinder 40 and the exhaust valve 132 is mounted in the exhaust chamber 128 .
- valve stop 138 preferably made of a rigid plastic. No valve stop is used (besides the piston) for the intake valve which opens during the expansion stroke.
- the valve stop 138 has a middle body 148 with an alignment tab 149 and an opening therethrough for the fastener 146 .
- Two arms 150 extend out from the body 148 at the same angles as the valve paddles 140 .
- Two hands 152 have fingers or lobes 154 , preferably three, extending outward and spaced apart at equal angles.
- the underside of the arms 150 and hands 152 tapers away from the valve plate, preferably with a slight convex curve, so that the lobes 154 are spaced away from the valve plate 44 enough to allow the valve paddles 140 to move sufficiently to open the ports. As shown in FIG. 16 , the paddles follow the contour of the underside of the arms and lobes when opened and are supported along their entire length (except at the tips).
- the arms 150 are approximately the width of the valve paddle necks 142 and the lobes 154 are sized to support the entire paddle heads 144 to prevent them from hyper-extending at the narrow necks.
- the underside of the lobes 154 are of less surface area than the paddle heads 144 and end inside of the boundaries of the heads.
- valve stop design limits the surface contact between the paddles and thus reduces or eliminates valve chatter.
- This valve stop design has two main advantages: first, it reduces the surface attracting forces or “stiction” between these elements which could cause the valves to stick to the stop and remain open, and second, it reduces noise/vibration in the valves that would otherwise be present were the valve tips to contact the stops.
- the valves are mounted to the valve plates with their middle sections disposed over recesses 156 shaped like the middle sections only larger. This allows the valves to be assembled and aligned by a fixture having pins that extend below the underside of the valves and into the recesses 156 .
- the alignment tabs 139 and 149 ensure that the valve and stop are in the proper orientation.
- the pump 30 includes small tubular members 158 , preferably having two opposite flat sides, extending from intake 160 and exhaust 162 transfer ports through the valve plates outside of the cylinders.
- these transfer tubes 158 are formed as a unitary part of the valve plates (see FIGS. 17 and 19 ).
- each transfer tube 158 A is a separate rigid member with (or without) stepped ends mounting resilient seals 166 A.
- each transfer tube 158 B could be made of a entirely of a resilient material so that no separate seals are needed. Preferably, it would have stepped ends that fit inside the corresponding openings in the crankcase and valve plate.
- the crankcase 36 has two sets of interior passageways 170 and 171 in the walls of the crankcase opening at the transfer openings 164 and 165 .
- these passageways 170 and 171 may also open to the channels 78 and 79 , which open to the interior of the crankcase. This can be done by boring through section 174 or by casting the crankcase to block off or connect passageways as needed.
- the passageways 170 and 171 couple the exhaust chambers of each valve head and the intake chambers of each valve head.
- the load can be connected at a hose barb or socket of either of the intake chambers (to pull a vacuum) or either of the exhaust chambers (to provide pressure) or both, without connecting to both of the intake chambers and/or exhaust chambers.
- a suitable muffler (not shown) can be connected to either the intake or exhaust side if not otherwise connected to a load.
- FIGS. 22-25 show another preferred pressure-vacuum embodiment of the pump 30 C such as can be used in a medical application, such as an oxygen concentrating apparatus.
- This embodiment of the invention is identical to that described above, with the following exceptions.
- cylinder 40 C, valve plate 44 C, valve head 46 C and the head of piston assembly 38 C are of a lesser size (diameter) than cylinder 41 C, valve plate 45 C, valve head 47 C and the head of piston assembly 39 C, respectively.
- the smaller side is the pressure side and the cylinder 40 C has a 1.5 inch diameter and the larger side is the vacuum side with the cylinder 41 C having a 2 inch diameter.
- the piston assemblies 38 C and 39 C are in phase as shown in FIGS. 23 and 24 (although they could be out of phase as well), the pressure side providing roughly 5 to 10 psi of pressure and the vacuum side drawing a vacuum of about ⁇ 10 to ⁇ 5 psi, which is preferred for oxygen concentrator devices.
- the retainers 96 C and 97 C are selected to have different masses, substantially equal to the difference in the masses of the other parts of the pistons (such as the connecting rods and the heads/pans). This can be accomplished by making the retainers 96 C and 97 C from disparate materials or of different thicknesses. Different density metals or polymers could be used. Both could be metals or plastic of different densities or sizes, or one could be a plastic and the other a metal.
- the retainer 96 C is made of a suitable zinc composition so that it has a greater mass (despite its smaller diameter) than retainer 97 C, which is made of an aluminum.
- retainer 97 C which is made of an aluminum.
- the pump also differs from that described above in that it has only one transfer tube 158 C connecting the exhaust side of valve head 47 C to passageway 171 C (through a transfer opening) in the crankcase 36 C. Passageway 171 C intersects with channel 78 C (as shown in FIG. 25 ).
- the crankcase 36 C has no other internal passageways as did the previously described embodiment.
- This embodiment of the pump is thus constructed so that air can be drawn from the load (through a hose (not shown) connected to barb 200 ) and into the intake chamber of valve head 47 C. Surrounding air can also be brought in through barb 202 (to which preferably a muffler (not shown)) is mounted. Air from the higher pressure side valve head 46 C exhaust chamber will be exhausted through barb 204 to the load (after passing through hoses and valves as needed). The exhaust chamber of the vacuum side valve head 47 C will exhaust through the transfer tube 158 C and the crankcase passageway 171 C to the non-pressure side of the inside of the crankcase 36 C, which is vented through barb 206 and another muffler (not shown). Passing the exhaust through the crankcase prior to the muffler provides further (two-stage) sound attenuation beneficial in low-noise applications, such as when used with medical devices.
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- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
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Abstract
A compact 180° opposed piston pump/compressor minimizes axial spacing between its pistons on the drive shaft and has mass-balanced pistons designed to reduce the shaking couple and noise from reciprocation of the pistons. The piston assemblies can have members, such as cup retainers, that are of different masses selected to compensate for the difference in piston masses and thereby equalize the masses of the pistons. Each piston assembly can be mounted to the drive shaft at eccentrics that occupy minimal or no space between the pistons.
Description
- This application is a continuation-in-part of U.S. application Ser. No. 10/338,950, filed on Jan. 8, 2003, now allowed and issue fee paid.
- Not applicable.
- The present invention relates to pumps and in particular to compact piston pumps.
- Pumps for medical applications, such as used in oxygen concentrators, generally need to be compact and quiet to operate discreetly in homes and hospitals. It is thus important to properly muffle the working air as well as reduce vibration during operation of the pump.
- One problem with conventional pumps is that they can create excessive noise and vibration as the piston(s) are reciprocated, especially if they are improperly balanced. One reason for this in opposed piston pumps is that the pistons may be coupled to the drive shaft by a single retainer or eccentric element between the connecting rods of the piston. Ordinarily, an eccentric element is mounted to the drive shaft and two nibs or bosses extend axially from each side of the eccentric element to mount the pistons to the drive shaft. A moment, or shaking couple, arises as the drive shaft is turn because of the axial spacing between the pistons.
- Another problem with conventional pumps is sealing the crankcase and cylinder(s). Improper sealing of the cylinders to the crankcase or the valve head(s) can cause pressurized air to leak to the outside of the pump, which both reduces pumping efficiency and makes noise. Typical sealing arrangements are either prone to leakage or require costly machining operations on the valve plate. Also, many crankcases are made with open necks to allow the pistons to be slid into the crankcase easily during assembly. Typically, the openings in the neck terminate at the cylinders, which have curved exterior surfaces. This makes sealing the crankcase difficult and typically requires separate seals in addition to that sealing the end of the crankcase, thus increasing assembly complexity and creating a potential leak path between the neck seals and the end seal.
- Another problem with conventional pumps is that the valve stops can create excessive noise during operation. Typically, thin flapper valves are used to control the intake and exhaust ports of the valve heads. Because of the exhaust port opens under the force of the compressed air, a valve stop is used to support the valve and prevent it from being hyper-extended beyond its elastic range. Usually the stops have undersides that ramp up from the valve plate to support the tip of the valve farther from the valve plate than the neck of the valve. The valves are usually metal and the stops can be metal or plastic, however, in either case the rapid contact between the two surfaces can generate tapping or clicking sounds that are unacceptable in medical applications. Another problem here is that the thin flat flapper valve can succumb to surface attraction between the flapper and the stop and essentially “stick” to the stop and thus remain open.
- Yet another problem confronting the design of low-noise pumps is properly muffling the intake and/or exhaust chambers of the valve heads. This can be done by attaching a muffler element to the valve head either direction or via suitable hoses. Another technique is to run the exhaust air into the crankcase on the non-pressure side of the piston head. In this case, if the crankcase is closed and the pistons are in phase, the crankcase will usually be vented through a muffler to avoid generating pulsations in the pump. Even using the later technique, the valve heads are usually exhausted through hoses leading to the crankcase, which is vented through a muffler directly mounted to the crankcase or at the end of a hose.
- Accordingly, an improved pump is needed which addresses the aforementioned problems.
- In accordance with one aspect, the invention provides a piston and drive shaft assembly for a pump or compressor. The invention includes two piston assemblies each having a head and a connecting rod. The connecting rods have openings in which fit open center bearings that mount to the drive shaft on eccentric elements. The piston assemblies each have a mass member of a different mass than that of the other mass member. The mass difference of the mass members is essentially equal to the mass difference of the two pistons so as to essentially equalize the total mass of each piston assembly.
- The invention further provides a pump or compressor having a motor with a drive shaft housed in a crankcase having a pair of cylinders. At least two mass balanced piston assemblies as described above are mounted to the drive shaft.
- In preferred forms, the eccentric elements are separate disk shaped parts that having axial bores that allow them to fit onto the drive shaft. Preferably, the eccentrics each have an axial dimension no more than substantially the axial dimension of the connecting rods, and the connecting rods are mounted to the drive shaft spaced apart no more than {fraction (1/16)}″. The eccentric elements are preferably press-fit into centers of inner races of the bearings.
- The mass members can be cup retainers mounted to the piston heads and weighted so that the moments effected on the drive shaft by the pistons are the about the same. For example, when one piston has a larger piston head and is thus heavier, a lighter would be mounted to the larger piston to equalize the total mass of each piston assembly. One way to accomplish this is to make the retainers of different sizes and/or materials. Different density metals or polymers could be used. For example, one retainer could be zinc and the other magnesium or aluminum, or both could be plastics of different densities or sizes or one could be a plastic and the other a metal.
- The invention thus provides a compact pump or compressor with decreased shaking couple on the drive shaft and thus lower noise and improved pump efficiency. These and other advantages of the invention will be apparent from the detailed description and drawings. What follows is a description of the preferred embodiments of the present invention. To assess the full scope of the invention the claims should be looked to as the preferred embodiments are not intended as the only embodiments within the scope of the invention.
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FIG. 1 is a perspective view an opposed piston pump of the present invention; -
FIG. 2 is a perspective view of the pump showing its piston assemblies exploded; -
FIG. 3 is another perspective view of the pump showing one of its cylinder and valve head assemblies exploded; -
FIG. 4 is an exploded perspective view showing one valve assembly in isolation; -
FIG. 5 is an enlarged partial cross-sectional view taken along arc 5-5 ofFIG. 9 showing a cylinder seal in a circumferential groove in an angled end of the cylinder; -
FIG. 6 is an enlarged partial cross-sectional view taken along line 6-6 ofFIG. 9 showing an assembly for sealing the open neck of the pump housing; -
FIG. 7 is a cross-sectional view taken along line 7-7 ofFIG. 1 showing the pump (without the intake and exhaust valves) with its pistons 180° out of phase and one piston at top dead center and the other at bottom dead center and with the valve heads coupled; -
FIG. 8 is a cross-sectional view similar toFIG. 7 albeit with the pistons in a position 180° from that ofFIG. 7 ; -
FIG. 9 is a cross-sectional similar toFIG. 7 showing the pump with its pistons in phase at bottom dead center and with one valve head exhausted to the crankcase and the other exhausted to the load; -
FIG. 10 is a cross-sectional view similar toFIG. 9 albeit showing the pistons at top dead center; -
FIG. 11 is a cross-sectional view taken along line 11-11 ofFIG. 9 ; -
FIG. 12 is a cross-sectional view taken along line 12-12 ofFIG. 9 ; -
FIG. 13 is an enlarged partial cross-sectional view showing one valve assembly; -
FIG. 14 is a cross-sectional view taken along line 14-14 ofFIG. 9 ; -
FIG. 15 is a cross-sectional view taken along line 15-15 ofFIG. 14 with an exhaust side flapper valve closed; -
FIG. 16 is a view similar toFIG. 15 albeit with the valve shown open; -
FIG. 17 is a cross-sectional view taken along line 17-17 ofFIG. 12 ; -
FIG. 18 is an enlarged partial cross-sectional view taken along arc 18-18 ofFIG. 17 ; -
FIGS. 19-21 are enlarged partial cross-sectional view taken along line 19-19 ofFIG. 17 showing various alternate constructions of a transfer tube; -
FIG. 22 is a perspective view of an alternate embodiment of the pump of the present invention with different sized cylinders and pistons; -
FIG. 23 is a cross-sectional view taken along line 23-23 ofFIG. 22 showing the pump (without the intake and exhaust valves) operating as a pressure-vacuum pump with its pistons in phase at bottom dead center and with the larger valve head exhausted to the crankcase; -
FIG. 24 is a cross-sectional view similar toFIG. 23 albeit showing the pistons at top dead center; and -
FIG. 25 is a cross-sectional view taken along line 25-25 ofFIG. 22 . -
FIGS. 1-4 illustrate apump 30 according to the present invention. Generally, thepump 30 has amotor 32 mounted in an inverted manner in atop opening 34 of a housing orcrankcase 36 containing twopiston assemblies cylinders crankcase 36 inrespective side openings Valve plates valve heads respective cylinders seal assembly 48 is mounted to theopen neck 50 of thecrankcase 36 over a bottom end opening 52 so that the interior of the crankcase is completely enclosed when the pump is assembled. - Referring to
FIGS. 1, 3 and 5, more specifically, to improve the seal between thecylinders valve plates FIG. 5 ) with acircumferential groove 56 therein sized to aretain seal 58, preferably a resilient o-ring. Each of thevalve plates angled surface 60 against which theseal 58 can seat when the pump is assembled. Thecylinders crankcase 36 byfasteners 63 connecting the valve heads 46 and 47 to thecrankcase 36 which compresses the seals between the grooves and the respective seats of the valve plates. This assembly provides a good seal as well as promotes serviceability in that the angled surfaces reduce the occurrence of the o-ring sticking to the valve plate over time and locking the valve plate to the cylinder. Also, the inwardly angled seat can be formed during casting of the valve plate without the need for additional machining. - Referring to
FIGS. 2 and 6 , the cover/seal assembly 48 improves the seal at thebottom opening 52 andopen neck 50 of thecrankcase 36. The unique cover/seal assembly 48 includes aresilient seal 64 and arigid backing plate 66. In particular, theseal 64 is a generally ring shaped structure defining acentral opening 68 and sized to fit onto theopen end 52 of thecrankcase 36. Theseal 64 defines two axially extending neck plugs 70 and 71 at opposite locations on the ring, for example at the 12 and 6 o'clock positions. The neck plugs 70 and 71 are sized and shaped to fit into theopenings neck 50 of thecrankcase 36. The neck plugs 70 and 71 define concave sealing surfaces 74 and 75 shaped to fit against the convex contour of the outside of thecylinders neck 50 and thecylinders 40 and 41 (seeFIG. 6 ). Theseal 64 also defines two channel plugs 76 and 77 extending radially outward from the ring at the 3 and 9 o'clock positions. These channel plugs 76 and 77 fit into the end ofchannels 78 and 79 formed in the crankcase 36 (as discussed below). Theseal 64 is retained by thebacking plate 66, which is generally a circular plate with fouropenings 80 through which fourfasteners 82 are disposed to fasten the cover/seal assembly 48 to thecrankcase 36. Thebacking plate 66 has axially extending plug supports 84 and 85 aligned with the neck plugs 70 and 71 withcurved edges ledges backing plate 66 also has twotabs seal 68. - The plug supports 84 and 85 help maintain the seal of the neck plugs 70 and 71. However, the pointed corners of the neck plugs 70 and 71 can flex away from the crankcase and cylinders somewhat to allow a leak path to relieve transient high pressure situations. The seal is designed primarily for low pressure applications to seal off air leaks for noise reductions. The corners of the neck plugs will unseat slightly when the internal pressure reaches about 15 psi as a pressure relief. The assembly could, of course, be used in higher pressure applications by using a more rigid elastomer or modifying the backing plate to prevent the seal from unseating.
- Referring to
FIG. 2 , thepiston assemblies pistons heads retainers 96 and 97 (shown in phantom), and connectingrods circular openings Bearings 102 and 103 (havinginner races outer races respective openings rods eccentric elements respective openings inner races eccentric elements bores - Referring to
FIGS. 7, 8 , 11 and 12, thepiston assemblies drive shaft 114 of themotor 32 one at a time in the throughbores eccentric elements drive shaft 114 is journalled to thecrankcase 36 by bearing 116. Thecrankcase openings cylinders piston assembly piston 90 reciprocates along the centerline ofcylinder 40 andpiston 91 reciprocates along the centerline ofcylinder 41 allowing the piston seals 94 and 95 of each assembly creating a sliding seal with the inner surfaces of the cylinders. - Importantly, the connecting
rods pistons drive shaft 114 so that the connectingrods drive shaft 114 caused by the axial displacement of thepiston assemblies - As shown in
FIGS. 7 and 8 , thepump 30 can operate as a parallel pressure or parallel vacuum pump in which the pistons reciprocate 180 degrees out of phase.FIG. 5 showspiston 90 at top dead center whilepiston 91 is at bottom dead center.FIG. 6 shows the pistons when the drive shaft is rotated 180 degrees so thatpiston 90 is at bottom dead center whenpiston 91 is at top dead center. This configuration of the pump results from theeccentric elements drive shaft 114 so that the throughbores bore 112 would be at a 12 o'clock position (toward the piston head) and the throughbore 113 would be at a 6 o'clock position. -
FIGS. 9 and 10 show an alternate configuration in which the pump operates as a pressure-vacuum pump with the pistons reciprocating in phase (i.e., moving in and out of the cylinders in unison). In this case, the eccentric elements would be mounted to the drive shaft when both are in the same orientation with respect to their piston, for example, both through bores being at 12 o'clock. This version of the pump can be otherwise identical to that shown inFIGS. 1-4 . - Air flow through the cylinders is controlled by the valving on the
valve plates FIGS. 3, 4 , and 13-16, thevalve plate 44 includes pairs ofintake ports 120 andexhaust ports 122. The pairs ofintake 120 andexhaust 122 ports are separated by a partition 124 of thevalve head 46 defining twointake 126 and exhaust 128 chambers. A specially shapedhead seal 130 lies between thevalve plate 44 and thevalve head 46 to seal and isolate the twochambers - The
intake 120 andexhaust 122 ports are controlled byrespective flapper valves flapper valves valves middle section 134 defining anopening 136 and analignment tab 139 as well as twoidentical paddles 140 extending from themiddle section 130 in opposite directions approximately 30 degrees from vertical. Thepaddles 140 havenarrow necks 142 and relative largeflat heads 144. The heads are sized slightly larger than the intake and exhaust ports and the necks are narrow to let the valves flex more easily under the force of the pressurized air, and thus reduce power consumption. Eachflapper valve valve plate 44 by afastener 146 inserted through theopening 136 in themiddle section 134 of the valve and threaded into bores in the valve plate. Theintake valve 130 is mounted at the inside of thecylinder 40 and theexhaust valve 132 is mounted in theexhaust chamber 128. - Referring to
FIGS. 4 and 13 -16, because theexhaust valve 132 opens under the force of the compressed air in the cylinder, it is backed by avalve stop 138 preferably made of a rigid plastic. No valve stop is used (besides the piston) for the intake valve which opens during the expansion stroke. In particular, thevalve stop 138 has amiddle body 148 with analignment tab 149 and an opening therethrough for thefastener 146. Twoarms 150 extend out from thebody 148 at the same angles as the valve paddles 140. Twohands 152 have fingers orlobes 154, preferably three, extending outward and spaced apart at equal angles. The underside of thearms 150 andhands 152 tapers away from the valve plate, preferably with a slight convex curve, so that thelobes 154 are spaced away from thevalve plate 44 enough to allow the valve paddles 140 to move sufficiently to open the ports. As shown inFIG. 16 , the paddles follow the contour of the underside of the arms and lobes when opened and are supported along their entire length (except at the tips). Thearms 150 are approximately the width of thevalve paddle necks 142 and thelobes 154 are sized to support the entire paddle heads 144 to prevent them from hyper-extending at the narrow necks. Collectively, the underside of thelobes 154 are of less surface area than the paddle heads 144 and end inside of the boundaries of the heads. This design limits the surface contact between the paddles and thus reduces or eliminates valve chatter. This valve stop design has two main advantages: first, it reduces the surface attracting forces or “stiction” between these elements which could cause the valves to stick to the stop and remain open, and second, it reduces noise/vibration in the valves that would otherwise be present were the valve tips to contact the stops. It should also be noted that the valves are mounted to the valve plates with their middle sections disposed overrecesses 156 shaped like the middle sections only larger. This allows the valves to be assembled and aligned by a fixture having pins that extend below the underside of the valves and into therecesses 156. Thealignment tabs - Another feature of the
pump 30 is the use oftransfer tubes 158 with air passageways formed in the body of the crankcase 36 (outside of the internal chamber) to either couple an intake or exhaust chamber to the inside of the crankcase or to couple the valve heads together (in parallel between exhaust chambers and/or between intake chambers or in series with the exhaust chamber of one valve head connected to the intake chamber of the other valve head) without the need for hoses. Referring now toFIGS. 11, 12 and 17-21, thepump 30 includes smalltubular members 158, preferably having two opposite flat sides, extending fromintake 160 andexhaust 162 transfer ports through the valve plates outside of the cylinders. In one preferred form, thesetransfer tubes 158 are formed as a unitary part of the valve plates (seeFIGS. 17 and 19 ). The free ends of thetransfer tubes 158 are coupled to two sets oftransfer openings resilient seal 166 therebetween having a flange 168 that fits inside thetransfer openings FIGS. 20 and 21 in which they are entirely separate elements. InFIG. 20 , eachtransfer tube 158A is a separate rigid member with (or without) stepped ends mountingresilient seals 166A. Or, as shown inFIG. 21 , eachtransfer tube 158B could be made of a entirely of a resilient material so that no separate seals are needed. Preferably, it would have stepped ends that fit inside the corresponding openings in the crankcase and valve plate. - As mentioned, the
crankcase 36 has two sets ofinterior passageways transfer openings passageways channels 78 and 79, which open to the interior of the crankcase. This can be done by boring throughsection 174 or by casting the crankcase to block off or connect passageways as needed. In the parallel pressure embodiment of the pump shown inFIGS. 11, 17 and 18, preferably thepassageways -
FIGS. 22-25 show another preferred pressure-vacuum embodiment of thepump 30C such as can be used in a medical application, such as an oxygen concentrating apparatus. This embodiment of the invention is identical to that described above, with the following exceptions. Here,cylinder 40C,valve plate 44C,valve head 46C and the head ofpiston assembly 38C are of a lesser size (diameter) thancylinder 41C,valve plate 45C,valve head 47C and the head ofpiston assembly 39C, respectively. Preferably, the smaller side is the pressure side and thecylinder 40C has a 1.5 inch diameter and the larger side is the vacuum side with thecylinder 41C having a 2 inch diameter. Preferably, in this embodiment, thepiston assemblies FIGS. 23 and 24 (although they could be out of phase as well), the pressure side providing roughly 5 to 10 psi of pressure and the vacuum side drawing a vacuum of about −10 to −5 psi, which is preferred for oxygen concentrator devices. - Since the pistons are of different sizes, they have different masses. The difference in masses will make the pistons out of balance and thus effect unequal moments on the drive shaft, which would cause vibration, noise and lower pump efficiency. Preferably, the
retainers retainers retainer 96C is made of a suitable zinc composition so that it has a greater mass (despite its smaller diameter) thanretainer 97C, which is made of an aluminum. Thus, theheavier retainer 96C would make up the difference in mass of the smaller piston 90C. The result is equally balanced piston assemblies and improved operation of the pump when the application requires different flow volumes in the cylinders. - The pump also differs from that described above in that it has only one
transfer tube 158C connecting the exhaust side ofvalve head 47C topassageway 171C (through a transfer opening) in thecrankcase 36C.Passageway 171C intersects withchannel 78C (as shown inFIG. 25 ). Thecrankcase 36C has no other internal passageways as did the previously described embodiment. - This embodiment of the pump is thus constructed so that air can be drawn from the load (through a hose (not shown) connected to barb 200) and into the intake chamber of
valve head 47C. Surrounding air can also be brought in through barb 202 (to which preferably a muffler (not shown)) is mounted. Air from the higher pressureside valve head 46C exhaust chamber will be exhausted throughbarb 204 to the load (after passing through hoses and valves as needed). The exhaust chamber of the vacuumside valve head 47C will exhaust through thetransfer tube 158C and thecrankcase passageway 171 C to the non-pressure side of the inside of thecrankcase 36C, which is vented throughbarb 206 and another muffler (not shown). Passing the exhaust through the crankcase prior to the muffler provides further (two-stage) sound attenuation beneficial in low-noise applications, such as when used with medical devices. - It should be appreciated that preferred embodiments of the invention have been described above. However, many modifications and variations to these preferred embodiments will be apparent to those skilled in the art, which will be within the spirit and scope of the invention. For example, while only two-cylinder embodiments were shown, the principles of the invention could apply to a single-cylinder pump or to three or four cylinder pumps, such pumps having a double shafted motor and additional crankcases, cylinders, pistons and valve heads. For multi-cylinder pumps, the valve heads of all of the cylinders could be coupled in series or parallel through the transfer tubes and integral crankcase passageways, like those described above. Shared valve heads for multiple cylinders could also be incorporated into such a pump. The pump of the present invention could also include transfer tubes which connect directly to the valve heads/plates to join air chambers without connected to passageways in the crankcase.
- Therefore, the invention should not be limited to the described embodiments. To ascertain the full scope of the invention, the following claims should be referenced.
Claims (16)
1. A piston and drive shaft assembly for a pump, comprising at least two piston assemblies having:
first and second pistons each having a head and a connecting rod, the connecting rods defining respective first and second openings;
first and second bearings disposed in the first and second openings and having open centers;
first and second eccentric elements disposed in the centers of the respective first and second bearings; and
first and second mass members coupled to the respective first and second pistons having different masses essentially equal to a mass difference of the first and second pistons so as to essentially equalize the total mass of each piston assembly.
2. The assembly of claim 1 , wherein the eccentric elements are disk shaped.
3. The assembly of claim 1 , wherein the first and second bearings each have an outer race rotatable with respect an inner race defining the center opening and wherein the outer races are press-fit in the first and second openings of the connecting rods and the eccentric elements are press-fit into the openings defined by the inner races.
4. The assembly of claim 1 , wherein the first and second mass members are retainers mounted to the heads of the respective first and second pistons, wherein the first piston has a greater mass than the second piston and the first retainer has a lesser mass than the second retainer.
5. The assembly of claim 4 , wherein the first retainer is made of a different material than the second retainer.
6. The assembly of claim 5 , wherein the first retainer is zinc and the second retainer is magnesium.
7. The assembly of claim 5 , wherein the first retainer is zinc and the second retainer is aluminum.
8. The assembly of claim 1 , wherein the connecting rods of the first and second pistons are mounted to the drive shaft spaced apart no more than {fraction (1/16)} inch.
9. The assembly of claim 1 , wherein the first eccentric element has an axial dimension no more than substantially the axial dimension of the first piston connecting rod and the second eccentric element has an axial dimension no more than substantially the axial dimension of the second piston connecting rod.
10. The assembly of claim 1 , wherein the first and second eccentric elements each have an axial through bore and extend axially to one side substantially no further than a face of the corresponding piston connecting rod.
11. The assembly of claim 1 , wherein at least on of the first and second retainers is plastic.
12. A pump, comprising;
a motor having a drive shaft;
a crankcase housing the drive shaft and having a pair of cylinders;
at least two piston assemblies including:
two pistons each having a head disposed in one of the cylinders and a connecting rod extending from the head to the drive shaft;
two bearings disposed in openings in the connecting rods axially offset along the drive shaft;
two eccentric elements disposed in the bearings; and
two mass members coupled to the pistons having different masses essentially equal to a mass difference of the pistons so as to essentially equalize the total mass of each piston assembly.
13. The pump of claim 12 , wherein the mass members are cup retainers attached to the piston heads so that the center of gravity is at essentially the same location of each piston.
14. The pump of claim 12 , wherein the eccentric members have axial through bores receiving the drive shaft.
15. A pump or compressor comprising a pair of piston assemblies, each assembly having a piston with a head and a connecting rod, which mounts a bearing that is rotatably mountable to a drive shaft by an eccentric element, and a mass member coupled to the piston, wherein the mass member of one assembly is different than that of the other assembly such that a mass difference of the mass members is essentially equal to a mass difference of the pistons.
16. The pump or compressor of claim 15 , wherein each of the mass members is selected from the group of materials including metals and polymers.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/995,726 US20050069431A1 (en) | 2003-01-08 | 2004-11-22 | Piston mounting and balancing system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/338,950 US6832900B2 (en) | 2003-01-08 | 2003-01-08 | Piston mounting and balancing system |
US10/995,726 US20050069431A1 (en) | 2003-01-08 | 2004-11-22 | Piston mounting and balancing system |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US10/338,950 Continuation-In-Part US6832900B2 (en) | 2003-01-08 | 2003-01-08 | Piston mounting and balancing system |
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US20050069431A1 true US20050069431A1 (en) | 2005-03-31 |
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Family Applications (6)
Application Number | Title | Priority Date | Filing Date |
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US10/338,950 Expired - Lifetime US6832900B2 (en) | 2003-01-08 | 2003-01-08 | Piston mounting and balancing system |
US10/995,715 Expired - Fee Related US7220109B2 (en) | 2003-01-08 | 2004-11-22 | Pump cylinder seal |
US10/995,726 Abandoned US20050069431A1 (en) | 2003-01-08 | 2004-11-22 | Piston mounting and balancing system |
US10/995,725 Expired - Lifetime US7037090B2 (en) | 2003-01-08 | 2004-11-22 | Crankcase sealing apparatus |
US11/007,111 Abandoned US20050100458A1 (en) | 2003-01-08 | 2004-12-08 | Pump with transfer tube |
US11/007,125 Abandoned US20050098222A1 (en) | 2003-01-08 | 2004-12-08 | Flapper valve mounting structure |
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Application Number | Title | Priority Date | Filing Date |
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US10/338,950 Expired - Lifetime US6832900B2 (en) | 2003-01-08 | 2003-01-08 | Piston mounting and balancing system |
US10/995,715 Expired - Fee Related US7220109B2 (en) | 2003-01-08 | 2004-11-22 | Pump cylinder seal |
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US10/995,725 Expired - Lifetime US7037090B2 (en) | 2003-01-08 | 2004-11-22 | Crankcase sealing apparatus |
US11/007,111 Abandoned US20050100458A1 (en) | 2003-01-08 | 2004-12-08 | Pump with transfer tube |
US11/007,125 Abandoned US20050098222A1 (en) | 2003-01-08 | 2004-12-08 | Flapper valve mounting structure |
Country Status (8)
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US (6) | US6832900B2 (en) |
EP (3) | EP1911973A3 (en) |
JP (3) | JP4482337B2 (en) |
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AT (1) | ATE380938T1 (en) |
CA (1) | CA2454752A1 (en) |
DE (1) | DE60318005T2 (en) |
HK (3) | HK1067685A1 (en) |
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Citations (45)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1629445A (en) * | 1925-07-07 | 1927-05-17 | Cornelius W Van Ranst | Method of balancing pistons |
US1634949A (en) * | 1925-07-23 | 1927-07-05 | Ingersoll Rand Co | Air-compressor valve |
US1669889A (en) * | 1922-04-17 | 1928-05-15 | Couzens Ice Machine Company | Compressor valve |
US1795445A (en) * | 1927-11-21 | 1931-03-10 | Walter G E Rolaff | Reciprocating compressor |
US1821862A (en) * | 1929-06-24 | 1931-09-01 | Wylie G Wilson | Sealing ring for joints |
US2170443A (en) * | 1936-09-09 | 1939-08-22 | Barbarou Marius Jean-Baptiste | Mounting of cylinders in motors |
US2302447A (en) * | 1941-08-30 | 1942-11-17 | Gen Electric | Compressor valve |
US2323068A (en) * | 1941-03-29 | 1943-06-29 | Maniscalco Pictro | Compressor |
US2609660A (en) * | 1946-02-25 | 1952-09-09 | Tenney | Resonating pulse jet engine |
US2725183A (en) * | 1951-01-10 | 1955-11-29 | Carrier Corp | Valves for reciprocating compressors |
US2856249A (en) * | 1955-01-11 | 1958-10-14 | Maquinaria Petrolifera S A | High-pressure pump liner and packing |
US3606361A (en) * | 1968-03-15 | 1971-09-20 | Ulrich Pohl | Flat gasket for the cylinder head of combustion engines and process for making same |
US3744261A (en) * | 1972-03-16 | 1973-07-10 | Hughes Aircraft Co | Cryogenic refrigerator |
US3839946A (en) * | 1972-05-24 | 1974-10-08 | Hardie Tynes Mfg Co | Nonlubricated compressor |
US3998571A (en) * | 1975-04-14 | 1976-12-21 | Sundstrand Corporation | Valve retainer |
US4073221A (en) * | 1976-06-21 | 1978-02-14 | Caterpillar Tractor Co. | Light-weight piston assemblies |
US4190402A (en) * | 1975-05-06 | 1980-02-26 | International Telephone And Telegraph Corporation | Integrated high capacity compressor |
US4246123A (en) * | 1979-04-20 | 1981-01-20 | Sherwood Medical Industries Inc. | Fluid collection device with phase partitioning means |
US4319498A (en) * | 1979-06-11 | 1982-03-16 | Mcwhorter Edward M | Reciprocating engine |
US4479419A (en) * | 1982-11-02 | 1984-10-30 | Westinghouse Electric Corp. | Dual capacity reciprocating compressor |
US4507059A (en) * | 1983-02-01 | 1985-03-26 | Kabushiki Kaisha Toyoda Jidoshokki Seisa-Kusho | Variable delivery compressor |
US4529365A (en) * | 1980-08-29 | 1985-07-16 | Durr-Dental Gmbh & Co., Kg | Compressor with longitudinally extending cooling fins |
US4550571A (en) * | 1983-12-28 | 1985-11-05 | Helix Technology Corporation | Balanced integral Stirling cryogenic refrigerator |
US4817967A (en) * | 1987-12-11 | 1989-04-04 | Dana Corporation | Angled junction sealing structure for gaskets |
US4929157A (en) * | 1987-11-23 | 1990-05-29 | Ford Motor Company | Pulsation damper for air conditioning compressor |
US5035050A (en) * | 1989-02-15 | 1991-07-30 | Tecumseh Products Company | Method of installing a valve assembly in a compressor |
US5110272A (en) * | 1989-06-07 | 1992-05-05 | Aspera S.R.L. | Valve unit for a reciprocating compressor for refrigerators and the like |
US5213125A (en) * | 1992-05-28 | 1993-05-25 | Thomas Industries Inc. | Valve plate with a recessed valve assembly |
US5327932A (en) * | 1993-04-19 | 1994-07-12 | Thomas Industries Inc. | Valve restraint enhancement |
US5456287A (en) * | 1994-10-03 | 1995-10-10 | Thomas Industries Inc. | Compressor/vacuum pump reed valve |
US5515769A (en) * | 1994-06-28 | 1996-05-14 | Carrier Corporation | Air compressor |
US5620166A (en) * | 1994-08-02 | 1997-04-15 | Lord; Bruce A. | Stem and nut with bearing for use in a motor operated valve |
US5879145A (en) * | 1995-01-17 | 1999-03-09 | Knorr-Bremse Systems Fur Nutzfahrzeuge Gmbh | Integrated cylinder liner and valve plate for a compressor |
US5934305A (en) * | 1996-09-12 | 1999-08-10 | Samsung Electronics Co., Ltd. | Method of manufacturing a reciprocating compressor |
US5961127A (en) * | 1996-01-12 | 1999-10-05 | Honda Giken Kogyo Kabushiki Kaisha | Sealing structure for cylinder and cylinder head in reciprocating type internal combustion engine and assembling method thereof |
US6036194A (en) * | 1996-09-16 | 2000-03-14 | Cummins Engine Company, Inc. | Combustion gas seal for an internal combustion engine |
US6148716A (en) * | 1998-12-16 | 2000-11-21 | Impact Mst Incorporated | Low noise high efficiency positive displacement pump |
US6314990B1 (en) * | 1997-12-17 | 2001-11-13 | Verdichter Oe. Ges. M.B.H. | Pressure valve for a compressor |
US6431840B1 (en) * | 1999-09-09 | 2002-08-13 | Sanyo Electric Co., Ltd. | Multistage high pressure compressor |
US6485266B2 (en) * | 2000-03-10 | 2002-11-26 | Thomas Industries, Inc. | Compressor assembly with deflector |
US6513544B1 (en) * | 1999-08-13 | 2003-02-04 | Orbital Engine Company (Australia) Pty Limited | Compressor valve arrangement |
US6595525B2 (en) * | 2001-01-25 | 2003-07-22 | Glen D. Schmidt | Attachable sealant bead and strip for use with a vehicle part |
US6679688B2 (en) * | 2001-02-14 | 2004-01-20 | Sanyo Electric Co., Ltd. | Reed valve restriction plate with anti-sticking means |
US6832900B2 (en) * | 2003-01-08 | 2004-12-21 | Thomas Industries Inc. | Piston mounting and balancing system |
US6843643B2 (en) * | 2001-11-06 | 2005-01-18 | Oken Seiko Co., Ltd. | Valve mounting arrangement in a diaphragm pump |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1156795A (en) * | 1956-09-18 | 1958-05-21 | Motion transmission device and its applications | |
US4679994A (en) * | 1981-03-09 | 1987-07-14 | Allied Corporation | Piston vacuum pump |
US4784396A (en) * | 1987-06-01 | 1988-11-15 | Ford Motor Company | Retaining clip and gasket for engine subassembly |
US4931000A (en) * | 1989-03-02 | 1990-06-05 | Gilian Instrument Corp. | Double acting diaphragm air pump |
JPH0526159A (en) * | 1991-07-19 | 1993-02-02 | Sanden Corp | Cam plate type compressor |
JP2792277B2 (en) * | 1991-08-13 | 1998-09-03 | 株式会社豊田自動織機製作所 | Compressor discharge valve device |
US5226801A (en) * | 1992-08-17 | 1993-07-13 | Cobile Alfredo P | Shock absorber type compressor |
JP3103722B2 (en) * | 1994-07-14 | 2000-10-30 | 東芝テック株式会社 | Fluid pump |
IT1287150B1 (en) * | 1996-11-11 | 1998-08-04 | Roberto Siviero | ALTERNATIVE PUMP WITH COAXIAL VALVES IN SPECIES FOR RIBS AND SIMILAR WITH MANUAL AND MOTORIZED OPERATION |
JP2001304109A (en) * | 2000-04-28 | 2001-10-31 | Toyota Industries Corp | Swash plate compressor |
JP2002310301A (en) * | 2001-04-10 | 2002-10-23 | Zexel Valeo Climate Control Corp | Sealing member and cooling medium compressor with sealing member |
-
2003
- 2003-01-08 US US10/338,950 patent/US6832900B2/en not_active Expired - Lifetime
- 2003-12-31 EP EP20070119272 patent/EP1911973A3/en not_active Withdrawn
- 2003-12-31 DE DE2003618005 patent/DE60318005T2/en not_active Expired - Lifetime
- 2003-12-31 EP EP20070119270 patent/EP1911972B1/en not_active Expired - Lifetime
- 2003-12-31 EP EP20030029999 patent/EP1437507B1/en not_active Expired - Lifetime
- 2003-12-31 AT AT03029999T patent/ATE380938T1/en not_active IP Right Cessation
-
2004
- 2004-01-05 CA CA 2454752 patent/CA2454752A1/en not_active Abandoned
- 2004-01-06 JP JP2004001062A patent/JP4482337B2/en not_active Expired - Fee Related
- 2004-01-08 CN CNA2007101860471A patent/CN101173655A/en active Pending
- 2004-01-08 CN CNB200410001681XA patent/CN100356060C/en not_active Expired - Fee Related
- 2004-01-08 CN CNB2007101860467A patent/CN100570154C/en not_active Expired - Fee Related
- 2004-01-08 CN CN2007101264647A patent/CN101100988B/en not_active Expired - Fee Related
- 2004-11-22 US US10/995,715 patent/US7220109B2/en not_active Expired - Fee Related
- 2004-11-22 US US10/995,726 patent/US20050069431A1/en not_active Abandoned
- 2004-11-22 US US10/995,725 patent/US7037090B2/en not_active Expired - Lifetime
- 2004-12-08 US US11/007,111 patent/US20050100458A1/en not_active Abandoned
- 2004-12-08 US US11/007,125 patent/US20050098222A1/en not_active Abandoned
-
2005
- 2005-01-04 HK HK05100019A patent/HK1067685A1/en not_active IP Right Cessation
-
2008
- 2008-01-04 JP JP2008000012A patent/JP4729050B2/en not_active Expired - Fee Related
- 2008-01-04 JP JP2008000013A patent/JP4861344B2/en not_active Expired - Fee Related
- 2008-07-02 HK HK08107283A patent/HK1116851A1/en not_active IP Right Cessation
- 2008-09-25 HK HK08110685A patent/HK1119219A1/en not_active IP Right Cessation
Patent Citations (45)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1669889A (en) * | 1922-04-17 | 1928-05-15 | Couzens Ice Machine Company | Compressor valve |
US1629445A (en) * | 1925-07-07 | 1927-05-17 | Cornelius W Van Ranst | Method of balancing pistons |
US1634949A (en) * | 1925-07-23 | 1927-07-05 | Ingersoll Rand Co | Air-compressor valve |
US1795445A (en) * | 1927-11-21 | 1931-03-10 | Walter G E Rolaff | Reciprocating compressor |
US1821862A (en) * | 1929-06-24 | 1931-09-01 | Wylie G Wilson | Sealing ring for joints |
US2170443A (en) * | 1936-09-09 | 1939-08-22 | Barbarou Marius Jean-Baptiste | Mounting of cylinders in motors |
US2323068A (en) * | 1941-03-29 | 1943-06-29 | Maniscalco Pictro | Compressor |
US2302447A (en) * | 1941-08-30 | 1942-11-17 | Gen Electric | Compressor valve |
US2609660A (en) * | 1946-02-25 | 1952-09-09 | Tenney | Resonating pulse jet engine |
US2725183A (en) * | 1951-01-10 | 1955-11-29 | Carrier Corp | Valves for reciprocating compressors |
US2856249A (en) * | 1955-01-11 | 1958-10-14 | Maquinaria Petrolifera S A | High-pressure pump liner and packing |
US3606361A (en) * | 1968-03-15 | 1971-09-20 | Ulrich Pohl | Flat gasket for the cylinder head of combustion engines and process for making same |
US3744261A (en) * | 1972-03-16 | 1973-07-10 | Hughes Aircraft Co | Cryogenic refrigerator |
US3839946A (en) * | 1972-05-24 | 1974-10-08 | Hardie Tynes Mfg Co | Nonlubricated compressor |
US3998571A (en) * | 1975-04-14 | 1976-12-21 | Sundstrand Corporation | Valve retainer |
US4190402A (en) * | 1975-05-06 | 1980-02-26 | International Telephone And Telegraph Corporation | Integrated high capacity compressor |
US4073221A (en) * | 1976-06-21 | 1978-02-14 | Caterpillar Tractor Co. | Light-weight piston assemblies |
US4246123A (en) * | 1979-04-20 | 1981-01-20 | Sherwood Medical Industries Inc. | Fluid collection device with phase partitioning means |
US4319498A (en) * | 1979-06-11 | 1982-03-16 | Mcwhorter Edward M | Reciprocating engine |
US4529365A (en) * | 1980-08-29 | 1985-07-16 | Durr-Dental Gmbh & Co., Kg | Compressor with longitudinally extending cooling fins |
US4479419A (en) * | 1982-11-02 | 1984-10-30 | Westinghouse Electric Corp. | Dual capacity reciprocating compressor |
US4507059A (en) * | 1983-02-01 | 1985-03-26 | Kabushiki Kaisha Toyoda Jidoshokki Seisa-Kusho | Variable delivery compressor |
US4550571A (en) * | 1983-12-28 | 1985-11-05 | Helix Technology Corporation | Balanced integral Stirling cryogenic refrigerator |
US4929157A (en) * | 1987-11-23 | 1990-05-29 | Ford Motor Company | Pulsation damper for air conditioning compressor |
US4817967A (en) * | 1987-12-11 | 1989-04-04 | Dana Corporation | Angled junction sealing structure for gaskets |
US5035050A (en) * | 1989-02-15 | 1991-07-30 | Tecumseh Products Company | Method of installing a valve assembly in a compressor |
US5110272A (en) * | 1989-06-07 | 1992-05-05 | Aspera S.R.L. | Valve unit for a reciprocating compressor for refrigerators and the like |
US5213125A (en) * | 1992-05-28 | 1993-05-25 | Thomas Industries Inc. | Valve plate with a recessed valve assembly |
US5327932A (en) * | 1993-04-19 | 1994-07-12 | Thomas Industries Inc. | Valve restraint enhancement |
US5515769A (en) * | 1994-06-28 | 1996-05-14 | Carrier Corporation | Air compressor |
US5620166A (en) * | 1994-08-02 | 1997-04-15 | Lord; Bruce A. | Stem and nut with bearing for use in a motor operated valve |
US5456287A (en) * | 1994-10-03 | 1995-10-10 | Thomas Industries Inc. | Compressor/vacuum pump reed valve |
US5879145A (en) * | 1995-01-17 | 1999-03-09 | Knorr-Bremse Systems Fur Nutzfahrzeuge Gmbh | Integrated cylinder liner and valve plate for a compressor |
US5961127A (en) * | 1996-01-12 | 1999-10-05 | Honda Giken Kogyo Kabushiki Kaisha | Sealing structure for cylinder and cylinder head in reciprocating type internal combustion engine and assembling method thereof |
US5934305A (en) * | 1996-09-12 | 1999-08-10 | Samsung Electronics Co., Ltd. | Method of manufacturing a reciprocating compressor |
US6036194A (en) * | 1996-09-16 | 2000-03-14 | Cummins Engine Company, Inc. | Combustion gas seal for an internal combustion engine |
US6314990B1 (en) * | 1997-12-17 | 2001-11-13 | Verdichter Oe. Ges. M.B.H. | Pressure valve for a compressor |
US6148716A (en) * | 1998-12-16 | 2000-11-21 | Impact Mst Incorporated | Low noise high efficiency positive displacement pump |
US6513544B1 (en) * | 1999-08-13 | 2003-02-04 | Orbital Engine Company (Australia) Pty Limited | Compressor valve arrangement |
US6431840B1 (en) * | 1999-09-09 | 2002-08-13 | Sanyo Electric Co., Ltd. | Multistage high pressure compressor |
US6485266B2 (en) * | 2000-03-10 | 2002-11-26 | Thomas Industries, Inc. | Compressor assembly with deflector |
US6595525B2 (en) * | 2001-01-25 | 2003-07-22 | Glen D. Schmidt | Attachable sealant bead and strip for use with a vehicle part |
US6679688B2 (en) * | 2001-02-14 | 2004-01-20 | Sanyo Electric Co., Ltd. | Reed valve restriction plate with anti-sticking means |
US6843643B2 (en) * | 2001-11-06 | 2005-01-18 | Oken Seiko Co., Ltd. | Valve mounting arrangement in a diaphragm pump |
US6832900B2 (en) * | 2003-01-08 | 2004-12-21 | Thomas Industries Inc. | Piston mounting and balancing system |
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