US20170082096A1 - Reciprocating Refrigeration Compressor and Method for Mounting a Reciprocating Refrigeration Compressor - Google Patents

Reciprocating Refrigeration Compressor and Method for Mounting a Reciprocating Refrigeration Compressor Download PDF

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Publication number
US20170082096A1
US20170082096A1 US15/126,617 US201515126617A US2017082096A1 US 20170082096 A1 US20170082096 A1 US 20170082096A1 US 201515126617 A US201515126617 A US 201515126617A US 2017082096 A1 US2017082096 A1 US 2017082096A1
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US
United States
Prior art keywords
crankshaft
rotor
piston
dead point
upper dead
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US15/126,617
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English (en)
Inventor
Marcio Roberto Thiessen
Diogo Londero da SILVA
Flavio Jorge Haddad KALLUF
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.)
Whirlpool SA
Original Assignee
Whirlpool SA
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 Whirlpool SA filed Critical Whirlpool SA
Publication of US20170082096A1 publication Critical patent/US20170082096A1/en
Assigned to WHIRLPOOL S. A. reassignment WHIRLPOOL S. A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DA SILVA, DIOGO LONDERO, KALLUF, Flavio Jorge haddad, THIESSEN, MARCIO ROBERTO
Abandoned 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04B39/0022—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 piston rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1066—Valve plates
    • 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

Definitions

  • the present invention refers to a compressor of the type provided with a piston which is driven, in a reciprocating linear movement in the interior of a cylinder, by a connecting rod coupled to the eccentric of a crankshaft affixed to the rotor of an electric motor, the electro-mechanical assembly of the compressor, including the crankshaft, the electric motor, the connecting rod and the piston, being constructed and mounted in order to avoid the stop of the piston in the upper dead point or vicinities thereof, when the electric motor turns off to stop the compressor.
  • the compression chamber is defined in the interior of the cylinder, between the top of the piston and a valve plate, containing the suction and discharge valves and which is affixed to the crankcase of the compressor, closing one of the ends of the cylinder.
  • the stop of the piston in the upper dead point, or its vicinities reduces de sealing capacity of the discharge valve(s), significantly increasing the return of the refrigerant fluid, from the condenser of the refrigeration system to the compressor region maintained under low pressure.
  • the chart represented in FIG. 1 of the appended drawings shows the pressure reduction in the discharge region of the compressor, as a function of the position of the eccentric of the crankshaft, after the motor turns off to stop the compressor.
  • the position of 180° represents the upper dead point of the piston, whereas the positions 0° and 360° represent the lower dead point.
  • the pressure drop rate which represents the leak through the discharge valve(s) is at least five times greater in the situations in which the compressor stops with the piston in the upper dead point) (180° or vicinities thereof.
  • the refrigerant fluid flows through the radial gap existing between the cylinder 11 and the piston 20 until the region of the compressor and refrigeration system, which are under low pressure.
  • the leaks through the discharge valve(s) 40 a after the stop of the compressor, reduce the energy saving obtained by using check valves installed between the condenser and the expanding device and whose function is to avoid a new compression of the refrigerant fluid already stored, at high pressure, in the condenser of the refrigeration system.
  • the present invention has the object to provide a reciprocating refrigeration compressor, which is constructed in order to avoid, upon the stop of the electric motor of the compressor, the piston from remaining in the upper dead point or in positions close to the latter, in which the pressure differential between the downstream side and the upstream side of the discharge valve(s) is not sufficient to guarantee the tight closing of said valve(s).
  • a reciprocating refrigeration compressor of the type which comprises: a crankcase carrying a cylinder and a bearing hub which lodges a crankshaft provided with an eccentric; a valve plate closing one end of the cylinder; a piston reciprocating in the interior of the cylinder and driven by a connecting rod coupled to the eccentric of the crankshaft; an electric motor having a stator affixed to the crankcase and provided with a plurality of winding grooves intercalated with teeth, each tooth carrying a shoe adjacent to the air gap of the stator, and a rotor affixed to the crankshaft and carrying magnet segments, which are circumferential and peripheral.
  • the stator, the rotor and the crankshaft present, in relation to one another, a relative positioning which produces, upon stop of the electric motor and with the assembly defined by the crankshaft and rotor being in the piston upper dead point position, a cogging torque capable of taking the piston away from the upper dead point, guaranteeing the sealing of the discharge valves.
  • the cogging torque is defined as the torque resulting from the variation of the reluctance to the passage of the useful magnetic flow, generated by the magnet, between at least one magnet segment of the rotor and a confronting stator tooth.
  • the invention further provides a method for mounting the compressor cited above, according to which the rotor is affixed to the crankshaft, which is already housed in the bearing hub and which is retained with its eccentric in a position corresponding to the piston upper dead point position and in which a cogging torque is generated capable of taking the piston away from the upper dead point.
  • the present proposed construction does not require any relevant constructive alteration to be made in the compressor.
  • a stop of the electric motor of the compressor occurs in a position of the rotor-crankshaft assembly in the piston upper dead point condition
  • at least one of the magnet segments of the rotor will produce, with a confronting stator tooth, a cogging torque capable of taking the piston away from the upper dead point and its vicinities, after the stop of the motor, creating an unstable balance position, allowing the magnetic flows circulating through the air gap to force the rotor and the crankshaft to jointly rotate to a position of minimum reluctance to the passage of the magnetic flow, stabilizing the rotor-crankshaft assembly in a position in which the piston is displaced away from its upper dead point, by a distance capable of producing a pressure differential between the interior of the compression chamber of the cylinder and the downstream side of the discharge valve(s), sufficient to guarantee the closing of the discharge valve(s).
  • the solution proposed by the invention transforms the usual stop system of the electric motor of the compressor, in which the piston has aleatory positions in the interior of the cylinder, in a controlled system through which, upon occurring a stop of the motor with the piston in the upper dead point position or close to said position, the rotor-crankshaft assembly will be magnetically turned to the stable balance position, taking the piston away from the upper dead point.
  • FIG. 1 represents a chart illustrating the pressure reduction in the discharge region of the compressor, as a function of the piston stop angle upon the stop of the electric motor of the compressor;
  • FIG. 2 illustrates, schematically, the excessive gas leak condition through the discharge valve upon the stop of the electric motor of the compressor with the piston in the upper dead point position
  • FIG. 3 represents a schematic plan view of the assembly formed by the stator, rotor, crankshaft, connecting-rod and piston in the upper dead point position, in which the rotor has a pair of magnet segments defining, with the respective teeth and shoes of the stator, a condition in which the cogging torque is capable of taking the piston away from the upper dead point and vicinities thereof;
  • FIG. 4 represents a view similar to that of FIG. 3 , but illustrating the piston away from its upper dead point position, with the crankshaft being additionally turned clockwise from the upper dead point position of the piston, with the magnet segments of the rotor defining, with the respective teeth and shoes of the stator, a stable condition, that is, of minimum reluctance to the passage of the useful magnetic flow formed between said magnet segments and the respective teeth and shoes of the stator; and
  • FIG. 5 represents a view similar to that of FIG. 4 , but illustrating the piston away from its upper dead point position with the crankshaft being additionally turned anti-clockwise from the upper dead point position of the piston, with the magnet segments of the rotor defining, with the respective teeth and shoes of the stator, a stable condition, that is, of minimum reluctance to the passage of the useful magnetic flow formed between said magnet segments and the respective teeth and shoes of the stator.
  • the present invention is applied to a refrigeration compressor, more specifically a reciprocating compressor, hermetic or not, of the type described above and which presents, in the interior of a shell (not illustrated), a crankcase B, usually formed in cast iron and presenting a usually flat outer face F.
  • a refrigeration compressor more specifically a reciprocating compressor, hermetic or not, of the type described above and which presents, in the interior of a shell (not illustrated), a crankcase B, usually formed in cast iron and presenting a usually flat outer face F.
  • the crankcase B carries at least one piston hub 10 which defines a cylinder 11 , having one end open to the outer face F of the crankcase and in whose interior is housed and displaced, in a reciprocating linear movement, a piston 20 .
  • the cylinder 11 has said end closed by a valve plate 40 and by a cylinder cover 41 , which are seated and affixed, usually by screws (not illustrated), against the outer face F of the crankcase B, as illustrated in FIG. 2 .
  • the valve plate 40 carries at least one discharge valve 40 a and one suction valve, not illustrated, said valves being of the blade type and presenting any construction adequate to the operation by pressure differential between its upstream and downstream sides, in order to establish a selective fluid communication between a compression chamber C, defined in the interior of the cylinder 11 between the piston 20 and the valve plate 40 and the suction and discharge sides of the compressor.
  • the crankcase B further carries a bearing hub 50 which houses a crankshaft 60 provided with an eccentric 61 in which is coupled one end of a connecting rod 62 whose opposite end is coupled to the piston 20 , in order to displace the latter in a reciprocating movement in the interior of the cylinder 11 , between upper dead point and lower dead point positions, by applying rotation to the crankshaft 40 .
  • the compressor is driven by an electric motor M having a stator 70 affixed to the crankcase B and provided with a plurality of winding grooves 71 intercalated with teeth 72 which carry, each one, respective shoe 72 a , and a rotor 80 , affixed to the crankshaft 60 and carrying magnet segments 81 , which are disposed substantially in a peripheral circumferential alignment.
  • one of the ways for mounting the electro-mechanical assembly of the compressor is accomplished by affixing the stator 70 , in a determined designed position, in the crankcase B of the compressor. After the position of the stator 70 is defined in relation to the crankcase B and, consequently, to the cylinder 11 which is defined in the piston hub 10 , the crankshaft 60 is mounted in the bearing hub 50 of the crankcase B and rotatively positioned in the upper dead point of the piston 20 .
  • the rotor 80 of the electric motor M may be affixed to a corresponding extension of the crankshaft 60 , in a relative angular positioning, which allows, when the eccentric 61 of the crankshaft 60 is in the upper dead point position of the piston 20 , generating a cogging torque capable of taking the piston away from the upper dead point and from vicinities thereof.
  • the proposed solution provides the fixation of the rotor 80 to the crankshaft 60 in a relative position in which the symmetry radial axis of at least one magnet segment 81 coincides with the symmetry radial axis of a corresponding winding groove 71 , with said symmetry radial axes being positioned between the two teeth 72 adjacent to said winding groove 71 .
  • the indexation for fixation of the crankshaft 60 in the rotor 80 and the fixation of the stator 70 in the crankcase B, with the indexation of at least one stator groove 71 , in relation to the rotational position of the assembly of crankshaft 60 and rotor 80 , corresponding to the upper dead point position of the piston 20 allows that, in this position of the piston 20 , the magnetic forces (not illustrated), which are present in the rotor-stator assembly, are used to prevent the piston from remaining, in a stationary condition, in the upper dead point position, if said position of the piston occurs upon a stop of the electric motor of the compressor.
  • the angular distance between each two consecutive positions of magnetic instability of the rotor 80 will correspond to the ratio of 360° for half the product of the number of magnet segments 81 by the number of stator grooves 71 .
  • the rotor has four magnet segments 81 (four poles) and the stator 70 has six stator grooves 71 .
  • the motor M presents 12 magnetic instability positions (unstable nature) and 12 magnetic stability positions (stable nature) of the rotor 80 , which positions are intercalated between one in relation to the other, each two consecutive positions, of the same nature, being angularly spaced from each other by an angle of 30° and also spaced from the adjacent or consecutive positions of other nature, by an angle of 15°.
  • the rotor 80 whenever the rotor 80 stops in a condition of unstable magnetic balance in relation to a diametrically opposite pair of magnet segments 81 , it will be magnetically forced to rotate in one or in the other sense, towards a stable magnetic balance condition generated by the magnetic field (not illustrated), by an angle which will depend on the number of poles of the rotor 80 and of the stator grooves 71 . In the illustrated example, the angle will be of at least 7.5 degrees in any of the senses. In a rotor of six poles, operating with a stator of nine grooves, said angle of additional magnetic displacement will be of at least 5 degrees.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
US15/126,617 2014-03-19 2015-03-16 Reciprocating Refrigeration Compressor and Method for Mounting a Reciprocating Refrigeration Compressor Abandoned US20170082096A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
BRBR1020140065474 2014-03-19
BR102014006547-4A BR102014006547B1 (pt) 2014-03-19 2014-03-19 Compressor alternativo de refrigeração e método de montagem de um compressor alternativo de refrigeração
PCT/BR2015/050029 WO2015139105A2 (en) 2014-03-19 2015-03-16 Reciprocating refrigeration compressor and method for mounting a reciprocating refrigeration compressor

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US20170082096A1 true US20170082096A1 (en) 2017-03-23

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US15/126,617 Abandoned US20170082096A1 (en) 2014-03-19 2015-03-16 Reciprocating Refrigeration Compressor and Method for Mounting a Reciprocating Refrigeration Compressor

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US (1) US20170082096A1 (pt)
EP (1) EP3126673B1 (pt)
CN (1) CN106662088B (pt)
BR (1) BR102014006547B1 (pt)
ES (1) ES2923866T3 (pt)
WO (1) WO2015139105A2 (pt)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3091339B1 (fr) * 2018-12-28 2021-01-01 Thales Sa Dispositif de refroidissement à cycle Stirling avec moteur à rotor externe
WO2021100279A1 (ja) * 2019-11-22 2021-05-27 パナソニックＩｐマネジメント株式会社 モータ駆動装置及びこれを用いた冷蔵庫

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5038065A (en) * 1988-05-13 1991-08-06 Hitachi, Ltd. Permanent magnet reversible synchronous motor
US20120060547A1 (en) * 2010-09-10 2012-03-15 Mitsubishi Electric Corporation Motor for compressor, compressor and refrigeration cycle apparatus
WO2012091339A2 (en) * 2010-12-29 2012-07-05 Lg Electronics Inc. Motor for compressor and compressor having the same

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3961868A (en) * 1974-02-21 1976-06-08 Thomas Industries, Inc. Air compressor
JP3571686B2 (ja) * 2000-12-27 2004-09-29 エルジー電子株式会社 往復揺動式モーター及び該往復揺動式モーターを利用したガス圧縮装置
JP2004353521A (ja) * 2003-05-28 2004-12-16 Matsushita Electric Ind Co Ltd 密閉型圧縮機
DE102004024562A1 (de) * 2004-05-18 2005-12-15 Pfeiffer Vacuum Gmbh Trocken laufende Kolbenvakuumpumpe
JP2006144731A (ja) * 2004-11-24 2006-06-08 Matsushita Electric Ind Co Ltd 圧縮機
TWI348258B (en) * 2006-11-10 2011-09-01 Ind Tech Res Inst A motor mechanism of dc frequency conversion of compressor
KR101403831B1 (ko) * 2010-09-20 2014-06-03 한라비스테온공조 주식회사 차량용 전동 압축기

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5038065A (en) * 1988-05-13 1991-08-06 Hitachi, Ltd. Permanent magnet reversible synchronous motor
US20120060547A1 (en) * 2010-09-10 2012-03-15 Mitsubishi Electric Corporation Motor for compressor, compressor and refrigeration cycle apparatus
WO2012091339A2 (en) * 2010-12-29 2012-07-05 Lg Electronics Inc. Motor for compressor and compressor having the same

Also Published As

Publication number Publication date
CN106662088A (zh) 2017-05-10
BR102014006547B1 (pt) 2022-10-11
ES2923866T3 (es) 2022-10-03
WO2015139105A3 (en) 2016-01-14
BR102014006547A2 (pt) 2015-12-01
EP3126673B1 (en) 2022-05-04
CN106662088B (zh) 2019-04-16
WO2015139105A2 (en) 2015-09-24
EP3126673A2 (en) 2017-02-08
BR102014006547A8 (pt) 2021-08-17

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Owner name: WHIRLPOOL S. A., BRAZIL

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:THIESSEN, MARCIO ROBERTO;DA SILVA, DIOGO LONDERO;KALLUF, FLAVIO JORGE HADDAD;REEL/FRAME:047033/0048

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