GB2039004A - Pressure responsive valve assembly - Google Patents

Pressure responsive valve assembly Download PDF

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Publication number
GB2039004A
GB2039004A GB7943570A GB7943570A GB2039004A GB 2039004 A GB2039004 A GB 2039004A GB 7943570 A GB7943570 A GB 7943570A GB 7943570 A GB7943570 A GB 7943570A GB 2039004 A GB2039004 A GB 2039004A
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Prior art keywords
valve
valve member
valve assembly
opening
discharge
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Granted
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GB7943570A
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GB2039004B (en
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Copeland Corp LLC
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Copeland Corp LLC
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component 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
    • F04B39/10Adaptations or arrangements of distribution members
    • F04B39/102Adaptations or arrangements of distribution members the members being disc valves

Abstract

A pressure responsive discharge valve assembly for use in reciprocating gas compressors, includes a discharge passage valve seat (18) of frusto conical shape in which a generally complementary shaped lightweight valve member (30), preferably formed from a polymeric material, is disposed. The included angles of the valve and seat are slightly different to provide progressive closing and sealing without permanent deformation. The materials used and the relative geometry 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. <IMAGE>

Description

SPECIFICATION Pressure responsive valve assembly The present invention relates generally to pressure responsive valve assemblies and more particularly to such valve assemblies adapted for use in reciprocating piston compressors, such as refrigeration compressors.
Reciprocating piston compressors typically employ suction and discharge pressure actuated valving mounted at the end of the cylinder between the head and cylinder housing. In designing these valve assemblies it is of critical importance to overall system operation to provide a sufficiently large port area to permit the flow of a maximum volume of fluid within a given time period ånd 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 operation should also be minimized.
These aspects take on increasing importance with high speed compressors.
Another important design objective is to minimize the reexpansion 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 chamber to an absolute minimum during the compression stroke without restricting gas flow.
While it may be possible to accompiish this objective by design of complex piston head shapes, manufacturing thereof becomes expensive, assembly more difficult, and throttling losses generally occur as the piston approaches top dead center. Reduction of reexpansion 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 valveseat combination improves the efficiency of the compressor by having improved flow characteristics at all valve lifts, good sealing without permanent deformation of the valve, long life, quietness in operation and an ability to operate in high speed compressors.
According to the present invention there is provided a pressure responsive valve assembly for a gas compressor, comprising: a valve plate having an inner surface defining in part a compression chamber; a discharge port extending through the valve plate; a valve seat of circular cross-section in said port, said valve seat being of increasing diameter in a direction away from the cylinder chamber: and a discharge valve member formed of a relatively compliant material disposed within said opening and having a peripheral edge surface adapted sealingly to engage said valve seat, said peripheral edge surface of said discharge valve member and said sidewall of said valve seat opening being configured so that a portion of said edge surface engages said valve seat first during closure, whereby complete seating occurs incident to distortion of said discharge valve member.
The valve assembly can be fabricated in a lightweight manner so as to obtain high force to weight ratios 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 preferably such as to present a substantially flat, flush end wall 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 minimum of top surface 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 the preferred embodiment and the relative geometries of the valve member and valve seat also reduced valve noise generated by the recurring impact of the valve member and valve seat. With the preferred embodiments valve port area is not a function of reexpansion volume; each can be optimized independently. Therefore, the valve assembly is suited for use both in air conditioning applications as well as heat pumps and low temperature units.
Further, the present arrangement can be used to maximize the use of the cylinder head area for valving.
The present invention will become further apparent from the following description given by way of example with reference to the accompanying drawings, in which: Figure 1 is a bottom 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 inverted 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 member in accordance with the present invention illustrating in an exaggerated manner the relative angles of inclination of the mating surfaces thereof, the valve member being shown in a position in which it is just beginning to seat; Figure 5 is a sectional view similar to and showing the valve assembly of Figure 2 but illustrating it in combination with a ring type suction valve; Figure 6 is a bottom plan view (from inside 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 combination with a reed type suction valve; Figure 9 is a fragmentary sectional view similar to that of Figure 7 but illustrating yet another embodiment of the discharge valve assembly of the present invention utilizing a polymeric valve member and; Figures 10 to 1 5 are fragmentary sectional views similar to Figure 4, but illustrating several embodiments of the valve member of the present invention formed out of metal.
Referring now to the drawings and in particular to Figures 1 to 3, there is illustrated 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 1 6 extending therethrough and a combined discharge passage and valve seat 18. A conventional reed type suction valve member 20 is also provided having an end portion 22 disposed in overlying valving relationship to suction passages 14 and 16, an opposite end portion 24 secured to valve plate 12 and an elongated centrally disposed opening 26 overlying discharge passage 18.
Recesses 29 are provided in the cylinder bore to provide clearance for the tips of the suction valve when it opens. the valve plate is mounted in the usual manner over a compressor cylinder defined by cylinder block 27 (in Figure 1 the position of the cylinder bore is shown in phantom).
As 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 1 8 with sidewalls 32 sealingly engaging sidewalls 28. As shown, discharge valve member 30-is-of a size and shape relative to discharge passage 18 so as to place lower surface 34 thereof in substantially coplanar relationship to lower surface 36 of valve plate 12. Discharge valve member 30 is also provided with a recess 38 in upper surface 40 thereof which receives an end portion 42 of a biasing means in the form of a helical compression spring 44, the opposite end 46 of which extends upwardly into engagement with a recess 48 provided in a bridge-like retainer member 50.The valve is essentially pressure actuated, and spring 44 is chosen primarily to provide stability and also an initial closing bias and a preload to establish an initial seal. Other types of springs than coil 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 performance polymeric material, and preferably a molding resin, such as polyimide, aramid, polyester, polyphenylene sulfide, and poly (amide-imide) resins. These materials have high strength, high temperature resistance, are relatively lightweight.
are unreactive, and are relatively compliant.
Although it is difficult to numerically define all of the desirable parameters for this material, it is thought that best results will be obtained using materials having a tensile strength to weight ratio greater than approximately 5 104 kilo/sq cm/kilom and a flexural strength to flexural modulus ratio less than approximately 0.04. In addition, the material should have a heat distortion temperature greater than 2300 C, high wear resistance, high internal dampening characteristics (for noise attenuation and sealing), compatibility with the environment, ease of manufacture (e.g., by compression or injection molding), low creep rate, and a high impact strength (preferably having a notched Izod impact strength greater than approximately 0.8).
At the present time the preferred material for the valve member is "Vespel", a polyimide resin available from duPont Company, Wilmington, Delaware. The compositions identified as "SP-1" and "SP-2 1" have been found to give excellent results. The use of such a polymeric composition for discharge valve member 30 facilitates easy fabrication, such as by molding, and the relative light weight of the valve member facilitates high speed operation due to the reduced inertia of the valve and the ability to use lighter springs, as well as reducing noise generated by contact of the valve and valve seat. The "Vespel" material is ideally suited for such application as it is able to resist degradation from relatively high temperatures and is unaffected by either refrigerant gas or lubricant.It has been found that the maximum operating temperature to which the refrigerant and lubricating oil can be subjected without damage is less than that for "Vespel." "Vespel" is also compliant enough to seal without permanent deformation.
Other suitable polymeric materials having the noted characteristics which it is believed may also be used, include those commercially available under the trademarks "Vespel" KS (an aramid resin available from the duPont Company), "Sparmon" (a polyimide resin available from Sparta Mfg. Co., Dover, Ohio), "Valve" 420 or 420-SEO (a glass reinforced, thermoplastic polyester available from the General Electric Co., Pittsfield, Mass.). "Ryton" (a polyphenylene sulfide available from Phiilips Petroleum Co., Bartlesville, Okla.), and "Torlon" (a poly (amide-imide) resin available from Amoco Chemicals Corp.,Chicago, Ill.
As shown in Figure 4, sidewalls 32 of valve member 30 are inclined relative to the center axis of discharge passageway 18 indicated at 55, at an angle 56 slightly greater (when unstressed) than the angle 58 of inclination of sidewalls 28 of the valve seat or discharge passage 18. An initial seal is achieved when the valve member closes to the position shown 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 primary closing force is that exerted by spring 44. Once an initial 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 valve member from the initial seal position of Figure 4 to the fully seated position of Figures 2, 3 and 5. Edge portion 60 deforms and becomes stressed as this seating takes place. The stress in edge portion 60 improves the degree of sealing and facilitates opening, but should not be so much as to cause permanent deformation of the valve member.
The valve member and spring are preferably designed so that the upward force exerted by the valve member as it unstresses and moves from its fully seated position to that shown in Figure.4 is significantly greater than the downward force exerted on the valve member by spring 44 during this initial opening movement. This significantly assists opening of the valve because as soon as the pressure differential across the valve member starts to reverse (i.e., after completion of the suction cycle and early in the discharge cycle) the residual stress in the valve member causes it to immediately spring off the valve seat (overcoming the force of spring 44) towards its Figure 4 position. This in turn immediately exposes 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 higher speed operation. It should also be noted that the passage area between opposed sidewalls 28 and 32 will continue to increase as valve member 30 is moved upwardly, thereby providing an extremely large area for fluid discharge with a given size port area. This provides worthwile increases in mass flow rate for a given compressor speed.
It should be noted that when the valve member is fully seated (as in Figures 2, 3 and 5) the effective area thereof exposed to the pressure differential is that defined by discharge passage 18, i.e., a considerably smaller area than that defined by the outer periphery of the valve.
Because it is desirable to use as light a weight construction as possible to maximize valve acceleration, it is thereby possible to construct the valve sufficiently light (considering material strengths and structural design) that it need not be able to accommodate (without excessive or permanent deformation) the stresses which would result if the maximum pressure differential across the valve member was applied to the maximum area thereof when seated, so long as the valve member accommodates the maximum pressure differential acting across the smaller effective 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 crosssectional area thereof was subjected to the pressure differentials thereacross.The relative angles of the valve member and seat also serve to cushion the impact of the parts on closing, thereby contributing (along with light weight) to the reduction of noise and wear.
It should be noted that valve member 30 will preferably have a thickness less than that of valve plate 12 in order to insure adequate sealing of sidewalls 32 with sidewalls 28 and to avoid a partial or complete annular groove being worn in sidewalls 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 member be shifted or cocked slightly during closing thereof.Additionally, spring 42 preferably has its ends squared and ground and is of as large a diameter as possible relative to the diameter of valve member 30 so as to place the biasing force exerted thereby closely adjacent the sealing sidewalls 32 and to aid in preventing a shifting, tilting or other dislocation 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. Valve 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, being 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 member 30' which is urged into sealing engagement therewith by gas pressure and a spring 44' extending between valve member 30' and a spring retainer 50' all of which are substantially identical to corresponding portions described above with reference to Figures 1 through 4.
A generally annular valve plate insert 80 is disposed within recess 68 through which fasteners 82 extend so as to secure valve assembly 64 to a cylinder housing 84. A plurality of spaced cutout areas or radially extending slots (not shown) are provided through valve 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, being received 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 reinforcing ribs 92 extending into engagement with surface 94 of sidewall 74.
This is best shown in Figure 6, in which is shown in bottom plan a different version of the discharge valve, but with a ring-type suction valve of the same construction as the present embodiment.
The terminal end 96 of sidewall 74 is positioned in coplanar relationship 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 suction reed valve member 100 in the form of an annular ring sealingly engages lower surfaces 96 and 98 so as to prevent passage of fluid between insert ring 86 and surface 94 into compression chamber 102. A central opening 104 is provided in suction reed valve member 98 which is arranged coaxially with discharge opening 72 so as to allow direct fluid communication between compressor chamber 102 and lower surface 34' of discharge valve member 30'.As best seen with reference to Figure 6, suction reed valve member 1 0O also has a pair of diametrically opposed radially outwardly extending tab portions 108 and 110, each of which is provided with a suitable opening 112 extending therethrough. As seen in Figure 5, tab portions 108 and 110 are received in respective notched portions 114 and 116 of cylinder housing 84 with fasteners 82 extending through openings 112 so as to retain suction reed valve member 100 in operative relationship thereto.
As the reciprocating piston (not shown) disposed within compression chamber 102 moves away from valve assembly 64 during a suction stroke, the pressure differential between compression chamber 102 and suction plenum 68 will cause suction reed valve member 100 to deflect inwardly with respect to compression chamber 102 thereby enabling fluid flow from suction plenum into compression chamber 102 through inlet passages 106. Because only tab portions 108 and 110 of suction reed valve member 100 extend outwardly beyond the sidewalls 118 of compression chamber 102, suction fluid 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. Thus, as a result of this concentric arrangement substantially the entire available surface area overlying compression chamber 102 is utilized for suction and discharge valving and porting, thereby allowing maximum fluid flow both into and out of j compression chamber 1 02.
Referring now to Figures 6 and 7, another embodiment of the present invention is illustrated which allows for even further utilization of the valve plate surface area overlying the compression chamber by providing a second concentrically arranged discharge port area. With the exception of the discharge valve member and spring retainer, the various elements and portions of the suction and discharge valve assembly 120 are substantially identical to the corresponding portions of valve assembly 64 of Figure 5 and therefore the same numerals are employed to designate identical portions and further description thereof is believed unnecessary.
A discharge valve member 122 is provided disposed within discharge passage 72. Discharge valve member 122 is similar to discharge valve member 30, being preferably fabricated from a polymeric composition having the aforementioned characteristics and having a frusto conical shape including outwardly diverging sidewalls 124, a lower surface 126, and an upper surface 128.
However, in this embodiment valve member 122 also is provided with a centrally located generally frusto conically-shaped opening 130 defined by upwardly converging sidewalls 132. A frusto conical disc member 1 34 having upwardly converging sidewalls 136 is also provided which is secured to and supported by a cylindrical stud member 138. Stud member 138 has an upper threaded portion 140 which extends through a threaded opening 142 provided in a spring retainer member 144 and cooperates therewith to enable a lower surface 146 of disc member 134 to be adjusted into substantially coplanar 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 included angle of the cone of sidewall 78. In like manner and for the same reasons, the included angle of conical sidewall 132 is greater (when unstressed) than the included angle of the cone of sidewall 136.
The operation of valve assembly 1 20 is substantially the same as that of valve assembly 64 described above except that as discharge valve member 122 is caused to move upwardly, compressed fluid will be able to exhaust between both sidewalls 78 and 124 and between sidewalls 132 and 136. This arrangement thereby offers substantially increased discharge flow rates to be achieved within the relatively restricted head area for a given cylinder size by providing means whereby the discharge port area is substantially increased. On the other hand, this arrangement is harder to manufacture because of the close tolerances required between the two separate seats in order to get a good seal.
Figure 8 illustrates a valve assembly 146 also in accordance with the present invention employing the discharge valve arrangement of Figure 6 in conjunction with a reed-type suction valve of the type described with reference to the embodiment of Figures 1 through 4. Accordingly, as the elements employed in this embodiment and the operation thereof are substantially identical to corresponding elements of Figures 1 through 4 and 6, like portions have been indicated by like numerals double primed and further description thereof is believed unnecessary.
Figure 9 illustrates an alternative embodiment of the present invention, indicated generally at 148, in which the additional porting is provided over that of the embodiment of Figures 1-5..
Valve assembly 148 comprises a valve plate 1 50 having a conventional reed-type suction valve member 152 engaging the lower surface 1 54 thereof and a frusto conical discharge opening defined by upwardly diverging sidewalls 1 58 extending therethrough, all of which is substantially identical to that described with reference to Figures 1 through 5 above.
In this embodiment, however, a two-piece discharge valve assembly is provided comprising a first frusto conical discharge valve member 1 60 having upwardly diverging sidewalls 1 62 adapted to sealingly engage sidewalls 158, an annular recess 1 64 provided in upper surface 1 66 thereof, and a centrally disposed frusto conical shaped opening defined by sidewalls 168 provided within recess 1 64. A second relatively movable frusto conical shaped discharge valve member 1 70 is provided having upwardly diverging sidewalls 1 72 adapted to sealingly engage sidewalls 1 68. Discharge valve member 1 70 has a recess 174 provided in upper surface 1 76 thereof which is adapted to receive one end of a biasing spring member 1 78 the other end of which engages a shoulder 180 provided on depending protrusion 1 82 of spring retainer 1 84. A second spring biasing member 1 86 has one end received in recess 164 of discharge valve member 1 60 and the other end engaging an annular recess 1 88 surrounding protrusion 1 82 of spring retainer 184.
Thus, spring biasing members 178 and 1 86 can operate independently to bias respective discharge valve members 1 70 and 1 60 into closed sealing engagement. Spring retainer 1 84 may also have stop means in the form of an annular shoulder 1 90 which is positioned to engage upper surface 1 66 of discharge valve member 1 60 while allowing continued upward movement of discharge valve member 1 70.
As is apparent, the relative sequence of opening of discharge valve members 1 60 and 1 70 may be easily selected by merely selecting the desired respective spring characteristics, using standard criteria. Both discharge valve members 160 and 170 preferably are fabricated from a suitable polymeric composition having the aforementioned characteristics, have a thickness sufficient to provide the necessary strength but less than the thickness of valve plate 1 50, and have both conical valve seats having included angles which are greater (when unstressed) than the included angles of the respective valve seat sidewalls.Further, the relative diameters of discharge valve members 1 60 and 170 will be such as to provide a substantially planar lower surface with surface 1 54 of valve plate 1 50.
With respect to the relative angles of incline of the respective valve members and valve seats, applicant has obtained excellent test results with valve members having an unstressed sidewall angle with respect to the axis of the valve seat or discharge passageway equal to approximately 450 (an included angle of 900), with a corresponding valve seat angle of 470 (an included angle of 940). These approximate relative angles apply to all of the disclosed embodiments of the invention, regardless of whether the valve member/vaive seat interface is on the outside periphery of the valve member or on the inside periphery of the valve member.
The significant performance improvements obtained using the aforedescribed preferred embodiment of the discharge valve (when substituted for existing discharge valves in current refrigeration compressors), are also believed to be obtainable using other then polymeric materials. For example, in Figures 10-1 5, 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 manner as those of the previously described valve members. Valve member 230 is contoured so that spring 244 will engage same at approximately the intersections of portions 232 and 234. The embodiment of Figure 11 is generally similar to that of Figure 10 with the valve member indicated at 246, also being stamped or similarly formed out of sheet metal, but is provided with an upstanding outer peripheral flange 248 defining an internal shoulder for engaging and locating spring 244. Figure 1 2 iliustrates a generally similar valve member, indicated at 250, which differs 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 engaging spring 244. The embodiment of Figure 1 3 comprises a valve member 254 which is essentially the same as that illustrated in Figure 1 2 but is contoured or relieved to minimize the weight thereof. As can be seen, the metal of centered disc portion 232 is in great part substantially thinner, reinforcing being provided by integral ribs 256 and 258. 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 embodiments, as will be appreciated by one skilled in the art. In all of the above embodiments it is envisioned that the valve member will be formed out of a single piece of metal, such as steel, bronze, aluminium, or the like.
It is envisioned that a valve member embodying the principles of the present invention may also be fabricated in composite form in the manner illustrated in Figures 14 and 1 5. 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 gauge, with stiffening 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 surface thereof and rigidly affixed to the inside surface of the valve member 260, such as by brazing.Center section 262 interconnects valve member 260 to sheath 264 so that they act as a single beam.
Sheath 264 and member 260 may be formed of any of the aforedescribed metals, and preferably sheath 264 defines an annular recess 266 to locate and engage spring 244.
In all of the embodiments illustrated in Figures 10 through 1 5 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 (for the metal used) to provide as light a weight 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 applicable) to provide a substantially 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 differenctials normally encountered, the same as in the case of the preceding embodiments. 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 polymeric valve elements, particularly those disclosed in Figures 1 thorugh 5.Ideally, the valve members of Figures 10 through 1 5 will be formed in such a way and with such geometry and of a material which will provide the characteristics achieved by applicant with the aforedescribed preferred form of the valve member. Although metal valve members may be slightly noisier than polymeric valves, the progressive engagement of valve member and valve seat due to the relative angle thereof is believed to provide some degree of noise attenuation.
One of the advantages of the valve of the present invention is that, unlike reed valves; the weight or mass of the valve is independent of the force of the return spring (i.e., spring 44, 44', 44", etc.). This makes it possible to choose the spring to optimize valve frequency (to achieve closure as close to top dead center as possible) and/or valve preload (i.e., the initial sealing force in absence of a pressure differential). Because one of the more important functions of the 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 very 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.

Claims (45)

1. A pressure responsive valve assembly for a gas compressor. comprising: a valve plate having an inner surface defining in part a compression chamber; a discharge port extending through the valve plate; a valve seat of circular cross-section in said port, said valve seat being of increasing diameter in a direction away from the cylinder chamber; and a discharge valve member formed of a relatively compliant material disposed within said opening and having a peripheral edge surface adapted sealingly to engage said valve seat, said peripheral edge surface of said discharge valve member and said sidewall of said valve seat opening being configured so that a portion of said edge surface engages said valve seat first during closure, whereby complete seating occurs incident to distortion of said discharge valve member.
2. A valve assembly as claimed in claim 1, wherein the largest diameter portion of said edge surface engages the valve seat first.
3. A valve assembly as claimed in claim 1, wherein said peripheral edge surface of said discharge valve member and said sidewall of said valve seat openings 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 when the valve is fully closed and on the full area of said valve member during opening.
4. A valve assembly as claimed in claim 3, wherein said valve member is adapted normally to accommodate a pressure differential thereacross of a predetermined maximum value and is formed of a iimited 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.
5. A valve assembly as claimed in claim 1, 2, 3 or 4, further comprising a spring biasing said valve member toward said valve seat.
6. A valve assembly as claimed in claim 5, wherein the force exerted away from the valve seat by the valve member as the valve member unstresses incident to relieving the tension of the valve member is greater than the force the spring applies against the valve member when seated.
7. A valve assembly as claimed in any preceding claim, wherein said valve seat is frusto conical in configuration.
8. A valve assembly as claimed in any preceding claim, wherein said peripheral edge surface is frusto-conical in configuration.
9. A valve assembly as claimed in any preceding claim, 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. A valve assembly as claimed in any preceding claim, wherein said valve member has an inner surface which is substantially flush with said inner surface of said valve plate when said valve member is seated.
1 A valve assembly as claimed in any preceding claim, 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.
12. A valve assembly as claimed in any preceding claim, further comprising means - limiting movement of said valve member with respect to said valve plate in a valve opening direction.
13. A valve assembly as claimed in any preceding claim, 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.
14. A valve assembly as claimed in any of claims 1 to 12, further comprising means defining suction passages in said valve plate and a suction valve member engaging said inner surface of said valve plate and operative alternately to allow and to prevent fluid flow through the suction passages.
1 5. A valve assembly as claimed in claim 14, wherein said suction valve member is a reed having a central opening therethrough aligned with said discharge valve seat opening.
1 6. A valve assembly as claimed in claim 14 or 15, wherein said suction passages comprise a plurality of openings through said valve plate on one side of said discharge valve seat openings.
17. A valve assembly as claimed in claim 14 or 15, wherein said suction passages comprise a plurality of openings disposed around the periphery of said discharge valve seat.
1 8. A valve assembly as claimed in claim 17, wherein said suction valve comprises a circular annular reed disposed concentrically with said discharge valve seat opening.
1 9. A valve assembly as claimed in any preceding claim, wherein an opening is provided through the discharge valve member and sealing means sealingly engage the sidewall 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.
20. A valve assembly as claimed in claim 19, wherein said sealing means comprises a frustoconically-shaped disc member.
21. A valve assembly as claimed in claim 20, 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.
22. A valve assembly as claimed in claim 19, 20 or 21, wherein said sidewall of said opening through said valve member and the outer peripheral surface of said sealing means are frusto conical in configuration.
23. A valve assembly as claimed in claim 22, wherein the unstressed included angle of said frusto conical sidewall of said opening through said valve member is slightly different than the included angle of said frusto conical surface of said sealing means.
24. A valve assembly as claimed in claim 23, wherein said frusto conical sidewall of said opening through said valve member has the greater included angle.
25. A valve assembly as claimed in claim 23, wherein said frusto conical surface of said sealing means has the greater included angle.
26. A valve assembly as claimed in any one of claims 19 to 25, further comprising support means fixedly supporting said sealing means relative to said valve plate.
27. A valve assembly as claimed in claim 26, wherein said support means comprises a stud portion, projecting outwardly from said sealing means, and retention means affixed to said valve plate, said stud member being threadedly and adjustably connected to said retention means.
28. A valve assembly as claimed in claim 27, further comprising coil spring means disposed coaxially of said stud portion and extending between said retention means and said valve member.
29. A valve assembly as claimed in claim 19, wherein said sealing means is moveable relative to said valve plate and to said discharge valve member.
30. A valve assembly as claimed in claim 19, 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.
31. A valve assembly as claimed in any one of claims 1 9 to 30, further comprising retention means mounted to said valve plate, and spring means disposed between said retention means and said disc member for biasing the latter into sealing engagement with said opening in said valve member.
32. A valve assembly as claimed in any preceding claim, wherein said seat and peripheral edge surface are frusto conical in configuration, with the unstressed included angle of said peripheral edge surface being approximately 94 degrees and said included angle of the frusto conical sidewall of the valve seat opening being approximately 90 degrees.
33. A valve assembly as claimed in any preceding claim, wherein said valve element is formed of a compliant polymeric composition capable of distorting to conform to the valve seat.
34. A valve assembly as claimed in claim 33, wherein said polymeric composition is a polyimide resin, an aramid resin, a polyester resin, a polyphenylene sulfide resin or a poly (amide/imide) resin.
35. A valve assembly as claimed in claim 33 or 34, wherein said composition has a tensile strength to weight ratio greater than 5 x 104 kilo/sq. cm/kilorn.
36. A valve assembly as claimed in claim 33, 34 or 35, wherein said composition has a flexural strength to flexural modulus less than approximately 0.04.
37. A valve assembly as claimed in any one of claims 33 to 36, wherein said composition has a notched Izod impact strength greater than 0.8.
38. A valve assembly as claimed in any one of claims 33 to 37, wherein said composition is a thermoplastic moulding resin.
39. A valve assembly as claimed in claim 34, wherein said valve element is annular and has an outwardly converging second seating surface concentric with and inwardly of said first seating surface for engaging a second valve seat which is concentric with said first valve seat and positioned radially inwardly of the first valve seat.
40. A valve assembly as claimed in any preceding claim, wherein said valve element has a coaxial port defined by an outwardly diverging second valve seat adapted to cooperate with a second discharge valve element.
41. A valve assembly as claimed in claim 40, wherein said first and second valve elements are independently spring biased toward closed positions thereof.
42. A valve assembly as claimed in any preceding claim, wherein said valve member is so contoured that pressure differential thereacross is operative in use thereof to cause movement of said peripheral edge surface from partial engagement into full seating engagement with said valve seat.
43. A valve assembly as claimed in any preceding claim, wherein said peripheral edge surface of said valve member is proportioned to engage said valve seat in essentially line contact in the absence of said 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 crosssectional area of said valve member exposed to a pressure differential thereacross.
44. Pressure responsive valve assemblies constructed and arranged to operate substantially as herein described with reference to and as illustrated in the accompanying drawings.
45. A refrigeration compressor including a pressure responsive valve assembly as claimed in any preceding claim.
GB7943570A 1978-12-20 1979-12-18 Pressure responsive valve assembly Expired GB2039004B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US97130978A 1978-12-20 1978-12-20

Publications (2)

Publication Number Publication Date
GB2039004A true GB2039004A (en) 1980-07-30
GB2039004B GB2039004B (en) 1983-01-26

Family

ID=25518200

Family Applications (1)

Application Number Title Priority Date Filing Date
GB7943570A Expired GB2039004B (en) 1978-12-20 1979-12-18 Pressure responsive 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)

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US4385872A (en) 1980-01-22 1983-05-31 Copeland Corporation Compressor
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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
BR0211144B1 (en) * 2001-07-13 2011-09-20 sealing element for gas compressor valve, gas compressor reciprocating valve, method for making said valve and reciprocating gas compressor.
DE102016011059A1 (en) 2016-09-12 2018-03-15 Thomas Magnete Gmbh Seat valve with electromagnetic actuation
DE102016011058B4 (en) 2016-09-12 2018-03-29 Thomas Magnete Gmbh Seat valve with electromagnetic actuation

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Also Published As

Publication number Publication date
SE7910405L (en) 1980-06-21
SE463731B (en) 1991-01-14
SE8506153L (en) 1985-12-30
ATA806479A (en) 1989-02-15
AR222060A1 (en) 1981-04-15
CA1179575A (en) 1984-12-18
JPS6325234B2 (en) 1988-05-24
DK596885A (en) 1985-12-20
JPS5597572A (en) 1980-07-24
IT1194601B (en) 1988-09-22
IT7927990A0 (en) 1979-12-07
GB2039004B (en) 1983-01-26
AT388974B (en) 1989-09-25
SE8601230D0 (en) 1986-03-17
DK161476B (en) 1991-07-08
DE2951462C2 (en) 1986-11-13
DE2954518C2 (en) 1989-06-08
SE8601230L (en) 1986-03-17
DK156093B (en) 1989-06-19
JPS63198785A (en) 1988-08-17
PH16984A (en) 1984-05-04
BR7908354A (en) 1980-07-22
MX150936A (en) 1984-08-22
AU5377879A (en) 1980-06-26
BE880746A (en) 1980-04-16
FR2444820A1 (en) 1980-07-18
FR2444820B1 (en) 1986-04-11
ES487055A1 (en) 1980-07-01
DK596885D0 (en) 1985-12-20
DK156093C (en) 1989-11-13
SE8506153D0 (en) 1985-12-30
DK161476C (en) 1991-12-16
JPH0154554B2 (en) 1989-11-20
DK544379A (en) 1980-06-21
DE2951462A1 (en) 1980-07-10
AU523545B2 (en) 1982-08-05

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PE20 Patent expired after termination of 20 years

Effective date: 19991217