EP1469200A2 - Kolbenverdichter - Google Patents

Kolbenverdichter Download PDF

Info

Publication number
EP1469200A2
EP1469200A2 EP04251927A EP04251927A EP1469200A2 EP 1469200 A2 EP1469200 A2 EP 1469200A2 EP 04251927 A EP04251927 A EP 04251927A EP 04251927 A EP04251927 A EP 04251927A EP 1469200 A2 EP1469200 A2 EP 1469200A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
motor
compressor according
piston
stator
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.)
Withdrawn
Application number
EP04251927A
Other languages
English (en)
French (fr)
Inventor
Walter T. Grassbaugh
Randall L. Knick
Kevin J. Gehret
Frank S. Wallis
Ernest R. Bergman
Kimberly A. Wenning
Jacob A. Groshek
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Copeland LP
Original Assignee
Copeland Corp LLC
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Copeland Corp LLC filed Critical Copeland Corp LLC
Publication of EP1469200A2 publication Critical patent/EP1469200A2/de
Withdrawn legal-status Critical Current

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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
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/125—Cylinder heads
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • 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
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block
    • 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
    • F04B39/14—Provisions for readily assembling or disassembling

Definitions

  • the present invention relates to a hermetically sealed motor driven reciprocating compressor, and more particularly to a reciprocating compressor having an improved construction.
  • a hermetic reciprocating compressor includes a sealed casing including upper and lower shells, a drive motor arranged in the sealed casing for driving a piston disposed within a compression cylinder also arranged in the sealed casing.
  • the electric motor typically includes a stator, a rotor, and a crankshaft with an eccentric portion formed on one end thereof for driving the piston.
  • the compression cylinder includes a cylinder block defining a compression chamber in which a piston is reciprocally movable in a linear direction by a connecting rod disposed between the piston and the eccentric portion of the crankshaft.
  • a head portion is mounted to the cylinder block and includes valving therein for providing controlled discharge of compressed gases from the compression chamber.
  • Figure 1 is a partial cross-sectional perspective view of a reciprocating compressor according to the principles of the present invention
  • Figure 2 is a detailed partial cross-sectional exploded perspective view illustrating the piston and discharge valve assembly according to the principles of the present invention
  • Figure 3 is a detailed partial cross-sectional perspective view illustrating the assembly technique for mounting the valve plate assembly according to the principles of the present invention
  • Figure 4A is a partial cross-sectional perspective view illustrating the compressor in a vertical arrangement with the motor housing submerged in oil according to the principles of the present invention
  • Figure 4B is a partial cross-sectional perspective view of the compressor being mounted within the hermetic shell in an upside down configuration with the head of the compressor disposed in the oil sump;
  • Figure 5 is a detailed cross-sectional view illustrating the connection of the compressor body and motor cover to the motor stator according to the principles of the present invention
  • Figure 6 is a cross-sectional view illustrating the connection between the motor stator and motor cover and lower bearing housing according to the principles of the present invention
  • Figure 7 is an exploded perspective view of a snap-fit discharge tube fitting
  • Figure 8A is a cross-sectional view of a thrust bearing utilized in the compressor of Figure 4A;
  • Figure 8B is a cross-sectional view of an oil plug provided in the upper end of the crankshaft utilized in the compressor of Figure 4A;
  • Figure 9A is a cross-sectional view of a thrust bearing utilized in the compressor of Figure 4B;
  • Figure 9B is a cross-sectional view of an oil plug provided in the upper end of the crankshaft utilized in the compressor of Figure 4B;
  • Figure 10 is a detailed cross-sectional view illustrating the connection of the compressor body and motor cover to the motor stator according to alternative embodiments of the present invention.
  • Figure 11 is a detailed cross-sectional view illustrating the connection of the compressor body and motor cover to the motor stator according to further alternative embodiments of the present invention.
  • the reciprocating compressor 10 includes a sealed casing 12 including a lower shell 14 and an upper shell 16 sealingly connected to one another.
  • a suction inlet passage 17 is provided in the sealed casing 12.
  • a motor 18 is disposed within the casing 12 and includes a rotor (not shown), a stator 20, and a crankshaft 22 which is connected to the rotor, as known in the art.
  • the crankshaft 22 includes an eccentric portion 24.
  • the motor 18 includes a motor cover 25.
  • a uni-body member 26 is mounted to the motor 18.
  • the uni-body member 26 includes a body portion 28 defining a cylinder 30 and a bell-shaped housing portion 32.
  • a head portion 34 is formed as a unitary piece with the body 28 and includes a first discharge cavity 36A in communication with the cylinder 30, and a second discharge cavity 36B is in communication with the first discharge cavity 36A via a restriction 36C.
  • the size of the first and second discharge chambers 36A, 36B are preferably sized to optimize discharge pulse or efficiency. Further, the restriction 36C can be sized or provided with an insert to further optimize the discharge pulse.
  • a discharge tube 100 is connected to the outlet port 102 of the second discharge chamber 36B.
  • the discharge tube 100 has a snap-fit engagement with the outlet port 102.
  • the discharge tube 100 can be provided with a tube fitting 104 with a radially expanding retainer ring 106 which upon being pushed through the outlet port 102 expands outward, preventing the tube fitting 104 from being removed or blown out.
  • a compliant seal member 105 forms a generally gas-tight seal between outlet port 102 and tube fitting 104.
  • a muffler 108 can optionally be provided in the discharge tube passage 100.
  • the discharge tube 100 is connected to a discharge port 110 provided in the sealed casing 12.
  • a piston 38 is disposed within the cylinder 30 and is connected to a connecting rod 40 which is connected to the eccentric portion 24 of the crankshaft 22.
  • a suction passage 42 is provided in the uni-body member 26 and communicates with the cylinder 30 and a hollow section 44 defined by the bell-shaped portion 32 of the body 28.
  • the piston 38 is generally cylindrical in shape and includes a recessed groove 46 that communicates with an inlet passage 48 that allows suction gas to pass through the suction passage 42, through the groove 46, and inlet passage 48 into the cylinder 30 at the top of the piston 38 through passages 47 which are covered by a suction reed valve 49 (secured to the top of the piston) during a suction phase of the compressor operation.
  • a discharge valve assembly 50 is provided in the open end of the cylinder 30.
  • the discharge valve assembly 50 includes a valve plate 52, a discharge valve member 54, and a valve retainer 56.
  • the valve plate 52 is generally disk-shaped and includes a pair of discharge ports 58 disposed therein.
  • the valve plate 52 further includes a plurality of holes 60 for receiving fasteners therein for mounting the discharge valve 54 and retainer 56 to the valve plate 52.
  • the discharge valve 54 as shown in Figure 2, is a reed-type valve which is made from a flexible material.
  • the discharge valve 54 is disposed against a valve retainer 56 which is provided with an arcuate face 62, and also includes mounting holes 64 (only one of which is shown in Figure 1) for receiving fasteners that extend through the mounting holes 60 provided in the valve plate 52, and the holes 66 provided in the discharge valve 54.
  • the discharge valve 54 is provided with arcuate cutouts 68 which are disposed radially inward from the discharge ports 58 provided in the valve plate 52 and help to control the flexibility of the discharge valve 54 to cover the discharge ports 58 during a suction phase of compressor operation and to flex away from the discharge ports 58 during a compression stage of compressor operation.
  • the arcuate face 62 of the valve retainer 56 has a profile configured to limit the opening of the reed valve 54 for stress and performance optimization.
  • the discharge valve assembly 50 can be assembled in the head portion 34 of the uni-body member 26 by forming the valve plate 52 and retainer 56 to have a diameter appropriately machined and toleranced to allow an interference fit between the outside diameter of the valve plate 52 and retainer 56 and the inside diameter of the cylinder 30.
  • the interference fit at the diameter provide sealing and retention of the valve plate 52 and retainer 56.
  • the piston 38 is held at a predetermined position such as, for example, top dead center and the discharge valve assembly 50 is chilled to a temperature low enough to thermally shrink the diameter of the assembly 50 so that it will freely drop into the cylinder 30.
  • the discharge valve assembly 50 rests on the piston 38 until it warms and grows into a press-fit in cylinder 30.
  • the press-fit retains the assembly 50 and provides a sealing between the cylinder 30 and the discharge valve assembly 50 diameter.
  • one method of positioning the piston 38 within the cylinder 30 during assembly of the discharge valve assembly 50 is to reverse-load the bearings (by application of force F) between the connecting rod 40 and crankshaft 22, relying on the bearing clearances to position the piston 38 slightly above the normal top dead center position. Gas forces (when the compressor is running) push down on the piston 38, reversing the loading on the bearing and creating a cold piston-to-valve plate clearance approximately equal to the sum of the bearing clearances in the running gear assembly.
  • the interference fit at assembly can be obtained by heating the cylinder in order to cause the cylinder inner diameter to expand prior to inserting the discharge valve assembly into the cylinder, as opposed to cooling the valve assembly, and leaving the cylinder at room temperature.
  • a combination of the two is also possible.
  • the sealing and retention between the valve plate 52 and cylinder 30 can also be enhanced by use of a sealing agent, such as, for example, LOCTITE.
  • valve plate to set in a counterbore of different diameter than that of the cylinder.
  • this option would require that a secondary machine operation be provided in order to generate the counterbore.
  • the top of the piston 38 is provided with contoured posts 70 which are designed to partially fill the discharge ports 58 in the valve plate 52 when the piston 38 is nearing top dead center.
  • the contoured posts 70 further reduce the amount of clearance between the piston 38 at top dead center and the valve plate 52 to further increase the efficiency of the compressor.
  • the uni-body member 26 includes a bearing portion 72 that receives an end of the crankshaft 22 therein:
  • the uni-body member 26 further includes an opening 74 provided in the bell-shaped portion 32 that is spaced from the bearing portion 72 and receives the crankshaft 22 therein.
  • a crank case isolation seal 76 is disposed between the opening 74 and the crankshaft 22 in order to provide for a large suction volume within the hollow section 44 to attenuate suction pulse.
  • the suction gas that enters through the suction inlet passage 17 is drawn into the motor cover 25 over top of an upper edge thereof and between the interior of the motor cover 25 and the outer surface of the stator 20.
  • the suction gas then passes upward between the rotor and stator 20 and into the space between the hollow section 44 of the bell-shaped portion 32 of the body 28 and the stator 20.
  • the free volume between the motor 18 and bell-shaped portion 32 is available to serve as a suction muffler.
  • the seal prevents oil from the upper main and connecting rod bearings from flowing down past the crankshaft and becoming entrained in the suction gas.
  • the above-described suction gas flow passage also prevents oil from becoming entrained in the suction gas.
  • the sealed casing 12 is sized and configured to be capable of supporting the motor 18 and uni-body member 26 for two different types of applications.
  • Oil temperature control is important in most hermetic compressors. If the oil is too hot, lubricating properties diminish and oil breakdown may occur. If the oil is too cool, refrigerant dilution may significantly impact lubricating properties of the oil, and otherwise negatively impact the reliability of the compressor.
  • the oil sump temperature is highly dependent on how the compressor is being applied. In those applications with high super heat and high pressure ratios, rejecting a minimal amount of heat to the oil can help keep it in a safe temperature zone. This can be accomplished by keeping the head of the compressor out of the oil. Applications with low super heat and low pressure ratios can benefit from heat rejection to the oil. This heat rejection to the oil can be enhanced by submerging the head and running gear in the oil.
  • the present invention provides that the sealed casing 12 be sized and configured to receive the motor 18 and uni-body member 26 with either the motor being disposed in the compressor sump, as illustrated in Figure 4A, or the uni-body member 26 being disposed in the compressor sump, as illustrated in Figure 4B.
  • the modifications required to do this consist in utilizing a crankshaft thrust bearing with an oil pump inlet at the end of the crankshaft that is submerged within the oil sump.
  • a cross-sectional view of the crankshaft thrust bearing 120 is shown for the compressor shown in Figure 4A.
  • the thrust bearing 120 includes a thrust washer 122 disposed between the end of the crankshaft 22 and a lower bearing housing 92.
  • a bearing 123 is provided between the crankshaft 22 and the lower bearing housing 92.
  • Figure 8B illustrates an oil plug 124 provided in the upper end of the crankshaft 22 of the embodiment of Figure 4A.
  • the plug 124 has a vent passage 126 to allow gases to vent while preventing oil from spewing out the upper end of the crankshaft 22 to control the oil circulation rate.
  • Figure 9A illustrates a cross-sectional view of a crankshaft thrust bearing 130 for the compressor shown in Figure 4B.
  • the thrust bearing 130 includes a thrust washer 132 disposed between the lower end of the crankshaft and a retainer ring 134 attached to the body 28.
  • Figure 9B illustrates an oil plug 136 provided in the upper end of crankshaft 22 of the embodiment of Figure 4B.
  • the plug 136 has a vent passage 138 to allow gases to vent while preventing oil from spewing out of the upper end of the crankshaft 22 to control the oil circulation rate.
  • many of the same components of the compressor design including the housing, motor, and uni-body member can be utilized in a compressor that is being utilized for either high or low super heat and pressure ratios.
  • the outside diameter of the stator 20 is press-fit in a counterbore inside diameter of the bell-shaped section 32 of the uni-body member 26.
  • the stator 20 is a structural member carrying bearing loads and suspension system loads.
  • an alternative embodiment relies on an epoxy filled gap in the counterbore of the bell-shaped section 32 to allow positioning of the stator 20.
  • the stator may be held in place with tack welds while the epoxy cures.
  • Another alternative embodiment, as illustrated in Figure 10 utilizes bolts 150 that extend through the housing 25, stator 20, and threadedly engage the bell-shaped section 32, stator 20 to position the stator, clamping it against the face of the bell-shaped section 32.
  • the bell-shaped section 32 can be connected by welds 151 to the stator 20.
  • Motor 18 includes a motor cover 25 which can be press-fit over the stator 20, as shown in Figure 1.
  • the motor cover can be provided with indents 25A (such as illustrated in Figure 6) that engage the stator and define air gaps between the motor cover 25 and the stator 20 to allow the flow of suction gas therebetween.
  • An alternative embodiment is to plug-weld the motor housing cover 25 to the stator 20. Plug welding may be used in conjunction with press-fitting or to position a housing with an epoxy filled gap 86, as best shown in Figure 5. Air gap shims are utilized during curing, and later removed to define air gaps for the suction gas.
  • motor cover 25 can be fastened to the stator by bolts 150, as illustrated in Figure 10, or connected by welds 152 as illustrated in Figure 11.
  • a further alternative embodiment is to use a two-part motor cover housing, including a motor cover 90 and lower bearing housing 92, as illustrated in Figure 6.
  • the motor cover 90 is press-fit, adhered, bolted, and/or welded to the stator 20, as discussed above.
  • the lower bearing housing 92 is moved laterally to position the lower bearing relative to the lower end of the crankshaft 22 and the lower bearing housing 92 is then plug welded to the motor cover housing 90.
  • the separate connection of the lower bearing housing 92 allows for proper location of the crankshaft 22 and rotor relative to the stator 20 to provide a proper air gap between the rotor and stator 20 for efficient motor operation.
  • crankshaft 22 which is provided with an internal lubricant passage 140, as is known in the art.
  • the crankshaft 22 is provided with radial passages 142, 144 for providing lubrication to an internal passage in connecting rod 40 and to the upper crankshaft bearing.
  • the cylinder 30 is splash lubricated with lubrication from the connecting rod 40.
EP04251927A 2003-04-14 2004-03-31 Kolbenverdichter Withdrawn EP1469200A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US413454 2003-04-14
US10/413,454 US20040202562A1 (en) 2003-04-14 2003-04-14 Reciprocating compressor

Publications (1)

Publication Number Publication Date
EP1469200A2 true EP1469200A2 (de) 2004-10-20

Family

ID=32908300

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04251927A Withdrawn EP1469200A2 (de) 2003-04-14 2004-03-31 Kolbenverdichter

Country Status (10)

Country Link
US (1) US20040202562A1 (de)
EP (1) EP1469200A2 (de)
JP (1) JP2004316647A (de)
KR (1) KR20040089486A (de)
CN (2) CN101067411A (de)
AU (1) AU2004201057A1 (de)
BR (1) BRPI0401105A (de)
CA (1) CA2464509A1 (de)
MX (1) MXPA04003363A (de)
TW (1) TWI234609B (de)

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WO2006056603A1 (de) * 2004-11-25 2006-06-01 Acc Austria Gmbh Kleinkältemittelkompressor
EP2031247A1 (de) * 2007-08-31 2009-03-04 Pfizer Inc. Flüssigkeitspumpe
WO2010138510A2 (en) 2009-05-28 2010-12-02 Carrier Corporation Light weight crankcase casting for compressor
DE102019127746A1 (de) * 2019-10-15 2021-04-15 Hanon Systems Vorrichtungen zum Verdichten eines dampfförmigen Fluids und Verfahren zum Betreiben einer Vorrichtung

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WO2006056603A1 (de) * 2004-11-25 2006-06-01 Acc Austria Gmbh Kleinkältemittelkompressor
CN100572808C (zh) * 2004-11-25 2009-12-23 Acc奥地利有限公司 用于气密密封式小型制冷机的压缩机
EP2031247A1 (de) * 2007-08-31 2009-03-04 Pfizer Inc. Flüssigkeitspumpe
WO2009027809A2 (en) * 2007-08-31 2009-03-05 Pfizer Inc. Liquid pump
WO2009027809A3 (en) * 2007-08-31 2009-09-24 Pfizer Inc. Liquid pump
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WO2010138510A2 (en) 2009-05-28 2010-12-02 Carrier Corporation Light weight crankcase casting for compressor
EP2435702A4 (de) * 2009-05-28 2015-07-29 Carrier Corp Giessung eines leichtgewichtigen kurbelgehäuses für einen kompressor
DE102019127746A1 (de) * 2019-10-15 2021-04-15 Hanon Systems Vorrichtungen zum Verdichten eines dampfförmigen Fluids und Verfahren zum Betreiben einer Vorrichtung
DE102019127746B4 (de) 2019-10-15 2021-07-29 Hanon Systems Vorrichtungen zum Verdichten eines dampfförmigen Fluids und Verfahren zum Betreiben einer Vorrichtung

Also Published As

Publication number Publication date
JP2004316647A (ja) 2004-11-11
MXPA04003363A (es) 2004-10-19
CN101067411A (zh) 2007-11-07
AU2004201057A1 (en) 2004-10-28
KR20040089486A (ko) 2004-10-21
CN1538064A (zh) 2004-10-20
TWI234609B (en) 2005-06-21
US20040202562A1 (en) 2004-10-14
BRPI0401105A (pt) 2005-01-11
CA2464509A1 (en) 2004-10-14
TW200506209A (en) 2005-02-16

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