US20180238312A1 - Reciprocating Compressor Vented Piston - Google Patents
Reciprocating Compressor Vented Piston Download PDFInfo
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- US20180238312A1 US20180238312A1 US15/752,058 US201615752058A US2018238312A1 US 20180238312 A1 US20180238312 A1 US 20180238312A1 US 201615752058 A US201615752058 A US 201615752058A US 2018238312 A1 US2018238312 A1 US 2018238312A1
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- Prior art keywords
- compressor
- piston
- projection
- channel
- valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—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 adaptations of pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
- F04B1/124—Pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/06—Venting
Definitions
- One aspect of the disclosure involves a compressor comprising: a case; and at least one piston mounted for reciprocating movement, each in a respective cylinder of the case.
- the at least one piston having a peripheral surface and an upper surface, the upper surface having an outer portion and a projection extending from the upper surface.
- the at least one piston has a channel positioned to pass flow from an area above the outer portion.
- the channel has a lower end along a side of the projection.
- the channel is one of a plurality of like channels distributed circumferentially about the at least one piston.
- the projection has a frustoconical lateral surface.
- the at least one piston comprises a plurality of identical pistons.
- the cylinder is formed in a cylinder block; a valve plate assembly is mounted to the cylinder block; and the at least one piston has a top-dead-center condition wherein the projection is at least partially within the valve plate assembly.
- the valve plate assembly has a seat forming a seating surface of a suction valve; and, in the top-dead-center condition, the projection is partially received within the seat.
- a method for using the compressor comprises: reciprocating the piston in the cylinder, during an upward portion of the reciprocating a flow of fluid moving upward in the channel.
- FIG. 1B is an enlarged view of a portion of the forward-most cylinder of the compressor of FIG. 1 .
- FIG. 2 is an isolated view of a piston of the compressor of FIG. 1 .
- Each piston has a lateral or side or outer diameter (OD) surface 50 ( FIG. 1A ) and an upper or top surface 52 .
- FIG. 1A shows a forward-most piston in a top-dead-center (TDC) position. In the TDC position, a lateral portion 54 of the upper surface 52 is approximately flush to an upper surface 60 of the cylinder block 44 .
- a valve plate assembly 70 is mounted atop the surface 60 (a gasket 62 intervening) and bears valve assemblies 72 associated with the respective cylinders. As is discussed further below, the valve assemblies 72 each comprise portions forming an inlet or suction valve and portions forming a discharge or outlet valve.
- a cylinder head 74 is mounted atop the valve plate assembly (a gasket 75 intervening) and encloses a discharge plenum 76 in communication with the discharge port 26 .
- FIG. 1A further shows the pistons comprising an upward projection 80 (having a lateral or side or outer diameter (OD) surface 82 and an upper or distal end 84 ) which, in the forward-most piston illustrated top-dead-center condition or position protrudes into the valve plate assembly 70 . This helps minimize the headspace in the top-dead-center condition for improved overall flow.
- an upward projection 80 having a lateral or side or outer diameter (OD) surface 82 and an upper or distal end 84 ) which, in the forward-most piston illustrated top-dead-center condition or position protrudes into the valve plate assembly 70 . This helps minimize the headspace in the top-dead-center condition for improved overall flow.
- OD lateral or side or outer diameter
- the exemplary valve plate assembly 70 comprises a bottom plate 90 and a top plate 92 separated by spacers.
- the spacers may include a perimeter plate 94 matching the perimeter of the valve plate assembly so as to enclose a plenum 96 . Additional spacers 98 may be distributed within the plenum.
- the plenum 96 is a suction plenum in communication with the suction port 24 .
- the suction plenum 96 may be in communication with the interior of the motor case via a passageway (not shown) cast in the case assembly.
- the exemplary seat 132 comprises an upper portion mounted to the upper plate 92 (e.g., via press fit, braze, or the like) and a lower portion depending through the plenum 96 and through an associated aperture 140 in the bottom plate 90 .
- reduced pressure/suction causes the valve element 120 to flex, bending in the middle (like a U) and supported by the two tabs 135 at the edge of the cylinder bore and stopped by cooperation of tabs 136 and complementary associated surfaces of recesses in the cylinder.
- the exemplary ID seat is formed by an outer diameter perimeter surface 164 of an inner seat member 166 .
- the member 166 is secured centrally to a valve guide 170 which, in turn, is mounted atop the upper plate 92 .
- One or more springs 180 e.g., a circumferential array of metallic coil springs held in pockets 182 in the guide (e.g., three to twenty such springs and pocket combinations per cylinder or eight to sixteen, with an exemplary twelve shown) may bias the valve element 152 into its closed condition.
- FIG. 1A adds channels 220 to a baseline piston configuration.
- the channels extend from lower ends 224 to upper ends 226 .
- the lower ends may generally form inlet ports (inlets) and the upper ends 226 may generally form outlet ports (outlets) for flow to pass during that final stage of upward movement of the piston to the top-dead-center condition.
- the exemplary lower ends 224 are along the projection lateral surface 82 ; whereas, the exemplary upper ends 226 are along the recess 200 .
- the exemplary channels 220 are closed channels (e.g., they have a full lateral perimeter) as distinguished from purely open channels or troughs. Accordingly, the exemplary channel 220 may be formed by drilling into the cast piston. An exemplary group of channels are evenly circumferentially distributed about the piston and cylinder axis 502 . The exemplary configuration has four such channels 220 ( FIG. 3 ). A broader range is 1-10 or 2-8.
- the holes caused a TDC clearance volume increase of 5%. This would normally be expected to decrease overall performance. Nevertheless there was an observed performance increase due to the increased clearance volume's influence being outweighed by the improved flow, and reduced power. Thus, it is expected that a diminishing return on hole size flow benefit will be overcome by the increased clearance volume and cause decreased performance if the holes are too large. There may also be a lower threshold on hole size where small size does not provide overall benefit due to resistance to flow through the holes.
- Alternative individual hole cross-sectional area is at least 2.0 mm 2 or 2.0 mm 2 to 10.0 mm 2 .
- Alternative aggregate cross-sectional area is at least 5.0 mm 2 or 5.0 mm 2 to 50.0 mm 2 .
- vent 300 One or more of several advantages may be obtained by adding the vent 300 . Aspects of discharge valve responsiveness may be improved by allowing the pocket 182 to vent. For example, when the valve element 150 is driven upward from its closed position, vapor above the valve element is either driven into the pocket or squeezed laterally out through a peripheral opening 320 . To the extent that vapor is driven into the pocket, this may cause back pressure in the pocket resisting upward movement of the valve element 150 . To the extent that vapor is driven laterally outward, this may also involve back pressure but also may cause that vapor to compete with vapor displaced from the cylinder.
- the vent may allow vapor initially above the valve element 150 to be vented into the pocket and vapor in the pocket to be vented outward.
- an additional potential advantage of some embodiments involves passing of flow from the cylinder through the pocket and vent.
- the nature of spring bias may be that during some portion or all of the discharging stroke of the piston, the valve element 150 does not top out and close the lower end of the pocket 182 .
- a portion of the vapor being discharged from the cylinder may pass radially and axially around the OD perimeter 160 of the valve element 150 and then back inward and upward through the pocket 182 and vent 300 .
- channels or other passageways may be provided so that flow may pass from the cylinder through the pockets and vents even with the valve element topped out against a stop surface.
Abstract
A compressor (20) comprises: a case (22); and at least one piston (40) mounted for reciprocating movement, each in a respective cylinder (42) of the case. The at least one piston having a peripheral surface (50) and an upper surface (52), the upper surface having an outer portion (54) and a projection (80) extending from the upper surface. The at least one piston has a channel (220) positioned to pass flow from an area above the outer portion.
Description
- Benefit is claimed of U.S. Patent Application No. 62/210,108, filed Aug. 26, 2015, and entitled “Reciprocating Compressor Vented Piston”, the disclosure of which is incorporated by reference herein in its entirety as if set forth at length.
- The disclosure relates to reciprocating compressors. More particularly, the disclosure relates to pistons.
- Reciprocating compressors have long been used in applications such as refrigeration. One recent configuration involves pistons whose upper surface has a protrusion that, at top-dead-center, protrudes above the upper face of the cylinder block to help completely fill a volume within a valve plate to provide a more complete expulsion of compressed fluid.
- One aspect of the disclosure involves a compressor comprising: a case; and at least one piston mounted for reciprocating movement, each in a respective cylinder of the case. The at least one piston having a peripheral surface and an upper surface, the upper surface having an outer portion and a projection extending from the upper surface. The at least one piston has a channel positioned to pass flow from an area above the outer portion.
- In one or more embodiments of any of the foregoing embodiments, the channel is a closed channel.
- In one or more embodiments of any of the foregoing embodiments, the projection has an upper end and a central recess in the upper end and the channel has an upper end at the recess.
- In one or more embodiments of any of the foregoing embodiments, the channel has a lower end along a side of the projection.
- In one or more embodiments of any of the foregoing embodiments, the channel is one of a plurality of like channels distributed circumferentially about the at least one piston.
- In one or more embodiments of any of the foregoing embodiments, the compressor comprises: a motor; a crankshaft driven by the motor; and at least one connecting rod coupling the crankshaft to the at least one piston.
- In one or more embodiments of any of the foregoing embodiments, the projection has a frustoconical lateral surface.
- In one or more embodiments of any of the foregoing embodiments, the channel comprises a drilled hole.
- In one or more embodiments of any of the foregoing embodiments, the at least one piston comprises a plurality of identical pistons.
- In one or more embodiments of any of the foregoing embodiments: the cylinder is formed in a cylinder block; a valve plate assembly is mounted to the cylinder block; and the at least one piston has a top-dead-center condition wherein the projection is at least partially within the valve plate assembly.
- In one or more embodiments of any of the foregoing embodiments: the valve plate assembly has a seat forming a seating surface of a suction valve; and, in the top-dead-center condition, the projection is partially received within the seat.
- In one or more embodiments of any of the foregoing embodiments: the seat forms an outer seating surface of a discharge valve; the valve plate assembly has an inner seat forming an inner seating surface of the discharge valve; the at least one piston has a recess in the projection; and, in the top-dead-center condition, the inner seat is partially received within the recess.
- In one or more embodiments of any of the foregoing embodiments, a method for manufacturing the compressor comprises: drilling to form the channel.
- In one or more embodiments of any of the foregoing embodiments, a method for using the compressor comprises: reciprocating the piston in the cylinder, during an upward portion of the reciprocating a flow of fluid moving upward in the channel.
- In one or more embodiments of any of the foregoing embodiments, the flow of fluid is from a region adjacent a suction valve toward a discharge valve.
- In one or more embodiments of any of the foregoing embodiments, a vapor compression system comprises the compressor.
- In one or more embodiments of any of the foregoing embodiments, the vapor compression system is a refrigeration system.
- The details of one or more embodiments are set forth in the accompanying drawings and the description below. Other features, objects, and advantages will be apparent from the description and drawings, and from the claims.
-
FIG. 1 is a longitudinal sectional view of a compressor. -
FIG. 1A is an enlarged view of the forward-most two cylinders of the compressor ofFIG. 1 . -
FIG. 1B is an enlarged view of a portion of the forward-most cylinder of the compressor ofFIG. 1 . -
FIG. 2 is an isolated view of a piston of the compressor ofFIG. 1 . -
FIG. 3 is an exploded cutaway view of a single cylinder of the compressor. - Like reference numbers and designations in the various drawings indicate like elements.
-
FIG. 1 shows acompressor 20. The compressor has a case orhousing assembly 22 which includes an inlet orsuction port 24 and an outlet ordischarge port 26. The exemplary compressor includes amotor 28 including astator 32 and arotor 30. Therotor 30 is integrated with acrankshaft 34 to drive rotation of the crankshaft about anaxis 500. The crankshaft is supported by a plurality of bearings for rotation about theaxis 500. The compressor is a reciprocating compressor having a plurality ofpistons 40 mounted for reciprocal movement in respective associatedcylinders 42 defined within acylinder block 44 of the case. The exemplary cylinders are coupled to the crankshaft viawrist pins 46 carried by the pistons and connectingrods 48 coupling the wrist pins to the crankshaft. - Each piston has a lateral or side or outer diameter (OD) surface 50 (
FIG. 1A ) and an upper ortop surface 52.FIG. 1A shows a forward-most piston in a top-dead-center (TDC) position. In the TDC position, alateral portion 54 of theupper surface 52 is approximately flush to anupper surface 60 of thecylinder block 44. Avalve plate assembly 70 is mounted atop the surface 60 (agasket 62 intervening) and bearsvalve assemblies 72 associated with the respective cylinders. As is discussed further below, the valve assemblies 72 each comprise portions forming an inlet or suction valve and portions forming a discharge or outlet valve. Acylinder head 74 is mounted atop the valve plate assembly (agasket 75 intervening) and encloses adischarge plenum 76 in communication with thedischarge port 26. -
FIG. 1A further shows the pistons comprising an upward projection 80 (having a lateral or side or outer diameter (OD)surface 82 and an upper or distal end 84) which, in the forward-most piston illustrated top-dead-center condition or position protrudes into thevalve plate assembly 70. This helps minimize the headspace in the top-dead-center condition for improved overall flow. - The exemplary
valve plate assembly 70 comprises abottom plate 90 and atop plate 92 separated by spacers. The spacers may include aperimeter plate 94 matching the perimeter of the valve plate assembly so as to enclose aplenum 96.Additional spacers 98 may be distributed within the plenum. As is discussed further below, theplenum 96 is a suction plenum in communication with thesuction port 24. For example, with thesuction port 24 in a motor case section of the case assembly, thesuction plenum 96 may be in communication with the interior of the motor case via a passageway (not shown) cast in the case assembly. - The suction valve comprises a flexible valve element 120 (
FIG. 1B ) mounted between thevalve plate assembly 70 andcylinder block 44 at the periphery of eachcylinder 42. Thevalve element 120 is formed as a sheet having alower surface 122 and anupper surface 124. At each cylinder, the valve element has a central aperture defined by an inner perimeter (inner diameter (ID))surface 126. In a closed condition, theupper surface 124 adjacent theinner perimeter 126 is seated against a seating surface 130 (an ID seat). Theexemplary seating surface 130 is a lower surface of aseat 132 whose upper surface forms a discharge valve seating surface as is discussed further below. An inner diameter (ID)surface 134 of the seat closely accommodates theOD surface 82 of theprojection 80 in the top-dead-center condition. An OD seating surface may be formed by a portion of the underside of thebottom plate 90. - The exemplary suction valve element is generally round but has two tabs 135 (
FIG. 5 ) 180° apart that sit on the crankcase deck for support and twosmaller tabs 136 serving as stops. - The
exemplary seat 132 comprises an upper portion mounted to the upper plate 92 (e.g., via press fit, braze, or the like) and a lower portion depending through theplenum 96 and through an associatedaperture 140 in thebottom plate 90. In operation, as the piston withdraws from its top-dead-center condition, reduced pressure/suction causes thevalve element 120 to flex, bending in the middle (like a U) and supported by the twotabs 135 at the edge of the cylinder bore and stopped by cooperation oftabs 136 and complementary associated surfaces of recesses in the cylinder. This flexing downward disengages the element from the ID and OD seat surfaces to allow ingestion of refrigerant from thesuction plenum 96 into the cylinder via a port 148 (an annular perimeter portion of theaperture 140 radially outboard of the outer diameter (OD) surface of the lower portion of the seat 132). Upon bottoming and reversing of the piston, thevalve element 120 flexes back into its closed or sealing condition engaging the seating surfaces to close theport 148. - The discharge valve may similarly comprise a valve element 150 (
FIG. 1B ) which has an open condition and a closed condition. Theexemplary valve element 150 is a spring-loaded annulus having alower surface 152, anupper surface 154, an inner diameter (ID)perimeter surface 156, and an outer diameter (OD)perimeter surface 158. The exemplary seat for the valve comprises an inner diameter (ID) seat and an outer diameter (OD) seat. The outer diameter seat is formed by anupper seating surface 160 of theseat 132. - The exemplary ID seat is formed by an outer
diameter perimeter surface 164 of aninner seat member 166. Themember 166 is secured centrally to avalve guide 170 which, in turn, is mounted atop theupper plate 92. One or more springs 180 (e.g., a circumferential array of metallic coil springs held inpockets 182 in the guide (e.g., three to twenty such springs and pocket combinations per cylinder or eight to sixteen, with an exemplary twelve shown) may bias thevalve element 152 into its closed condition. - As the piston moves upward towards its top-dead-center condition, eventually pressure in the headspace will exceed pressure in the discharge plenum. At this point (or thereafter due to bias of the discharge valve) the
discharge valve element 150 will shift from its closed condition toward an open condition allowing refrigerant to pass from the headspace into the discharge plenum. When the piston reaches top-dead-center, the discharge valve will reclose. - With this exemplary configuration of discharge valve, the
piston projection 80 includes a central recess 200 (FIG. 1A ) that receives and accommodates the discharge valveinner seat member 166 as the piston approaches top-dead-center so as to minimize headspace. - As the piston approaches top-dead-center, gas in the small space above the
lateral portion 54 of theupper surface 52 is driven upward. In a baseline system, this refrigerant is driven upward between thelateral surface 82 of theprojection 80 and theadjacent ID surface 134 of theseat 132. The tightness of the space may cause flow resistance, reducing compressor efficiency. Accordingly,FIG. 1A addschannels 220 to a baseline piston configuration. The channels extend fromlower ends 224 to upper ends 226. The lower ends may generally form inlet ports (inlets) and the upper ends 226 may generally form outlet ports (outlets) for flow to pass during that final stage of upward movement of the piston to the top-dead-center condition. The exemplary lower ends 224 are along theprojection lateral surface 82; whereas, the exemplary upper ends 226 are along therecess 200. Theexemplary channels 220 are closed channels (e.g., they have a full lateral perimeter) as distinguished from purely open channels or troughs. Accordingly, theexemplary channel 220 may be formed by drilling into the cast piston. An exemplary group of channels are evenly circumferentially distributed about the piston andcylinder axis 502. The exemplary configuration has four such channels 220 (FIG. 3 ). A broader range is 1-10 or 2-8. - During a late stage of upward movement, the channel
lower end 224 will be exposed between the suction valve element above and piston upwardsurface lateral portion 52 below. Further upward movement of the piston will tend to drive some gas upward through thechannel 220 exiting the upper end/outlet 226 and passing therefrom out the discharge valve. Tests on a prototype have shown approximately 1% improvement in efficiency at the rated condition of the baseline compressor. Depending upon implementation, embodiments may be configured to provide a slight increase in capacity (or potentially a slight decrease). - Exemplary dimensions of each hole involve a diameter of 0.5 mm and cross-sectional area of 4.9 mm2. Exemplary aggregate cross-sectional area of the channels (e.g. four times the hole cross-sectional area for the exemplary piston) is 19.6 mm2.
- When compared to an otherwise similar baseline compressor lacking the holes/
channels 220, the holes caused a TDC clearance volume increase of 5%. This would normally be expected to decrease overall performance. Nevertheless there was an observed performance increase due to the increased clearance volume's influence being outweighed by the improved flow, and reduced power. Thus, it is expected that a diminishing return on hole size flow benefit will be overcome by the increased clearance volume and cause decreased performance if the holes are too large. There may also be a lower threshold on hole size where small size does not provide overall benefit due to resistance to flow through the holes. - Alternative individual hole cross-sectional area is at least 2.0 mm2 or 2.0 mm2 to 10.0 mm2. Alternative aggregate cross-sectional area is at least 5.0 mm2 or 5.0 mm2 to 50.0 mm2.
- An additional modification relative to the baseline compressor is the addition of vents 300 (
FIG. 1B ) to the spring pockets 182. In one exemplary modification, the baseline spring pocket is a blind bore extending upward from a lowerperimeter surface portion 302 of thevalve guide 170. The upper end of thebaseline spring 180 sits against the base of the blind bore. The exemplary modification adds thevent 300 as a narrower passageway such as a drilled coaxial bore of smaller diameter leaving ashoulder 304 formed by a perimeter portion of the base surface of the baseline pocket. Thevent 300 thus has alower end 310 at thepocket 182 and anupper end 312 at anupper surface 314 of thevalve guide 170. - One or more of several advantages may be obtained by adding the
vent 300. Aspects of discharge valve responsiveness may be improved by allowing thepocket 182 to vent. For example, when thevalve element 150 is driven upward from its closed position, vapor above the valve element is either driven into the pocket or squeezed laterally out through aperipheral opening 320. To the extent that vapor is driven into the pocket, this may cause back pressure in the pocket resisting upward movement of thevalve element 150. To the extent that vapor is driven laterally outward, this may also involve back pressure but also may cause that vapor to compete with vapor displaced from the cylinder. - One or both of these situations may be addressed by addition of the vent. In some embodiments, the vent may allow vapor initially above the
valve element 150 to be vented into the pocket and vapor in the pocket to be vented outward. - Yet an additional potential advantage of some embodiments involves passing of flow from the cylinder through the pocket and vent. For example, the nature of spring bias may be that during some portion or all of the discharging stroke of the piston, the
valve element 150 does not top out and close the lower end of thepocket 182. In this situation, a portion of the vapor being discharged from the cylinder may pass radially and axially around theOD perimeter 160 of thevalve element 150 and then back inward and upward through thepocket 182 and vent 300. In yet other situations, channels or other passageways may be provided so that flow may pass from the cylinder through the pockets and vents even with the valve element topped out against a stop surface. - Independently of the modifications discussed above regarding the
piston channels 220, testing on a prototype showed a capacity increase of approximately 2% at the rating condition and an EER improvement of 1%. - Various further modifications may be made to the
channels 220 or vents 300. In one example, the illustratedchannels 220 may be replaced with fully open channels along the periphery of the projection or with some form of hybrid of open channel and closed channel such as an open channel along a lower portion of the projection periphery transitioning to a closed channel penetrating into therecess 200. Another variation might involve replacing the array ofcoil springs 180 andpockets 182 with a single wave spring (e.g., in an annular space such as a downwardly-open channel). The vents could extend upward from that annular space. - The compressor is used in a vapor compression system (e.g., refrigeration system including chillers, air conditioners, heat pumps, and the like). In such a system, the compressor may drive refrigerant flow along the recirculating flowpath passing through one or more heat rejection heat exchangers and one or more heat absorption heat exchangers. The basic configuration involves a sequential flowpath passing through a heat rejection heat exchanger, an expansion device, a heat absorption heat exchanger, and returning to the compressor.
- The compressor may be made using otherwise conventional or yet-developed materials and techniques.
- The use of “first”, “second”, and the like in the description and following claims is for differentiation within the claim only and does not necessarily indicate relative or absolute importance or temporal order. Similarly, the identification in a claim of one element as “first” (or the like) does not preclude such “first” element from identifying an element that is referred to as “second” (or the like) in another claim or in the description.
- One or more embodiments have been described. Nevertheless, it will be understood that various modifications may be made. For example, when applied to an existing basic system, details of such configuration or its associated use may influence details of particular implementations. Accordingly, other embodiments are within the scope of the following claims.
Claims (17)
1. A compressor (20) comprising:
a case (22); and
at least one piston (40) mounted for reciprocating movement, each in a respective cylinder (42) of the case, the at least one piston having a peripheral surface (50) and an upper surface (52), the upper surface having an outer portion (54) and projection (80) extending from the upper surface,
wherein the at least one piston has:
a closed channel (220) positioned to pass flow from an area above the outer portion.
2. (canceled)
3. The compressor of claim 1 wherein:
the projection has an upper end and a central recess (200) in the upper end; and
the channel has an upper end (226) at the recess.
4. The compressor of claim 1 wherein:
the channel has a lower end (224) along a side of the projection.
5. The compressor of claim 1 wherein:
the channel is one of a plurality of like channels distributed circumferentially about the at least one piston.
6. The compressor of claim 1 further comprising:
a motor (28);
a crankshaft (34) driven by the motor; and
at least one connecting rod (48) coupling the crankshaft to the at least one piston.
7. The compressor of claim 1 wherein:
the projection has a frustoconical lateral surface (82).
8. The compressor of claim 1 wherein:
the channel comprises a drilled hole.
9. The compressor of claim 1 wherein:
the at least one piston comprises a plurality of identical pistons.
10. The compressor of claim 1 wherein:
the cylinder is formed in a cylinder block (44);
a valve plate assembly (70) is mounted to the cylinder block; and
the at least one piston has a top-dead-center condition wherein the projection is at least partially within the valve plate assembly.
11. The compressor of claim 10 wherein:
the valve plate assembly has a seat (132) forming a seating surface (130) of a suction valve; and
in the top-dead-center condition, the projection is partially received within the seat.
12. The compressor of claim 10 wherein:
the seat forms an outer seating surface (160) of a discharge valve;
the valve plate assembly has an inner seat (166) forming an inner seating surface (164) of the discharge valve;
the at least one piston has a recess (200) in the projection; and
in the top-dead-center condition, the inner seat is partially received within the recess.
13. A method for manufacturing the compressor of claim 1 , the method comprising:
drilling to form the channel.
14. A method for using the compressor of claim 1 , the method comprising:
reciprocating the at least one piston in the respective cylinder, during an upward portion of the reciprocating a flow of fluid moving upward in the channel.
15. The method of claim 14 wherein:
the flow of fluid is from a region adjacent a suction valve toward a discharge valve.
16. A vapor compression system comprising the compressor of claim 1 .
17. The vapor compression system of claim 16 being a refrigeration system.
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US15/752,058 US20180238312A1 (en) | 2015-08-26 | 2016-08-19 | Reciprocating Compressor Vented Piston |
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US201562210108P | 2015-08-26 | 2015-08-26 | |
PCT/US2016/047782 WO2017034983A1 (en) | 2015-08-26 | 2016-08-19 | Reciprocating compressor vented piston |
US15/752,058 US20180238312A1 (en) | 2015-08-26 | 2016-08-19 | Reciprocating Compressor Vented Piston |
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US20180238312A1 true US20180238312A1 (en) | 2018-08-23 |
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US15/752,058 Abandoned US20180238312A1 (en) | 2015-08-26 | 2016-08-19 | Reciprocating Compressor Vented Piston |
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US (1) | US20180238312A1 (en) |
EP (1) | EP3341610A1 (en) |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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RU207096U1 (en) * | 2021-05-25 | 2021-10-12 | Федеральное государственное казенное военное образовательное учреждение высшего образования "Военный учебно-научный центр Военно-воздушных сил "Военно-воздушная академия имени профессора Н.Е. Жуковского и Ю.А. Гагарина" (г. Воронеж) Министерства обороны Российской Федерации | PISTON DETANDER |
US20230048353A1 (en) * | 2021-08-12 | 2023-02-16 | Zf Cv Systems Europe Bv | Air compressor with ramped head deck |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3136477A (en) * | 1961-03-28 | 1964-06-09 | Worthington Corp | Multi-stage compressor |
JPS5810176A (en) * | 1981-07-10 | 1983-01-20 | Mitsubishi Electric Corp | Cooling medium compressor |
JP2501603Y2 (en) * | 1990-06-22 | 1996-06-19 | トヨタ自動車株式会社 | Combustion chamber structure of 2-cycle diesel engine with sub chamber |
JP3205122B2 (en) * | 1993-05-19 | 2001-09-04 | 株式会社日立製作所 | Hermetic electric compressor |
SI2300715T1 (en) * | 2008-05-01 | 2015-10-30 | Arcelik Anonim Sirketi | A compressor with improved refrigerant flow performance |
WO2014088695A1 (en) * | 2012-12-06 | 2014-06-12 | Carrier Corporation | Discharge reed valve for reciprocating refrigeration compressor |
-
2016
- 2016-08-19 EP EP16757491.2A patent/EP3341610A1/en not_active Withdrawn
- 2016-08-19 US US15/752,058 patent/US20180238312A1/en not_active Abandoned
- 2016-08-19 WO PCT/US2016/047782 patent/WO2017034983A1/en active Application Filing
- 2016-08-19 CN CN201680049509.2A patent/CN107923378A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RU207096U1 (en) * | 2021-05-25 | 2021-10-12 | Федеральное государственное казенное военное образовательное учреждение высшего образования "Военный учебно-научный центр Военно-воздушных сил "Военно-воздушная академия имени профессора Н.Е. Жуковского и Ю.А. Гагарина" (г. Воронеж) Министерства обороны Российской Федерации | PISTON DETANDER |
US20230048353A1 (en) * | 2021-08-12 | 2023-02-16 | Zf Cv Systems Europe Bv | Air compressor with ramped head deck |
Also Published As
Publication number | Publication date |
---|---|
CN107923378A (en) | 2018-04-17 |
WO2017034983A1 (en) | 2017-03-02 |
EP3341610A1 (en) | 2018-07-04 |
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