CA1179575A - Valve assembly - Google Patents
Valve assemblyInfo
- Publication number
- CA1179575A CA1179575A CA000341333A CA341333A CA1179575A CA 1179575 A CA1179575 A CA 1179575A CA 000341333 A CA000341333 A CA 000341333A CA 341333 A CA341333 A CA 341333A CA 1179575 A CA1179575 A CA 1179575A
- Authority
- CA
- Canada
- Prior art keywords
- valve
- combination
- valve member
- opening
- valve seat
- 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.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/102—Adaptations or arrangements of distribution members the members being disc valves
Abstract
VALVE ASSEMBLY
ABSTRACT OF THE DISCLOSURE
There are disclosed herein several embodiments of a pressure responsive discharge valve assembly particularly adapted for use in reciprocating type gas compressors. The valve assembly includes a discharge passage valve seat of frusto conical shape in which a gen-erally complementary shaped light-weight valve member is disposed.
The valve member is preferably formed from a polymeric material, but may also be formed of metal. The materials used and the relative geo-metry of the valve seat and member are such as to reduce clearance or reexpansion volume, provide quiet closure with good sealing, long life and high speed operation, and still have the required flow areas at low valve lifts, thereby providing improved n ow characteristics and efficiency. The included angles of the valve and seat are slightly different to provide progressive closing and sealing without permanent deformation. The valve concepts are also disclosed embodied in two other known types of valves in which the valve element is provided with a central opening and associated closure means to provide additional discharge flow area. The closure means in one embodiment is in the form of a fixed member and in another embodiment is in the form of a second separately biased movable valve disc member. The discharge valve of the present invention is also shown in combination with several different types of known suction valves.
ABSTRACT OF THE DISCLOSURE
There are disclosed herein several embodiments of a pressure responsive discharge valve assembly particularly adapted for use in reciprocating type gas compressors. The valve assembly includes a discharge passage valve seat of frusto conical shape in which a gen-erally complementary shaped light-weight valve member is disposed.
The valve member is preferably formed from a polymeric material, but may also be formed of metal. The materials used and the relative geo-metry of the valve seat and member are such as to reduce clearance or reexpansion volume, provide quiet closure with good sealing, long life and high speed operation, and still have the required flow areas at low valve lifts, thereby providing improved n ow characteristics and efficiency. The included angles of the valve and seat are slightly different to provide progressive closing and sealing without permanent deformation. The valve concepts are also disclosed embodied in two other known types of valves in which the valve element is provided with a central opening and associated closure means to provide additional discharge flow area. The closure means in one embodiment is in the form of a fixed member and in another embodiment is in the form of a second separately biased movable valve disc member. The discharge valve of the present invention is also shown in combination with several different types of known suction valves.
Description
11 79575 , BAcKGRoln~D AND SN~WRY o~ ~ E INVrNnloN
The prcscnt invcntion relatcs ger.er~lly to pressurc rcsponsive ~alve asscmblies and more p~rticularly to such valvc asscmblies adaptcd for use in reciprocatin~ piston type compressors, such as refrigeration S oompressors.
Reciprocating piston type compressors typically employ suction and dischar~e pressurc actuated valving mounted Dt thc end of the cylinder between the hcad and cylindcr housin~. In desi~ning these valve assemblies it is of critical importance to overall system aperation to provide a sufficiently large port area to permit the flow of a m~ximum ~olume of fluid within a given time period and at an acceptably small pressure drop. This is particularly true for refrigeration compressors employed in air conditioning systems because of the relatively high mass flow ~ rates generally required in such systems, Associated and conflicting with the desirability to maximize port area for a given size cylinder is the need to reduce the weight of the moving valve member so as to limit the inertia effect thereof.
Noise of aperation should also be minimized. These aspects take on increasing importance with high speed compressors.
Another impartant design objective is to minimize the reexpan-sion or clearance volume of the cylinder. The valving and cylinder top end wall should have a shape complementary with that of the top of the piston and as flat as possible to enable the piston to reduce the volume of the compression -~hamber to an absolute minimum during 25 ~ the compression strokc without restricting gas n ow. While it may be possible to ~ccomplish this objectivè by design o complex piston head sh~pcs, manufacturin~ thcrcof bccomcs cxpcnsive, asscmbly morc difficult, and throttling losscs gcncrally occur ~s thc piston approachcs ",,._...................................... .
11'~9575 top dead center. Reduction oE reexparlsion volume is of great importance in refrigeration compressors having relatively low mass flow rates, such as those units employed in very low temperature refrigeration systems, as well as in units for heat pump applications.
It is therefore the primary object of this invention to provide an improved valve and an improved valve and seat combination for use as a discharge valve in a reciprocating gas compressor, such as, for example, the compressors used in refrigeration equipment, which valve and valve-seat combination improves the efficiency of the compressor and is characterized by its improved flow characteristics at all valve lifts, good sealing without permanent deformation of the valve, long life, quietness in operation and its ability to operate in high speed compressors.
Broadly speaking the present invention provides in combination with a gas compressor an improved pressure responsive valve assembly comprising: a valve plate having an inner surface in part defining a com-pression chamber of the compressor; a discharge port extending through the valve plate; means defining a valve seat of circular cross-section in the port, the valve seat being of increasing diameter in a direction away from the compression chamber; and a discharge valve member formed of a ~0 relatively compliant polymeric composition disposed within the port such that the inner surface of the discharge valve member lies substantially in the plane of the inner surface of the valve plate when the discharge port is closed, the discharge valve member having a peripheral edge surface adapted to sealingly engage the valve seat, the peripheral edge surface of the discharge valve member and the sidewall of sd/ c -3-the valve seat being configured so that a larger diameter poxtion of the edge surface engages the valve seat first during closure/ whereb~ complete seating occurs incident to distortion of the discharge valve member, the distortion resulting in a reactive force tending to unseat the discharge valve member.
The present invention provides an improved valve assembly utilizing a valve member the entire area of which is subjected to valve actuating pressure differentials and which is fabricated in a light-weight manner so that high force to weight ratios are obtained for a given port size. This maximizes acceleration and hence efficiency, especially at high speeds.
Further, the design of the valve member and associated valve plate is such as to present a substantially flat, flush end wal~
for the compression chamber. Thus, the reexpansion volume for the compression chamber is substantially reduced over conventional valving arrangements and simple flat topped pistons (or pistons with a minumum of top surfaces contour) can be used. Also, because of the lightweight characteristics of the valve member, valving action is faster and port size may be increased without detrimental inertial effects. The use of a polymeric material for the valve member in one embodiment and the relative geometries of the valve member and valve seat also reduce valve noise generated by the recurring impact sd/~ 3a---" ^ 11795~S
of the valvc mcmbcr and valve scat. With thc prcscnt invcntion valvc port arca is not a function of rcexp~nsion volumc; each cnn be opti-mized indcpcndcntly. Thcrefore, thc valve assembly of tl-c prcsent invcntion is idcally suitcd for use both in air conditioning applica-tions as well as heat pumps and low temperature ~nits. Further, ~hc present arrangement can be used to maximize the use of the cylinder head area for valving.
Additional advantages and features of the prescnt invcntion will become apparent from the subsequent description and the appended claims taken in conjunction with the accompanying drawings.
BRIEF DESCRIPTION OF THE DR~~ NGS
Figure 1 is a bottcm plan view (from inside the cylinder chamber) of a pressure responsive discharge valve assembly utilizing a polymeric valve member in accordance with the present invention, shown in combination with a reed type suction valve;
Figure 2 is an inverted sectional view of the valve assembly of Figure 1, the section being taken along line 2-2 thereof;
Figure 3 is an in~erted sectional view of the valve assembly of Figure 1, the section being taken along line 3-3 thereof;
Figure 4 is an enlarged fragmentary view of a portion of a valve seat and associated valve mcmber in accordance with the present invention illustrating in an exaggerated manner the relative angles of inclination of the mating sl~rfaces thereof, thc val~e membcr being shown in a position in which it is just bcginning to scat;
Pigure S is a scctional vicw similar to and showing the val w assem~ly of Fi~ure 2 but illustrating it in combination with a ring -- 1179~5 type suction valve;
Figure 6 is a bottom plan view (from insicle the cylinder chamber~ of another embodiment of the discharge valve assembly of the present invention, utilizing a polymeric valve member;
Figure 7 is an inverted sectional view of the embodiment of Figure 6, the section being taken along line 7-7 thereof;
Figure 8 is a sectional view similar to, and showing the valve assembly of, Figure 7, but illustrating it in combina-tion with the reed type suction valve shown in Figures 1 through 4.
Figure 9 is a fragmentary sectional view similar to that of Figure 7 but illustrating yet another emhodiment of the dis-charge valve assembly of the present invention utilizing a poly~
meric valve member; and Figures 10 through 15 are fragmentary sectional views similar to Figure 4, but illustrating several embodiments of the valve member of the present invention formed out of metal.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings and in particular to Figures 1 through 3, there is illustra-ted a valve assembly in accordance with the present invention indicated generally at 10.
Valve assembly 10 comprises a conventional. valve plate 12 having a pair of spaced suction passages 14 and 16 extending there-through and a combined discharge passage and valve seat 18. A
conventional reed type suction valve member 20 i5 also provided having an end portion 22 disposed in overly.i.ng valvincJ relation-ship to sucti~n passages 14 and 16, an opposite end portion 24 secured to valve plate 12 and an elongated centrally sd/(`~ 5-~-"` 1179S'75 disposed opening 26 werlying disc!~arge passage 18. Recessos=~qLe__ provided in the cylinder bore to provide elearanee h r the tip$ of tho suetion v~lve when it opens. T~e valve plate is moun~ed in the usu~l manner over a compressor cylinder defined by cylinder block 27 (in S Figure 1 the position of the cylinder bore is sh~wn in phantom)~
~s best seen with reference to Figures 2 and 3, discharge passage 18 is of a frusto conical shape being defined by outwardly diverging sidewalls 28. A discharge valve member 30 in the form of a frusto conically shaped disc is disposed within discharge passage 18 with sidewalls 32 sealingly engaging sidewalls 28. As shown, dis-charge Yalve member 30 is of a size and shape relative to discharge passage 18 so as to place lower surface 34 thereof in substantially eo-planar relationship to lower surface 36 of valve plate 12. Discharge valve member 30 is also providet with a recess 38 in upper surface 40 thereof which receives an end portion 42 of a biasing means in the form of a helieal compression spring 44, the opposite end 46 of which extends ; upwardly into engagement with a recess 48 provided in a bridge-like re-tainer member 50. The valve is essentially pressure actuated, and spring 44 is ehosen primarily to provide stability and also an initial elosing bias and a preload to establish an initial seal. Other types of springs than eoil springs may of course be used for this purpose.
Retainer member 50, which also serves as a stop to limit opening movement of the valve element, is secured to valve plate 12 by suitable fasteners 52 and 54.
Generally speaking, discharge valve member 30 is preferably formed from a high performanee polymerie material, and preferably a .
molding resin, sueh as polyimide, aramid, polyester, polyphenylene suifide, and poly (2mide-imide) resins. These muterials hav¢ high strength, high temperature resistanee, are relatively li~htweight, are unreaetive, and are rolatiYely eor~ nt. Although it is difficult . ~ 6 -- 117gS7~
to numerically define all of the desirable par~meters for this material, it is thought that best results will be obtained using materials having a tensile strength to weight ratio greater than approximately 3.25 x 105 psi/lbm and a n exural strength to n exurnl mDdulus ratio less than approximately 0.04. In addition, the material should have a heat distortion temperature gTeater than 450~F.9 high wear resistanee, high inteTnal dampening characteristics (for noise attenuation and sealing), compatibl~it~ ~ith the envirormlent, ease of manlfacture ~e.g., by com-pression or injection molding), low creep rate, and a higll impact strength (preferably having a notched I70d impact strength gTeater than approxi-mately 0.8).
At the pTesent time the preferTed material for the valve member ijs '~espel",~a polyimide resin available from duPont Company, Wilmington, Dela~are. The cc~Dositior,s identified as "SP-l" and "SP-21"
have been found to give excellent results. The use of such a polymeric eomposition for discharge valve member 30 facilitates easy fabrication, sueh as by molding, and the relative light weight of the valve member faeilitates high speed operation due to the redueed inertia of the valve and the ability to use lighter springs, as well as reducing noise generated by eontaet of the valve and valve seat. ~e 'nVespel" msterial is ideally suited for such application a~s it is able to resist degrada-tion from relatively high temperatures and is unaffected by either ref~igerant gas or lubricant. It has been found that the maximum operating t~nperature to which the refrigerant and lubricating oil can be subjected without damage is less than that for '~espel". 'nVespel" is also compli-ant en w ~h to seal without permanent deformation.
Other suitable polymerie m3t~rials havin~ the noted eharae-teristics whieh it is believed m~y also be used, include those eommer-, eially available wlder the trademarXs '~espel" ~S (an aramid resin ~a~ - ~a~Y~
, _, . _,_, .. . .. .
. 11795~S
availablc from the duront Company), "Sparmonl' (a polyimidc rcsin available from Sparta Mfg. Co., Dovcr, Ohio), '~alox" 420 or 420-SEO (a glass rein-forced, thcrmoplastic polyesterlavailable from the Gencral Electric Co., Pittsfield, Mass.), "hyton" (a polyphenylene sulfide available from Phillips Petroleum Co., Bartlesville, Okla.), and '~orlon" (a poly (amide-imide) ~esin available from Amoco Chemicals Corp., Chicago, Ill.).
As shown in Figure 4, sidewalls 32 of valve member 30 are inclined Telative to the ccnter axis of discharge passageway 18 indicated at 55, at an angle 56 slightly grcater (when unstressed) than the angle 58 of inclination of sidewalls 28 of the valve seat or discharge passage 18.
initial seal is achieved when the valve member closes to the position sh~wn in Figure 4, i.e., when the thin outer sealing periphery 60 of sidewall 32 first engages sidewall 28. Because the pressure differentials across the valve element are relatively small during most of the closure cycle, the primaIy closing force is that exerted by spring 44. Gnce an ~nitial seal is achieved, however, a substantial pressure differential is created across the valve member as the compressor piston starts down from top dead center. This creates a substantial closing force which moves the ~alve member from the initial seal position of Figure 4 to the fully seated position of Figures 2, 3 and S. Edge portion 60 deforms and becomes stressed as this seating takes place. The stress in edge portion 60 improves the de~ree of sealing and facilitates opening, but should not be so ~uch as to cause permanent deformation of the valve member.
~ e valve member and spring are preferably dcsigned so that the
The prcscnt invcntion relatcs ger.er~lly to pressurc rcsponsive ~alve asscmblies and more p~rticularly to such valvc asscmblies adaptcd for use in reciprocatin~ piston type compressors, such as refrigeration S oompressors.
Reciprocating piston type compressors typically employ suction and dischar~e pressurc actuated valving mounted Dt thc end of the cylinder between the hcad and cylindcr housin~. In desi~ning these valve assemblies it is of critical importance to overall system aperation to provide a sufficiently large port area to permit the flow of a m~ximum ~olume of fluid within a given time period and at an acceptably small pressure drop. This is particularly true for refrigeration compressors employed in air conditioning systems because of the relatively high mass flow ~ rates generally required in such systems, Associated and conflicting with the desirability to maximize port area for a given size cylinder is the need to reduce the weight of the moving valve member so as to limit the inertia effect thereof.
Noise of aperation should also be minimized. These aspects take on increasing importance with high speed compressors.
Another impartant design objective is to minimize the reexpan-sion or clearance volume of the cylinder. The valving and cylinder top end wall should have a shape complementary with that of the top of the piston and as flat as possible to enable the piston to reduce the volume of the compression -~hamber to an absolute minimum during 25 ~ the compression strokc without restricting gas n ow. While it may be possible to ~ccomplish this objectivè by design o complex piston head sh~pcs, manufacturin~ thcrcof bccomcs cxpcnsive, asscmbly morc difficult, and throttling losscs gcncrally occur ~s thc piston approachcs ",,._...................................... .
11'~9575 top dead center. Reduction oE reexparlsion volume is of great importance in refrigeration compressors having relatively low mass flow rates, such as those units employed in very low temperature refrigeration systems, as well as in units for heat pump applications.
It is therefore the primary object of this invention to provide an improved valve and an improved valve and seat combination for use as a discharge valve in a reciprocating gas compressor, such as, for example, the compressors used in refrigeration equipment, which valve and valve-seat combination improves the efficiency of the compressor and is characterized by its improved flow characteristics at all valve lifts, good sealing without permanent deformation of the valve, long life, quietness in operation and its ability to operate in high speed compressors.
Broadly speaking the present invention provides in combination with a gas compressor an improved pressure responsive valve assembly comprising: a valve plate having an inner surface in part defining a com-pression chamber of the compressor; a discharge port extending through the valve plate; means defining a valve seat of circular cross-section in the port, the valve seat being of increasing diameter in a direction away from the compression chamber; and a discharge valve member formed of a ~0 relatively compliant polymeric composition disposed within the port such that the inner surface of the discharge valve member lies substantially in the plane of the inner surface of the valve plate when the discharge port is closed, the discharge valve member having a peripheral edge surface adapted to sealingly engage the valve seat, the peripheral edge surface of the discharge valve member and the sidewall of sd/ c -3-the valve seat being configured so that a larger diameter poxtion of the edge surface engages the valve seat first during closure/ whereb~ complete seating occurs incident to distortion of the discharge valve member, the distortion resulting in a reactive force tending to unseat the discharge valve member.
The present invention provides an improved valve assembly utilizing a valve member the entire area of which is subjected to valve actuating pressure differentials and which is fabricated in a light-weight manner so that high force to weight ratios are obtained for a given port size. This maximizes acceleration and hence efficiency, especially at high speeds.
Further, the design of the valve member and associated valve plate is such as to present a substantially flat, flush end wal~
for the compression chamber. Thus, the reexpansion volume for the compression chamber is substantially reduced over conventional valving arrangements and simple flat topped pistons (or pistons with a minumum of top surfaces contour) can be used. Also, because of the lightweight characteristics of the valve member, valving action is faster and port size may be increased without detrimental inertial effects. The use of a polymeric material for the valve member in one embodiment and the relative geometries of the valve member and valve seat also reduce valve noise generated by the recurring impact sd/~ 3a---" ^ 11795~S
of the valvc mcmbcr and valve scat. With thc prcscnt invcntion valvc port arca is not a function of rcexp~nsion volumc; each cnn be opti-mized indcpcndcntly. Thcrefore, thc valve assembly of tl-c prcsent invcntion is idcally suitcd for use both in air conditioning applica-tions as well as heat pumps and low temperature ~nits. Further, ~hc present arrangement can be used to maximize the use of the cylinder head area for valving.
Additional advantages and features of the prescnt invcntion will become apparent from the subsequent description and the appended claims taken in conjunction with the accompanying drawings.
BRIEF DESCRIPTION OF THE DR~~ NGS
Figure 1 is a bottcm plan view (from inside the cylinder chamber) of a pressure responsive discharge valve assembly utilizing a polymeric valve member in accordance with the present invention, shown in combination with a reed type suction valve;
Figure 2 is an inverted sectional view of the valve assembly of Figure 1, the section being taken along line 2-2 thereof;
Figure 3 is an in~erted sectional view of the valve assembly of Figure 1, the section being taken along line 3-3 thereof;
Figure 4 is an enlarged fragmentary view of a portion of a valve seat and associated valve mcmber in accordance with the present invention illustrating in an exaggerated manner the relative angles of inclination of the mating sl~rfaces thereof, thc val~e membcr being shown in a position in which it is just bcginning to scat;
Pigure S is a scctional vicw similar to and showing the val w assem~ly of Fi~ure 2 but illustrating it in combination with a ring -- 1179~5 type suction valve;
Figure 6 is a bottom plan view (from insicle the cylinder chamber~ of another embodiment of the discharge valve assembly of the present invention, utilizing a polymeric valve member;
Figure 7 is an inverted sectional view of the embodiment of Figure 6, the section being taken along line 7-7 thereof;
Figure 8 is a sectional view similar to, and showing the valve assembly of, Figure 7, but illustrating it in combina-tion with the reed type suction valve shown in Figures 1 through 4.
Figure 9 is a fragmentary sectional view similar to that of Figure 7 but illustrating yet another emhodiment of the dis-charge valve assembly of the present invention utilizing a poly~
meric valve member; and Figures 10 through 15 are fragmentary sectional views similar to Figure 4, but illustrating several embodiments of the valve member of the present invention formed out of metal.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings and in particular to Figures 1 through 3, there is illustra-ted a valve assembly in accordance with the present invention indicated generally at 10.
Valve assembly 10 comprises a conventional. valve plate 12 having a pair of spaced suction passages 14 and 16 extending there-through and a combined discharge passage and valve seat 18. A
conventional reed type suction valve member 20 i5 also provided having an end portion 22 disposed in overly.i.ng valvincJ relation-ship to sucti~n passages 14 and 16, an opposite end portion 24 secured to valve plate 12 and an elongated centrally sd/(`~ 5-~-"` 1179S'75 disposed opening 26 werlying disc!~arge passage 18. Recessos=~qLe__ provided in the cylinder bore to provide elearanee h r the tip$ of tho suetion v~lve when it opens. T~e valve plate is moun~ed in the usu~l manner over a compressor cylinder defined by cylinder block 27 (in S Figure 1 the position of the cylinder bore is sh~wn in phantom)~
~s best seen with reference to Figures 2 and 3, discharge passage 18 is of a frusto conical shape being defined by outwardly diverging sidewalls 28. A discharge valve member 30 in the form of a frusto conically shaped disc is disposed within discharge passage 18 with sidewalls 32 sealingly engaging sidewalls 28. As shown, dis-charge Yalve member 30 is of a size and shape relative to discharge passage 18 so as to place lower surface 34 thereof in substantially eo-planar relationship to lower surface 36 of valve plate 12. Discharge valve member 30 is also providet with a recess 38 in upper surface 40 thereof which receives an end portion 42 of a biasing means in the form of a helieal compression spring 44, the opposite end 46 of which extends ; upwardly into engagement with a recess 48 provided in a bridge-like re-tainer member 50. The valve is essentially pressure actuated, and spring 44 is ehosen primarily to provide stability and also an initial elosing bias and a preload to establish an initial seal. Other types of springs than eoil springs may of course be used for this purpose.
Retainer member 50, which also serves as a stop to limit opening movement of the valve element, is secured to valve plate 12 by suitable fasteners 52 and 54.
Generally speaking, discharge valve member 30 is preferably formed from a high performanee polymerie material, and preferably a .
molding resin, sueh as polyimide, aramid, polyester, polyphenylene suifide, and poly (2mide-imide) resins. These muterials hav¢ high strength, high temperature resistanee, are relatively li~htweight, are unreaetive, and are rolatiYely eor~ nt. Although it is difficult . ~ 6 -- 117gS7~
to numerically define all of the desirable par~meters for this material, it is thought that best results will be obtained using materials having a tensile strength to weight ratio greater than approximately 3.25 x 105 psi/lbm and a n exural strength to n exurnl mDdulus ratio less than approximately 0.04. In addition, the material should have a heat distortion temperature gTeater than 450~F.9 high wear resistanee, high inteTnal dampening characteristics (for noise attenuation and sealing), compatibl~it~ ~ith the envirormlent, ease of manlfacture ~e.g., by com-pression or injection molding), low creep rate, and a higll impact strength (preferably having a notched I70d impact strength gTeater than approxi-mately 0.8).
At the pTesent time the preferTed material for the valve member ijs '~espel",~a polyimide resin available from duPont Company, Wilmington, Dela~are. The cc~Dositior,s identified as "SP-l" and "SP-21"
have been found to give excellent results. The use of such a polymeric eomposition for discharge valve member 30 facilitates easy fabrication, sueh as by molding, and the relative light weight of the valve member faeilitates high speed operation due to the redueed inertia of the valve and the ability to use lighter springs, as well as reducing noise generated by eontaet of the valve and valve seat. ~e 'nVespel" msterial is ideally suited for such application a~s it is able to resist degrada-tion from relatively high temperatures and is unaffected by either ref~igerant gas or lubricant. It has been found that the maximum operating t~nperature to which the refrigerant and lubricating oil can be subjected without damage is less than that for '~espel". 'nVespel" is also compli-ant en w ~h to seal without permanent deformation.
Other suitable polymerie m3t~rials havin~ the noted eharae-teristics whieh it is believed m~y also be used, include those eommer-, eially available wlder the trademarXs '~espel" ~S (an aramid resin ~a~ - ~a~Y~
, _, . _,_, .. . .. .
. 11795~S
availablc from the duront Company), "Sparmonl' (a polyimidc rcsin available from Sparta Mfg. Co., Dovcr, Ohio), '~alox" 420 or 420-SEO (a glass rein-forced, thcrmoplastic polyesterlavailable from the Gencral Electric Co., Pittsfield, Mass.), "hyton" (a polyphenylene sulfide available from Phillips Petroleum Co., Bartlesville, Okla.), and '~orlon" (a poly (amide-imide) ~esin available from Amoco Chemicals Corp., Chicago, Ill.).
As shown in Figure 4, sidewalls 32 of valve member 30 are inclined Telative to the ccnter axis of discharge passageway 18 indicated at 55, at an angle 56 slightly grcater (when unstressed) than the angle 58 of inclination of sidewalls 28 of the valve seat or discharge passage 18.
initial seal is achieved when the valve member closes to the position sh~wn in Figure 4, i.e., when the thin outer sealing periphery 60 of sidewall 32 first engages sidewall 28. Because the pressure differentials across the valve element are relatively small during most of the closure cycle, the primaIy closing force is that exerted by spring 44. Gnce an ~nitial seal is achieved, however, a substantial pressure differential is created across the valve member as the compressor piston starts down from top dead center. This creates a substantial closing force which moves the ~alve member from the initial seal position of Figure 4 to the fully seated position of Figures 2, 3 and S. Edge portion 60 deforms and becomes stressed as this seating takes place. The stress in edge portion 60 improves the de~ree of sealing and facilitates opening, but should not be so ~uch as to cause permanent deformation of the valve member.
~ e valve member and spring are preferably dcsigned so that the
2~ upward force exerted by the valve member as it unstresses and moves from its fu~ly seated position to that sh~wn in Figure 4 is significantly greater than the downward force exerted on the~valve mcmber by sprin~ 44 during this initiDl opening movemcnt. This significantly assists opening of the valve bcc~use as soon as the prcssure diffcrcntial across the valve mcmber starts to rcvcrse ti.e., after completion of the suction cycle and early . ~ 8 -. .
.
--" 11795 ~S
in the discharge cycle) the residual stress ~n the valve member causes it to immediately spring off the valve seat (overcoming the force of sprin~ 44) tow~rds its Fi~ure 4 position. m is in turn immediately cxposes the full area of the valve member to opening pressure generated within the compression chamber. This exposure of a maximum effective area to opening or lifting pressure accelerates valve opening and permits bigher speed operation. It should also be noted that the passage area between opposed sidewalls 28 and ;2 will continue to increase as valve r~mber 30 is moved upwardly, thereby providing an extremely large area for fluid discharge with a given size port area. This provides worthwhile ibncreases in ~ass n ow rate for a given compressor speed.
It should be noted that when the valve member is fully seated (as in Figurés 2, 3 and 5) the effective area thereof exposed to the pres-~sure di fferential is that defined by discharge passage 18, i.e., a con-1~ siderably smaller area than that defined by the outer periphery of themilve. Because it is desirable to use as light a weight construction as possible to maximize valve acceleration, it is thereby possible to const~uct the ~alve sufficiently light tconsidering material strengths ~nd structu~al design) that it need not be able to accommodate twithout excessive cr peTmanènt de h rmation) the stresses which would result if the DEuo~num pressure differential across the valve member was applied to ~be arez thereof when seated, so long as the valve member accom-no3ates the maximum pressure differential acting across the smaller dEfective area thereof defined by the inner periphery of the discharge _~port. Stated conversely, the valve would have to be of much sturdier ~and hence heavier) construction if, when seated, the entire cross-sectional rea theTeof was subjected to the pressure dif* rentials thereacross. The Te]ative an~les ~f the valve member and seat also serve to cushion the imp~ct of the parts on closing, thereby contributin~ talon~ with light wci~ht) to thc reduction of noise and wear, .. . ....
.
--" 11795 ~S
in the discharge cycle) the residual stress ~n the valve member causes it to immediately spring off the valve seat (overcoming the force of sprin~ 44) tow~rds its Fi~ure 4 position. m is in turn immediately cxposes the full area of the valve member to opening pressure generated within the compression chamber. This exposure of a maximum effective area to opening or lifting pressure accelerates valve opening and permits bigher speed operation. It should also be noted that the passage area between opposed sidewalls 28 and ;2 will continue to increase as valve r~mber 30 is moved upwardly, thereby providing an extremely large area for fluid discharge with a given size port area. This provides worthwhile ibncreases in ~ass n ow rate for a given compressor speed.
It should be noted that when the valve member is fully seated (as in Figurés 2, 3 and 5) the effective area thereof exposed to the pres-~sure di fferential is that defined by discharge passage 18, i.e., a con-1~ siderably smaller area than that defined by the outer periphery of themilve. Because it is desirable to use as light a weight construction as possible to maximize valve acceleration, it is thereby possible to const~uct the ~alve sufficiently light tconsidering material strengths ~nd structu~al design) that it need not be able to accommodate twithout excessive cr peTmanènt de h rmation) the stresses which would result if the DEuo~num pressure differential across the valve member was applied to ~be arez thereof when seated, so long as the valve member accom-no3ates the maximum pressure differential acting across the smaller dEfective area thereof defined by the inner periphery of the discharge _~port. Stated conversely, the valve would have to be of much sturdier ~and hence heavier) construction if, when seated, the entire cross-sectional rea theTeof was subjected to the pressure dif* rentials thereacross. The Te]ative an~les ~f the valve member and seat also serve to cushion the imp~ct of the parts on closing, thereby contributin~ talon~ with light wci~ht) to thc reduction of noise and wear, .. . ....
3 5. ~ ~;
It should be notcd that valvc mcmbcr 30 will prcfcrably h~vc a thickness less than that of valvc platc 12 in ordcr to insurc adoquate sealing of sidewalls 32 with sid'cwalls 28 and to avoid a partial or complcte annular groove being worn in sidcwalls 32, which groove could possibly interfere with proper seating and/or sealing of valve member 30. Also, edge portion 60 will preferably be provided with a small radius or chamfer which operates to insure proper sealing even should valve mcmbcr bc shiftcd or cocked sliglltly during closing thereof.
Additionally, spring 4Z preferably has its ends squared snd ground and is of as large a di~meter as possible relative to the diameter of valve member 30 so as to place the biasing h rce exerted thereby closely adjacent the sealing sidewalls 3Z and to aid in preventing 8 shifting, tilting or other tislocation of valve member 30 during operation thereof.
While the present invention has been described with reference to Figures 1 through 4 utilizing a reed-type suction valve, it is also well suited for use with a conventional ring-type suction valve such as is shown in the embodiment indicated generally at 64 in Figure 5.
~alve assembly 64 includes a valve plate 66 having a relatively large irregularly shaped generally annular recessed portion 68 defining a suction plenum in the lower surface 70 thereof. A discharge opening 72 of frusto conical shape is also provided, bcing defined by a radially inwardly inclined or beveled sidewall 74 extending between upper surface 76 and lower surface 70 of valve plate 66. Surface 78 of sidewall 74 provides a valve seat for a discharge valve mcmber 30~ which is ur~ed into s¢aling en~agcment thcrcwith by gas pressure and a spring 44' cxtcnd;ng bctween valvc mcmbcr 30' and a spring retainer 50' all of which arc substantiolly identical to corrcsponding portions describcd abovc with rcfercnce to Figurcs 1 through 4 ~ 10 , , , , - 1179S7~;
; A generally annul3r valve plate insert 80 is disposed within recess 68 throu~h which fasteners B2 extend so as to seeure valve as-sembly 64 to a cylinder housingl84~ A plurality of spaced cutout areas or radially extendin~ slots (not shown) are provided throu~h valve S plate insert 80 so as to allow suction fluid flow between radially inner and outer sides thereof.
A second insert in the form of an annular ring 86 is also provided, bein~ reeeived in an annular notch 88 provided in radially inward edge of lower surface 90 of valve plate insert 80, and being provided with a plurality of spaced radially inwardly extending rein-foreing ribs 92 extending into engagement with surface 94 of sidewall 74. This is best shown in Figuse 6, in which is shswn in bottom plan a different version of the discharge valve, but with a ring-type suction valve of the same eonstruction as the present embodiment.
The terminal end 96 of sidewall 74 is positioned in coplanar selationship with lower surface 70 of valve plate 66, lower surface 90 of valve plate insert 80 and lower surface 98 of annular ring 86.
A suetion reed valve member 100 in the form of an annular ring sealingly engages lower surfaees 96 and 98 so as to prevent passage of fluid between insert ring 86 and surface 94 into compression chamber 102.
B A eentral opening 104 is provided in suction reed valve member~ ~ which is arran~ed eoaxially with discharge openin~ 72 so as to allow direct 1uid eomm~nication between eoQpression ehambeJ 102 and lower surface 34' of discnarge valve ~ember 30'. As best seen with reference to Figure 6, suction reed valve member 100 also has a pair of di~metrically opposed radially outwDrdly extending tab portions 108 and llO, each of whieh is provided with a suitable opening 112 extending therethrough~
As seen in Figure 5, tab portions 108 and 110 are reeeived in respeetive notched portions 114 Dnd 116 of eylinder hol~sing 84 with fasteners 82 , .
. 117957S
.
extcnding through opcnin~s 112 so as to rctnin suction rced v~lvc ~cmbcs 100 in operative Telationship thcrctoO
As the scciprocating piston ~not shown) disposcd within com-pression chnmber 102 moves away from valvc assembly 64 durin~ a suction stroke, the pressure differential between compression chambcr 102 and suction plenum 68 wnll cause suction reed valve membes 100 to deflect inwasdly with respect to compressior, chnmber 102 thereby enabling fluid n ow fsom suction plenum into com?rcssion chamber 102 throu~ inlet yassages 106. Because only tab portions lOB and 110 of suction reed valve member 100 extend outwardly beyond the sidewalls 118 of compres-sion chamber 102, suction n uid will readily flow into chamber 102 between suction reed valve member 100 and both surfaces 98 and 96 around substantially the entire inner and outer peripheries of suction valve member 100. As a compression stroke of the piston begins, suction.
valve 100 will be forced into sealing engagement with surfaces 96 and 98 and the discharge valve member will begin to operate in the manner described above with reference to Figures 1 through 4. ~hus, as a result of this concentric arrangement substantially the entire available surface area overlying compression chamber 102 is utilized for suction snd discharge valving and porting, thereby allowing maximum fluid flow both into and out of compression chamber 102.
Referring now to Figures 6 and 7, another embodimcnt of the present invention is illustrated which allows for e~en further utiliza-tion of the valve plate surfacc area overlying the compression chamber by providing a second concentrically arranged dischargo port area.
With thc exception of the discharge valve member and spring retainer, the various elcmcnts and portions of th~e suction and dischnrgc valve asscmbly 120 are substantially idcntical to the corrcsponding portions of valvc asscmhly 64 of Fi~urc S ~nd thcrcforc thc snmc numcrnls arc - " a . . .
.
. 117957~;
employed to designate identical portions Dnd further description thereof is believed UnneeCSSDry.
A disch~rge valve member 122 is provided disposed within discharge passage 72. Discharge valve member 122 is similar to dis-S eharge valve meml)er 30, being preferably fabricated from a polymerie composition having the aforementioned characteristics and having a frusto eonical shape including outwardly diverging sidewalls 124, a ; lower surface 126, and an u~per surf~ce 128; However, in this embodi-ment valve member 122 also is provided with a eentrally located generally 10 . frusto eonically-shaped opening 130 defined by upwardly eonverging sidewalls 132. A frusto eonieal dise member 134 having upwardly eon-verging sidewalls 136 is also provided which is secured to and supported by a eylindrical stud member 138. Stud member 138 has an upper threaded portion 140 which extends through a threaded opening 142 provided in a spring retainer m~mber 144 and cooperates therewith to enable a lower surface 146 of dise member 134 to be adjusted into substantially co-planar relationship with lower surfaces 70 and 126 of valve plate 66 and discharge valve member 122 respectively. Retainer member 144 also serves to limit opening movement of valve member 122.
As previously mentioned with regard to discharge valve member 30, conical sidewall 124 of discharge valve member 122 is preferably formed with an included angle (when unstressed) greater than the in-eluded angle of the cone of sidewall 78. In like manner and for the same reasons, the included angle of eonical sidewall 132 is greater (when unstressed) than the ineluded angle of the cone of sidewall 136.
The operation OI valve assembly 120 is substantially the sDme as thDt of valve assem~ly 64 deseribed above except that as dis-ehargo valve member 122 is eaused to move upwllrdly, eo ~ ressed fluid will be sble to exh~ust between both sidew~lls 78 and 124 Dnd between , ~" 117957S
' sidcwalls 132 nnd 136. This arrangcmcnt thcrcby offcrs substnntinlly incrcnscd disch3rgc flow ratcs to bc achicvcd within thc Tclativcly Tcstrictcd hcad area for a givcn cylindcr sizc by providing mcnns whcre-by the dischargc port arca is substantinlly incrcascd. Gn thc othcr S ha~d, this arrangcment is hnrder to m~nufacture because of the close tolerances required betwcen the two separate seats in order to get a good seal.
Figurc 8 illustrntcs a valvc assembly 146 a]so in accordnnCe with the presen. invention employing the discharge valve arrangement of Figure 6 in conjunction with a reed-type suction valve of the type described with Teference to the embodiment of Figures 1 through 4.
Accordingly, as the elements employed in this embodiment and the opers-tion thereof are substzntially identical to corresponding elements of Figures 1 through 4 and 6, like portions have been indicated by lS like numerals double primed and further description thereof is believed unnecessary.
Pigure 9 illustrates an alternative embodiment of the present invention, indicatcd generally at 148, in which the additional porting is provided over that of the embodiment of Figures l-S. Valve assembly Z0 148 comprises a valvc plate 150 having a conventional reed-type suction valve member lS2 engaging the lower surface 154 thereof and a frusto conical dischargs opening defined by upwardly diverging sidewalls 158 extending therethrough, all of which is substantially identical to that described with reference to Figures 1 through S above.
. . _ .
In this embodiment, however, a two-piece discharge valve asscmbly is providcd comprising a first frusto conical discharge vaIve membcr 160 having upwardly divcrging sidcwalls 162 ndnpted to sealingly en~nge sidcwnlls 158, an nnnular reoess 164 providcd in uppcr surface i66 thcrcof, nnd n ccntrally disposcd frusto conical shapcd opcning 14 ~
.
i-. .
1~7~S7~;
.; , . . .
defincd by sidcwalls 168 providcd within recess 1640 A second relatively vable frusto conical shapcd discharge valYc mcmbcr 170 is providcd having upwardly divcrging sidcwalls 172 adapted to sealingly engage sidewalls 168. Discharge valve mcmber 170 has a Tecess 174 providcd in upper surface 176 thereof which is adapted to receive one end of a biasing spring member 178 the other enl of which engages a shoulder 180 provided on depending protrusion 182 of spring retainer 184. A
sccond spring biasing mcmber 1~6 has one end rcceived in recess 164 of discharge valve member 160 and the otheT end engaging an annular 10 recess 188 surrounding protrusion 182 of spring retainer 184. Thus, spring biasing members 178 and 186 can operate independently to bias respective discharge valve members 170 and 160 into closed sealing engagement. Spring retainer 184 may also have stop means in the form of an annular shoulder 190 which is positioned to engage upper surface 15 166 of discharge valve member 160 while allowing continued upward move-ment of discharge valve member 170.
As is apparent, the relative sequence of opening of discharge valve members 160 and 170 may be easily selected by merely selecting the desired respective spring characteristics, using standard criteria.
20 Both discharge valve members 160 and 170 preferably are fabricated from a suitable polymeric composition having the aforementioned char-acteristics, have a thickness sufficient to provide the w cessary strength but less than the thickness of valve plate 150, and have both conical valve seats having includcd angles which are greater (when unstressed) 25 than the included angles of the respective valve seat sidewalls. Further, the relative diameters of discharge valve members 160 and 170 will bc such as to provide a substantially planar lower sur h ce with surface 154 of valve plate 15D.
-117957~
With rcspcct to thc rc~ativc an~lcs of inclinc of thc rcspcct-ive valve mcmbers and valve seats, applic~nt has obtaincd excellcnt test results with valvc membcrs havin~ an unstresscd sidcwall ~ngle with respect to the axis of the valve seat or disch~r~c passageway equal to approximately 47 (an included angle of 94~ , with a corre-sponding valve seat angle of 45 (an included angle of 90~ . These approximate relative angles apply to all of the disclosed embodiments of the invcntion, reg~rdless of ~-cthcr the valve membcr/valve seat interface is on the outside periphery of the valve member or on the inside periphery of the valve member.
lhe significant performance improvements obtained using the ; aforedescribed preferred emb æi~,ent of the discharge valve ~when sub-stituted for existing discharge valves m current refrigeration com-pres~ors), are also believed to be obtainable using other than polymeric materials For example, in Figures 10-15, there are illustrated several different lightweight designs in which the valve member is formed from metal, and which are believed to also provide the advantages of the present invention. In all of these embodiments the valve plate is indicated at 212, the discharge port or passageway at 218, the frusto conical valve seat at 228 and the helical compression spring at 244.
In Figure 10 the valve member, indicated generally at 230, is formed, such as by stamping from sheet metal, into the frusto conical form illustrated, having a generally flat centered disc portion 232 and upwardly and outwardly extending conical side walls 234, the outside surfaces of which sealingly engage valve seat 228 in exactly the same nanner as those of the previously described valve members. Valve mcmber 230 is contoured so that spring 244 will engagc same-at approximately the intcrscctions of portions 232 and 234. Thc embodimcnt of Figurc 11 is gc~crally similar to that of Figure lO with thc valve membcr, ~i ' .
11795~7S
indicated at 246, al50 being st~ed or similarly formed out of shcct metal, but is provide~ with an upstanding outer peripheral flange 248 defining an internal shoul~er for eng~ing and locatin~ sprin~ 244.
Figure 12 illustrates a generally similar valve member, indicated at S 250, which difhrs from preceding embodiment in that a definite annular pocket 252, having both bottom and side walls, is defined adjacent the outer periphery of the valve member for positioning and enga~ing spring 244. The cmbodiment of Figllre 13 comprises a valve member 254 which is essentially the same as that illustrated in Figure 12 but is contoured or relieved to minimize the weight thereof. As can be seen, the metal of eentered disc portion 232 is in great part substantially thinner, reinforcing being provided by integral ribs 2S6 and 2S8. The embodiments of Figures 12 and 13 may be formed by cold heading. Other manufacturing techniques, such as casting, may be applicable to any of the metal em-bodiments, as will be appreciated by one skilled in the art. In all of the above embodiments it is envisioned that the valve m~nber will be formed out of a single piece of metal, such as steel, bronze, aluminum, or the like.
It is envisioned that a valve member anbodying the principles of the present invention may also be fabricated in composite form in the manner illus~rated in Figures 14 and 15. In both of these figures the valve member itself, indicated at 260, is substantially the same as that shown in Figure 10, although of slightly lesser ga~Jge, with stiff-ening and strength being provided by a thickened or filled center section 262 formed of an extremely lightweight rigid material (such as, for example, rigid foam, metal honeycomb, or the like) securely bonded to valve member 260 and provided with a suitable reinforcing and protecting sheath 264 bonded to the opposite surfDee thereof and rigidly affixed - 30 to the inside surhce of valve member 260, such DS by brazing. Centersection 262 interconnocts valve mombor 260 to sheath 264 so that thoy ~ 17 -.
117957$
act as a singlc bcam. Shcath 264 ~nd mcmbcr 260 may bc formcd of any of the aforc~cscribcd mctals, and prcferably shcath 264 dcfines an annular rccess 266 to locatc and en~a~c spring 244.
In all of the embodiments illustrated in Figures 10 through 15 the respective angles of the valve seats and the outer surface of side walls 234 are identical to those described in the preceding embodiments, and the thickness of the side wall portion 234 is chosen (~or the m~tal uscd) ~o provide as light a WCig]lt as possible, as well as the compliance or resilience necessary to permit the valve member to close and seal without permanent deformation. Similarly, center disc portion 232 is formed as light as possible but of a sufficient thickness and strength for the material used (in combination with center stiffening section 262 where appl~cable) to provide a substanti-ally flat flush surface (i.e., no excessive distortion or permanent deformation) at the top of the cylinder chamber when fully closed and subjected to the maximum pressure differentials normally encountered, the same as in the case of the preceding ~nbodiments. In all of the embodiments formed from metal, the resulting valve member, whether it be of unitary construction or of composite construction, is extremely light weight compared to known conical valves and is believed to be capable of providing the advantages of the previously described poly-meric valve elements, particularly those disclosed in Figures 1 through 5. Ideally, the valve members of Pigures 10 through 15 will be formed in such a way and with such geoJnctry and of a material which will pro-vide the characte~istics achieved by applicant with the aforedescribcd prcferred form of the valve member. Although mctal valve mcmbers may be slightly noisier than polymcric valvcs, the progressive engagcment of valv¢ mcm~cr and valvc seat duc to thc rclativc an~lc thcreof is bclicvcd to provide somc de~rec of noisc attcnuation.
~ lg -.
.. . ' llt~9575 One of thc a~Y~ntagcs of the valvc of the prcscnt invcntion is that, unlikc recd valvcs, thc wcight or mass of the va]ve is indc-pendent of the force of the return spring ~i.c., spring 44, 44', 44", etc.). This makes it possible to choose the spring eo DptimiZe valvc frequency (to achieve closure as close to top dead center as possible) and/or valve preload (i.e., ~he initial sealing force in absence of a pressure differential). Because one of the more important functions of thc return spring is to stabilize the valve as it is cycled in response to changing pressure differentials, the spring is preferably of as large a diameter as is feasible.
In all embodiments of the invention the valve plate is utilized in the compressor in a conventional manner, and the pistons, cylinders, suction valves, manifolds, etc. are conventional. If desired, the top of the piston may be ver~ slightly contoured to fill the small, thin space in the center of the suction valve when the piston is at top dead center, thereby further reducing reexpansion volume. Also, the bridges may have three legs instead of two in order to increase flow area, H~ile it will be apparent that the preferred embodiments of the invention disClosed are well calculated to providé the advantages and features above statcd, it will be appreciated that the invention is susceptible to dification, variation and change without departing from the proper scope or fair meaning of the subjoined claims.
It should be notcd that valvc mcmbcr 30 will prcfcrably h~vc a thickness less than that of valvc platc 12 in ordcr to insurc adoquate sealing of sidewalls 32 with sid'cwalls 28 and to avoid a partial or complcte annular groove being worn in sidcwalls 32, which groove could possibly interfere with proper seating and/or sealing of valve member 30. Also, edge portion 60 will preferably be provided with a small radius or chamfer which operates to insure proper sealing even should valve mcmbcr bc shiftcd or cocked sliglltly during closing thereof.
Additionally, spring 4Z preferably has its ends squared snd ground and is of as large a di~meter as possible relative to the diameter of valve member 30 so as to place the biasing h rce exerted thereby closely adjacent the sealing sidewalls 3Z and to aid in preventing 8 shifting, tilting or other tislocation of valve member 30 during operation thereof.
While the present invention has been described with reference to Figures 1 through 4 utilizing a reed-type suction valve, it is also well suited for use with a conventional ring-type suction valve such as is shown in the embodiment indicated generally at 64 in Figure 5.
~alve assembly 64 includes a valve plate 66 having a relatively large irregularly shaped generally annular recessed portion 68 defining a suction plenum in the lower surface 70 thereof. A discharge opening 72 of frusto conical shape is also provided, bcing defined by a radially inwardly inclined or beveled sidewall 74 extending between upper surface 76 and lower surface 70 of valve plate 66. Surface 78 of sidewall 74 provides a valve seat for a discharge valve mcmber 30~ which is ur~ed into s¢aling en~agcment thcrcwith by gas pressure and a spring 44' cxtcnd;ng bctween valvc mcmbcr 30' and a spring retainer 50' all of which arc substantiolly identical to corrcsponding portions describcd abovc with rcfercnce to Figurcs 1 through 4 ~ 10 , , , , - 1179S7~;
; A generally annul3r valve plate insert 80 is disposed within recess 68 throu~h which fasteners B2 extend so as to seeure valve as-sembly 64 to a cylinder housingl84~ A plurality of spaced cutout areas or radially extendin~ slots (not shown) are provided throu~h valve S plate insert 80 so as to allow suction fluid flow between radially inner and outer sides thereof.
A second insert in the form of an annular ring 86 is also provided, bein~ reeeived in an annular notch 88 provided in radially inward edge of lower surface 90 of valve plate insert 80, and being provided with a plurality of spaced radially inwardly extending rein-foreing ribs 92 extending into engagement with surface 94 of sidewall 74. This is best shown in Figuse 6, in which is shswn in bottom plan a different version of the discharge valve, but with a ring-type suction valve of the same eonstruction as the present embodiment.
The terminal end 96 of sidewall 74 is positioned in coplanar selationship with lower surface 70 of valve plate 66, lower surface 90 of valve plate insert 80 and lower surface 98 of annular ring 86.
A suetion reed valve member 100 in the form of an annular ring sealingly engages lower surfaees 96 and 98 so as to prevent passage of fluid between insert ring 86 and surface 94 into compression chamber 102.
B A eentral opening 104 is provided in suction reed valve member~ ~ which is arran~ed eoaxially with discharge openin~ 72 so as to allow direct 1uid eomm~nication between eoQpression ehambeJ 102 and lower surface 34' of discnarge valve ~ember 30'. As best seen with reference to Figure 6, suction reed valve member 100 also has a pair of di~metrically opposed radially outwDrdly extending tab portions 108 and llO, each of whieh is provided with a suitable opening 112 extending therethrough~
As seen in Figure 5, tab portions 108 and 110 are reeeived in respeetive notched portions 114 Dnd 116 of eylinder hol~sing 84 with fasteners 82 , .
. 117957S
.
extcnding through opcnin~s 112 so as to rctnin suction rced v~lvc ~cmbcs 100 in operative Telationship thcrctoO
As the scciprocating piston ~not shown) disposcd within com-pression chnmber 102 moves away from valvc assembly 64 durin~ a suction stroke, the pressure differential between compression chambcr 102 and suction plenum 68 wnll cause suction reed valve membes 100 to deflect inwasdly with respect to compressior, chnmber 102 thereby enabling fluid n ow fsom suction plenum into com?rcssion chamber 102 throu~ inlet yassages 106. Because only tab portions lOB and 110 of suction reed valve member 100 extend outwardly beyond the sidewalls 118 of compres-sion chamber 102, suction n uid will readily flow into chamber 102 between suction reed valve member 100 and both surfaces 98 and 96 around substantially the entire inner and outer peripheries of suction valve member 100. As a compression stroke of the piston begins, suction.
valve 100 will be forced into sealing engagement with surfaces 96 and 98 and the discharge valve member will begin to operate in the manner described above with reference to Figures 1 through 4. ~hus, as a result of this concentric arrangement substantially the entire available surface area overlying compression chamber 102 is utilized for suction snd discharge valving and porting, thereby allowing maximum fluid flow both into and out of compression chamber 102.
Referring now to Figures 6 and 7, another embodimcnt of the present invention is illustrated which allows for e~en further utiliza-tion of the valve plate surfacc area overlying the compression chamber by providing a second concentrically arranged dischargo port area.
With thc exception of the discharge valve member and spring retainer, the various elcmcnts and portions of th~e suction and dischnrgc valve asscmbly 120 are substantially idcntical to the corrcsponding portions of valvc asscmhly 64 of Fi~urc S ~nd thcrcforc thc snmc numcrnls arc - " a . . .
.
. 117957~;
employed to designate identical portions Dnd further description thereof is believed UnneeCSSDry.
A disch~rge valve member 122 is provided disposed within discharge passage 72. Discharge valve member 122 is similar to dis-S eharge valve meml)er 30, being preferably fabricated from a polymerie composition having the aforementioned characteristics and having a frusto eonical shape including outwardly diverging sidewalls 124, a ; lower surface 126, and an u~per surf~ce 128; However, in this embodi-ment valve member 122 also is provided with a eentrally located generally 10 . frusto eonically-shaped opening 130 defined by upwardly eonverging sidewalls 132. A frusto eonieal dise member 134 having upwardly eon-verging sidewalls 136 is also provided which is secured to and supported by a eylindrical stud member 138. Stud member 138 has an upper threaded portion 140 which extends through a threaded opening 142 provided in a spring retainer m~mber 144 and cooperates therewith to enable a lower surface 146 of dise member 134 to be adjusted into substantially co-planar relationship with lower surfaces 70 and 126 of valve plate 66 and discharge valve member 122 respectively. Retainer member 144 also serves to limit opening movement of valve member 122.
As previously mentioned with regard to discharge valve member 30, conical sidewall 124 of discharge valve member 122 is preferably formed with an included angle (when unstressed) greater than the in-eluded angle of the cone of sidewall 78. In like manner and for the same reasons, the included angle of eonical sidewall 132 is greater (when unstressed) than the ineluded angle of the cone of sidewall 136.
The operation OI valve assembly 120 is substantially the sDme as thDt of valve assem~ly 64 deseribed above except that as dis-ehargo valve member 122 is eaused to move upwllrdly, eo ~ ressed fluid will be sble to exh~ust between both sidew~lls 78 and 124 Dnd between , ~" 117957S
' sidcwalls 132 nnd 136. This arrangcmcnt thcrcby offcrs substnntinlly incrcnscd disch3rgc flow ratcs to bc achicvcd within thc Tclativcly Tcstrictcd hcad area for a givcn cylindcr sizc by providing mcnns whcre-by the dischargc port arca is substantinlly incrcascd. Gn thc othcr S ha~d, this arrangcment is hnrder to m~nufacture because of the close tolerances required betwcen the two separate seats in order to get a good seal.
Figurc 8 illustrntcs a valvc assembly 146 a]so in accordnnCe with the presen. invention employing the discharge valve arrangement of Figure 6 in conjunction with a reed-type suction valve of the type described with Teference to the embodiment of Figures 1 through 4.
Accordingly, as the elements employed in this embodiment and the opers-tion thereof are substzntially identical to corresponding elements of Figures 1 through 4 and 6, like portions have been indicated by lS like numerals double primed and further description thereof is believed unnecessary.
Pigure 9 illustrates an alternative embodiment of the present invention, indicatcd generally at 148, in which the additional porting is provided over that of the embodiment of Figures l-S. Valve assembly Z0 148 comprises a valvc plate 150 having a conventional reed-type suction valve member lS2 engaging the lower surface 154 thereof and a frusto conical dischargs opening defined by upwardly diverging sidewalls 158 extending therethrough, all of which is substantially identical to that described with reference to Figures 1 through S above.
. . _ .
In this embodiment, however, a two-piece discharge valve asscmbly is providcd comprising a first frusto conical discharge vaIve membcr 160 having upwardly divcrging sidcwalls 162 ndnpted to sealingly en~nge sidcwnlls 158, an nnnular reoess 164 providcd in uppcr surface i66 thcrcof, nnd n ccntrally disposcd frusto conical shapcd opcning 14 ~
.
i-. .
1~7~S7~;
.; , . . .
defincd by sidcwalls 168 providcd within recess 1640 A second relatively vable frusto conical shapcd discharge valYc mcmbcr 170 is providcd having upwardly divcrging sidcwalls 172 adapted to sealingly engage sidewalls 168. Discharge valve mcmber 170 has a Tecess 174 providcd in upper surface 176 thereof which is adapted to receive one end of a biasing spring member 178 the other enl of which engages a shoulder 180 provided on depending protrusion 182 of spring retainer 184. A
sccond spring biasing mcmber 1~6 has one end rcceived in recess 164 of discharge valve member 160 and the otheT end engaging an annular 10 recess 188 surrounding protrusion 182 of spring retainer 184. Thus, spring biasing members 178 and 186 can operate independently to bias respective discharge valve members 170 and 160 into closed sealing engagement. Spring retainer 184 may also have stop means in the form of an annular shoulder 190 which is positioned to engage upper surface 15 166 of discharge valve member 160 while allowing continued upward move-ment of discharge valve member 170.
As is apparent, the relative sequence of opening of discharge valve members 160 and 170 may be easily selected by merely selecting the desired respective spring characteristics, using standard criteria.
20 Both discharge valve members 160 and 170 preferably are fabricated from a suitable polymeric composition having the aforementioned char-acteristics, have a thickness sufficient to provide the w cessary strength but less than the thickness of valve plate 150, and have both conical valve seats having includcd angles which are greater (when unstressed) 25 than the included angles of the respective valve seat sidewalls. Further, the relative diameters of discharge valve members 160 and 170 will bc such as to provide a substantially planar lower sur h ce with surface 154 of valve plate 15D.
-117957~
With rcspcct to thc rc~ativc an~lcs of inclinc of thc rcspcct-ive valve mcmbers and valve seats, applic~nt has obtaincd excellcnt test results with valvc membcrs havin~ an unstresscd sidcwall ~ngle with respect to the axis of the valve seat or disch~r~c passageway equal to approximately 47 (an included angle of 94~ , with a corre-sponding valve seat angle of 45 (an included angle of 90~ . These approximate relative angles apply to all of the disclosed embodiments of the invcntion, reg~rdless of ~-cthcr the valve membcr/valve seat interface is on the outside periphery of the valve member or on the inside periphery of the valve member.
lhe significant performance improvements obtained using the ; aforedescribed preferred emb æi~,ent of the discharge valve ~when sub-stituted for existing discharge valves m current refrigeration com-pres~ors), are also believed to be obtainable using other than polymeric materials For example, in Figures 10-15, there are illustrated several different lightweight designs in which the valve member is formed from metal, and which are believed to also provide the advantages of the present invention. In all of these embodiments the valve plate is indicated at 212, the discharge port or passageway at 218, the frusto conical valve seat at 228 and the helical compression spring at 244.
In Figure 10 the valve member, indicated generally at 230, is formed, such as by stamping from sheet metal, into the frusto conical form illustrated, having a generally flat centered disc portion 232 and upwardly and outwardly extending conical side walls 234, the outside surfaces of which sealingly engage valve seat 228 in exactly the same nanner as those of the previously described valve members. Valve mcmber 230 is contoured so that spring 244 will engagc same-at approximately the intcrscctions of portions 232 and 234. Thc embodimcnt of Figurc 11 is gc~crally similar to that of Figure lO with thc valve membcr, ~i ' .
11795~7S
indicated at 246, al50 being st~ed or similarly formed out of shcct metal, but is provide~ with an upstanding outer peripheral flange 248 defining an internal shoul~er for eng~ing and locatin~ sprin~ 244.
Figure 12 illustrates a generally similar valve member, indicated at S 250, which difhrs from preceding embodiment in that a definite annular pocket 252, having both bottom and side walls, is defined adjacent the outer periphery of the valve member for positioning and enga~ing spring 244. The cmbodiment of Figllre 13 comprises a valve member 254 which is essentially the same as that illustrated in Figure 12 but is contoured or relieved to minimize the weight thereof. As can be seen, the metal of eentered disc portion 232 is in great part substantially thinner, reinforcing being provided by integral ribs 2S6 and 2S8. The embodiments of Figures 12 and 13 may be formed by cold heading. Other manufacturing techniques, such as casting, may be applicable to any of the metal em-bodiments, as will be appreciated by one skilled in the art. In all of the above embodiments it is envisioned that the valve m~nber will be formed out of a single piece of metal, such as steel, bronze, aluminum, or the like.
It is envisioned that a valve member anbodying the principles of the present invention may also be fabricated in composite form in the manner illus~rated in Figures 14 and 15. In both of these figures the valve member itself, indicated at 260, is substantially the same as that shown in Figure 10, although of slightly lesser ga~Jge, with stiff-ening and strength being provided by a thickened or filled center section 262 formed of an extremely lightweight rigid material (such as, for example, rigid foam, metal honeycomb, or the like) securely bonded to valve member 260 and provided with a suitable reinforcing and protecting sheath 264 bonded to the opposite surfDee thereof and rigidly affixed - 30 to the inside surhce of valve member 260, such DS by brazing. Centersection 262 interconnocts valve mombor 260 to sheath 264 so that thoy ~ 17 -.
117957$
act as a singlc bcam. Shcath 264 ~nd mcmbcr 260 may bc formcd of any of the aforc~cscribcd mctals, and prcferably shcath 264 dcfines an annular rccess 266 to locatc and en~a~c spring 244.
In all of the embodiments illustrated in Figures 10 through 15 the respective angles of the valve seats and the outer surface of side walls 234 are identical to those described in the preceding embodiments, and the thickness of the side wall portion 234 is chosen (~or the m~tal uscd) ~o provide as light a WCig]lt as possible, as well as the compliance or resilience necessary to permit the valve member to close and seal without permanent deformation. Similarly, center disc portion 232 is formed as light as possible but of a sufficient thickness and strength for the material used (in combination with center stiffening section 262 where appl~cable) to provide a substanti-ally flat flush surface (i.e., no excessive distortion or permanent deformation) at the top of the cylinder chamber when fully closed and subjected to the maximum pressure differentials normally encountered, the same as in the case of the preceding ~nbodiments. In all of the embodiments formed from metal, the resulting valve member, whether it be of unitary construction or of composite construction, is extremely light weight compared to known conical valves and is believed to be capable of providing the advantages of the previously described poly-meric valve elements, particularly those disclosed in Figures 1 through 5. Ideally, the valve members of Pigures 10 through 15 will be formed in such a way and with such geoJnctry and of a material which will pro-vide the characte~istics achieved by applicant with the aforedescribcd prcferred form of the valve member. Although mctal valve mcmbers may be slightly noisier than polymcric valvcs, the progressive engagcment of valv¢ mcm~cr and valvc seat duc to thc rclativc an~lc thcreof is bclicvcd to provide somc de~rec of noisc attcnuation.
~ lg -.
.. . ' llt~9575 One of thc a~Y~ntagcs of the valvc of the prcscnt invcntion is that, unlikc recd valvcs, thc wcight or mass of the va]ve is indc-pendent of the force of the return spring ~i.c., spring 44, 44', 44", etc.). This makes it possible to choose the spring eo DptimiZe valvc frequency (to achieve closure as close to top dead center as possible) and/or valve preload (i.e., ~he initial sealing force in absence of a pressure differential). Because one of the more important functions of thc return spring is to stabilize the valve as it is cycled in response to changing pressure differentials, the spring is preferably of as large a diameter as is feasible.
In all embodiments of the invention the valve plate is utilized in the compressor in a conventional manner, and the pistons, cylinders, suction valves, manifolds, etc. are conventional. If desired, the top of the piston may be ver~ slightly contoured to fill the small, thin space in the center of the suction valve when the piston is at top dead center, thereby further reducing reexpansion volume. Also, the bridges may have three legs instead of two in order to increase flow area, H~ile it will be apparent that the preferred embodiments of the invention disClosed are well calculated to providé the advantages and features above statcd, it will be appreciated that the invention is susceptible to dification, variation and change without departing from the proper scope or fair meaning of the subjoined claims.
Claims (48)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. In combination with a gas compressor, an improved pressure responsive valve assembly comprising:
a valve plate having an inner surface in part defining a compression chamber of the compressor;
a discharge port extending through said valve plate;
means defining a valve seat of circular cross-section in said port, said valve seat being of increasing diameter in a direction away from said compression chamber; and a discharge valve member formed of a relatively compliant polymeric composition disposed within said port such that the inner surface of said discharge valve member lies substantially in the plane of said inner surface of said valve plate when the discharge port is closed, said discharge valve member having a peripheral edge surface adapted to sealingly engage said valve seat, said peripheral edge surface of said discharge valve member and the sidewall of said valve seat being configured so that a larger diameter portion of said edge surface engages said valve seat first during closure, whereby complete seating occurs incident to distortion of said discharge valve member, said distortion resulting in a reactive force tending to unseat said discharge valve member.
a valve plate having an inner surface in part defining a compression chamber of the compressor;
a discharge port extending through said valve plate;
means defining a valve seat of circular cross-section in said port, said valve seat being of increasing diameter in a direction away from said compression chamber; and a discharge valve member formed of a relatively compliant polymeric composition disposed within said port such that the inner surface of said discharge valve member lies substantially in the plane of said inner surface of said valve plate when the discharge port is closed, said discharge valve member having a peripheral edge surface adapted to sealingly engage said valve seat, said peripheral edge surface of said discharge valve member and the sidewall of said valve seat being configured so that a larger diameter portion of said edge surface engages said valve seat first during closure, whereby complete seating occurs incident to distortion of said discharge valve member, said distortion resulting in a reactive force tending to unseat said discharge valve member.
2. The combination as claimed in claim 1, wherein said peripheral edge surface of said discharge valve member and said sidewall of said valve seat opening are configured so that -the largest diameter portion of said edge surface sealingly engages said valve seat first during closure and last during opening of the valve, and a smaller diameter edge portion of said edge surface sealingly engages said valve seat upon complete closure of the valve, valve actuating pressure acting on the smaller area of said valve member within said smaller diameter upon full closure and on the full area of said valve member during opening.
3. The combination as claimed in claim 2, wherein said valve member is adapted to normally accommodate a pressure differential thereacross of known maximum value and is formed of a limited strength light-weight construction to reduce mass and enhance high speed operation, said valve member having an overall strength which is sufficient to withstand said pressure value acting on said smaller area without excessive distortion, and insufficient to withstand said pressure value acting across said full area.
4. The combination as claimed in claim 1, further comprising a spring biasing said valve member toward said valve seat.
5. The combination as claimed in claim 4, wherein the reactive force exerted away from said valve seat by said valve member as said valve member unstresses is greater than the force said spring applies against said valve member when seated.
6. The combination as claimed in claim 1, wherein said valve seat is conical in configuration.
7. The combination as claimed in claim 1, wherein said peripheral edge surface is conical in configuration.
8. The combination as claimed in claim 1, wherein said valve seat and said peripheral edge surface are conical in configuration.
9. The combination as claimed in claim l, further comprising a spring guiding and biasing said valve member toward said valve seat, said spring directly engaging said valve member and constituting the sole guide for said valve member as it moves toward and away from said valve seat.
10. The combination as claimed in claim 1, wherein said valve plate has an outer surface and said valve member, when fully closed, is disposed wholly between the planes of said inner and outer surfaces of said valve plate.
11. The combination as claimed in claim 1, further comprising a suction gas opening extending through said valve plate, said suction gas opening being generally annular in shape and surrounding said discharge valve seat opening; and an annular suction reed valve disposed in said compression chamber and surrounding said discharge valve seat opening to control the flow of suction gas through said suction gas opening,
12. The combination as claimed in claim 1, further comprising means limiting movement of said valve member with respect to said valve plate in a valve opening direction.
13. The combination as claimed in claim 1, further comprising means defining suction passages in said valve plate and a suction valve member engaging said inner surface of said valve plate to alternately allow and prevent fluid flow through said suction passages.
14. The combination as claimed in claim 13, wherein said suction valve member is a reed having a central opening therethrough aligned with said discharge valve seat opening.
15. The combination as claimed in claim 14, wherein said suction passages comprise a plurality of openings through said valve plate on one side of said discharge valve seat opening.
16. The combination as claimed in claim 14, wherein said suction passages comprise a plurality of openings disposed around the periphery of said discharge valve seat opening.
17. The combination as claimed in claim 16, wherein said suction valve comprises a circular annular reed disposed concentrically with said discharge valve seat opening.
18. The combination as claimed in claim l, further comprising means defining an opening through said discharge valve member and sealing means sealingly engaging the side-wall of said opening in said valve member when said discharge valve member is in a closed position so as to prevent fluid flow through said discharge valve seat opening, said sealing means and discharge valve member being movable relative to one another to allow additional discharge fluid flow when said discharge valve member is in an open position.
19. The combination as claimed in claim 18, wherein said sealing means comprises a frusto conically-shaped disc member sealingly disposed in said opening in said discharge valve member.
20. The combination as claimed in claim 19, wherein said sealing means and said valve member each have inner surfaces which are coplanar with said inner surface of said valve plate when said valve member is in a closed position.
21. The combination as claimed in claim 18, wherein said sidewall of said opening through said valve member and the outer peripheral surface of said sealing means are conical in configuration.
22. The combination as claimed in claim 21, wherein the unstressed included angle of said conical sidewall of said opening through said valve member is slightly different than the included angle of said conical surface of said sealing means.
23. The combination as claimed in claim 22, wherein said conical sidewall of said opening through said valve member has the greater included angle.
24. The combination as claimed in claim 22, wherein said conical surface of said sealing means has the greater included angle.
25. The combination as claimed in claim 18, further comprising support means fixedly supporting said sealing means relative to said valve plate.
26. The combination as claimed in claim 25, wherein said support means comprises a stud portion projecting out-wardly from said sealing means, and retention means affixed to said valve plate, said stud member being threadedly and adjustably connected to said retention means.
27. The combination as claimed in claim 26, further comprising coil spring means disposed coaxially of said stud portion and extending between said retention means and said valve member.
28. The combination as claimed in claim 18, wherein said sealing means is movable relative to said valve plate and to said discharge valve member.
29. The combination as claimed in claim 18, wherein said sealing means has an outwardly diverging peripheral edge sealingly engaging said sidewall of said opening, said edge diverging at an angle relative to the axis of said discharge valve seat opening greater than the corresponding angle of said opening in said valve member when the respective parts are unstressed.
30. The combination as claimed in claim 28, further comprising retention means mounted to said valve plate, and spring means disposed between said retention means and said sealing means for biasing the latter into sealing engagement with said opening in said valve member.
31. The combination as claimed in claim 1, wherein said seat and peripheral edge surface are conical in configuration, said unstressed included angle of said peripheral edge surface being approximately 94 degrees and said included angle of said conical sidewall of said valve seat opening being approximately 90 degrees.
32. The combination as claimed in claim 1, wherein said valve member is capable of distorting to conform to the valve seat.
33. The combination as claimed in claim 32, wherein said polymeric composition is a polyimide resin.
34. The combination as claimed in claim 32, wherein said polymeric composition is an aramid resin.
35. The combination as claimed in claim 32, wherein said polymeric composition is a polyester resin.
36. The combination as claimed in claim 32, wherein said polymeric composition is a polyphenylene sulfide resin.
37. The combination as claimed in claim 32, wherein said polymeric composition is a poly (amide-imide) resin.
38. The combination as claimed in claim 32, wherein said polymeric composition is a resin selected from the group consisting of polyimide, aramid, polyester, poly-phenylene sulfide, and poly (amide-imide).
39. The combination as claimed in claim 32, wherein said composition has a tensile strength to weight ratio greater than approximately 3.25 x 10.5 psi/lbm.
40. The combination as claimed in claim 32, wherein said composition has a flexural strength to flexural modulus ratio less than approximately 0.04.
41. The combination as claimed in claim 32, wherein said composition has a notched Izod impact strength greater than approximately 0.8.
42. The combination as claimed in claim 32, wherein said composition is a thermoplastic molding resin.
43. The combination as claimed in claim 32, wherein said valve member is annular and has an outwardly converging inner edge surface concentric with and inwardly of said peripheral edge surface for engaging a second valve seat which is concentric with the first valve seat and positioned radially inwardly of the first valve seat.
44. The combination as claimed in claim 43, wherein said edge surfaces are contoured so that the outer edge surface portion of largest diameter and the inner edge surface portion of smallest diameter engage their seats first during valve closure, whereby complete closure occurs incident to distortion of the valve member.
45. The combination as claimed in claim 32, wherein said valve member has a coaxial port defined by an outwardly diverging second valve seat adapted to cooperate with a second discharge valve member.
46. The combination as claimed in claim 45, wherein said first and second valve members are independently spring biased toward the closed positions thereof.
47. The combination as claimed in claim 1, wherein said valve member is contoured so that the pressure differential thereacross causes movement of said peripheral edge surface from partial engagement into full seating engagement with said valve seat.
48. The combination as claimed in claim 1, wherein said peripheral edge surface of said valve member is proportioned to engage said valve seat in essentially line contact in the absence of a pressure differential across said valve member, and wherein said valve member is movable in response to a net pressure above said valve member into area contact between said peripheral surface thereof and a corresponding surface of said valve seat accompanied by a reduction in the effective cross-sectional area of said valve member exposed to a pressure differential thereacross.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US97130978A | 1978-12-20 | 1978-12-20 | |
| US971,309 | 1978-12-20 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1179575A true CA1179575A (en) | 1984-12-18 |
Family
ID=25518200
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000341333A Expired CA1179575A (en) | 1978-12-20 | 1979-12-06 | Valve assembly |
Country Status (16)
| Country | Link |
|---|---|
| JP (2) | JPS5597572A (en) |
| AR (1) | AR222060A1 (en) |
| AT (1) | AT388974B (en) |
| AU (1) | AU523545B2 (en) |
| BE (1) | BE880746A (en) |
| BR (1) | BR7908354A (en) |
| CA (1) | CA1179575A (en) |
| DE (2) | DE2951462C2 (en) |
| DK (2) | DK156093C (en) |
| ES (1) | ES487055A1 (en) |
| FR (1) | FR2444820B1 (en) |
| GB (1) | GB2039004B (en) |
| IT (1) | IT1194601B (en) |
| MX (1) | MX150936A (en) |
| PH (1) | PH16984A (en) |
| SE (3) | SE7910405L (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4385872A (en) | 1980-01-22 | 1983-05-31 | Copeland Corporation | Compressor |
| US4329125A (en) | 1980-01-22 | 1982-05-11 | Copeland Corporation | Discharge valve |
| CA1214758A (en) * | 1981-02-13 | 1986-12-02 | Copeland Corporation | Discharge valve assembly |
| JPS6463669A (en) * | 1987-09-02 | 1989-03-09 | Toyoda Automatic Loom Works | Compressor |
| JPH0313153U (en) * | 1989-06-22 | 1991-02-08 | ||
| KR100323526B1 (en) * | 2000-03-03 | 2002-02-19 | 구자홍 | Discharge Apparatus of Compressor |
| WO2003006826A2 (en) * | 2001-07-13 | 2003-01-23 | Delaware Capital Formation, Inc. | Elastomeric sealing element for gas compressor valve |
| DE102016011058B4 (en) | 2016-09-12 | 2018-03-29 | Thomas Magnete Gmbh | Seat valve with electromagnetic actuation |
| DE102016011059A1 (en) | 2016-09-12 | 2018-03-15 | Thomas Magnete Gmbh | Seat valve with electromagnetic actuation |
Family Cites Families (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1718350A (en) * | 1929-06-25 | Valve fob pump assemblies | ||
| DE213136C (en) * | ||||
| US1490141A (en) * | 1921-07-21 | 1924-04-15 | Leigh W Morris | Compressor valve |
| US1514233A (en) * | 1922-12-01 | 1924-11-04 | Searles | Valve and the method of making it |
| DE452903C (en) * | 1924-10-22 | 1927-11-22 | Aaron Montgomery Searles | Poppet valve |
| US2358950A (en) * | 1941-11-04 | 1944-09-26 | Bendix Aviat Corp | Valve |
| US2366004A (en) * | 1942-10-29 | 1944-12-26 | Westinghouse Air Brake Co | Compressor valve |
| US2341709A (en) * | 1943-05-20 | 1944-02-15 | Morley V Friedell | Valve |
| FR940160A (en) * | 1946-01-31 | 1948-12-06 | Climax Rock Drill & Engineering Works Ltd | Valve enhancements for air compressors and pneumatic tools |
| GB679079A (en) * | 1950-09-15 | 1952-09-10 | Compressor Acdessories Ltd | Improvements in, or relating to, automatic valves for compressors and similar apparatus |
| US2900999A (en) * | 1955-07-21 | 1959-08-25 | Weatherhead Co | Valve seal |
| US3092139A (en) * | 1960-04-14 | 1963-06-04 | American Iron & Machine Works | Valve with means for controlling and indicating wear |
| DE1856211U (en) * | 1962-05-25 | 1962-08-09 | Ritzau Pari Werk Kg Paul | DIAPHRAGM VACUUM PUMP FOR VACUUM EXTRACTION FOR OBSTETRICS. |
| DE1550254A1 (en) * | 1966-06-23 | 1969-07-31 | Gerdts Gustav F Kg | Check valve |
| GB1199523A (en) * | 1968-01-13 | 1970-07-22 | Nat Res Dev | Valve Damping Means. |
| US3548868A (en) * | 1968-02-14 | 1970-12-22 | Sealol | Check valve with spring assisted flexible auxiliary valve seat |
| AT292906B (en) * | 1970-07-08 | 1971-09-10 | Hoerbiger Ventilwerke Ag | Lamella valve for reciprocating compressors |
| US3770009A (en) * | 1971-12-29 | 1973-11-06 | Victor Equipment Co | Sensitive check valve |
| DE2443030A1 (en) * | 1973-09-15 | 1975-03-20 | Bendix Westinghouse Ltd | COMPRESSOR |
| US4115044A (en) * | 1976-10-04 | 1978-09-19 | Tecumseh Products Company | Valve arrangement for compressor |
-
1979
- 1979-12-06 CA CA000341333A patent/CA1179575A/en not_active Expired
- 1979-12-07 IT IT27990/79A patent/IT1194601B/en active
- 1979-12-13 AU AU53778/79A patent/AU523545B2/en not_active Expired
- 1979-12-17 JP JP16395579A patent/JPS5597572A/en active Granted
- 1979-12-18 SE SE7910405A patent/SE7910405L/en unknown
- 1979-12-18 GB GB7943570A patent/GB2039004B/en not_active Expired
- 1979-12-19 DK DK544379A patent/DK156093C/en not_active IP Right Cessation
- 1979-12-19 FR FR7931154A patent/FR2444820B1/en not_active Expired
- 1979-12-19 ES ES487055A patent/ES487055A1/en not_active Expired
- 1979-12-19 BE BE0/198659A patent/BE880746A/en not_active IP Right Cessation
- 1979-12-19 AR AR279369A patent/AR222060A1/en active
- 1979-12-19 BR BR7908354A patent/BR7908354A/en not_active IP Right Cessation
- 1979-12-20 DE DE2951462A patent/DE2951462C2/en not_active Expired
- 1979-12-20 DE DE2954518A patent/DE2954518C2/de not_active Expired
- 1979-12-20 PH PH23443A patent/PH16984A/en unknown
- 1979-12-20 AT AT0806479A patent/AT388974B/en not_active IP Right Cessation
-
1980
- 1980-01-02 MX MX180609A patent/MX150936A/en unknown
-
1985
- 1985-12-20 DK DK596885A patent/DK161476C/en active
- 1985-12-30 SE SE8506153A patent/SE463731B/en not_active IP Right Cessation
-
1986
- 1986-03-17 SE SE8601230A patent/SE8601230D0/en unknown
-
1987
- 1987-11-18 JP JP62291655A patent/JPS63198785A/en active Granted
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