WO2020204826A1 - Vilebrequin pour compresseur hermétique et compresseur hermétique - Google Patents

Vilebrequin pour compresseur hermétique et compresseur hermétique Download PDF

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Publication number
WO2020204826A1
WO2020204826A1 PCT/SG2020/050190 SG2020050190W WO2020204826A1 WO 2020204826 A1 WO2020204826 A1 WO 2020204826A1 SG 2020050190 W SG2020050190 W SG 2020050190W WO 2020204826 A1 WO2020204826 A1 WO 2020204826A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft portion
counterweight
eccentric shaft
coupled
hermetic compressor
Prior art date
Application number
PCT/SG2020/050190
Other languages
English (en)
Inventor
San Haw CHONG
Kevin Kai Wei TEO
Original Assignee
Panasonic Appliances Refrigeration Devices Singapore
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 Panasonic Appliances Refrigeration Devices Singapore filed Critical Panasonic Appliances Refrigeration Devices Singapore
Priority to JP2021560192A priority Critical patent/JP2022528559A/ja
Publication of WO2020204826A1 publication Critical patent/WO2020204826A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/28—Counterweights, i.e. additional weights counterbalancing inertia forces induced by the reciprocating movement of masses in the system, e.g. of pistons attached to an engine crankshaft; Attaching or mounting same
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/32—Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels
    • F16F15/322—Correcting- or balancing-weights or equivalent means for balancing rotating bodies, e.g. vehicle wheels the rotating body being a shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers

Definitions

  • the present disclosure relates to hermetic compressors and in particular to the provision of a counterweight on a crankshaft of a hermetic compressor.
  • Hermetic compressors typically include a crankshaft having an eccentric portion coupled to a compression mechanism including a piston which is driven when the crankshaft rotates.
  • the piston is arranged in a cylinder and is coupled to the eccentric portion of the crankshaft by a connecting rod.
  • the counterweights are often attached to the eccentric shaft itself; however this can result in the length of the crankshaft having to be increased.
  • the height of an upper housing of the hermetic compressor having to be located in a higher position to avoid collisions with the counterweight.
  • a crankshaft for a hermetic compressor comprises: a main shaft portion; a flange portion coupled on an end of the main shaft portion; an eccentric shaft portion coupled to the flange portion, the eccentric shaft portion having a main axis parallel to and offset from the rotational axis of the main shaft portion; an arm portion extending from an end of the eccentric shaft portion distal to the flange portion, the arm portion having a part coupled to the end of eccentric shaft portion distal to the flange portion, an angled part angled away from the flange portion and a counterweight supporting part which is parallel to the part coupled to the end of the eccentric shaft; and a counterweight coupled to the counterweight supporting part of the arm portion.
  • the arm portion has a part that is angled away from the flange portion, the length of the eccentric shaft portion can be reduced while still ensuring that the counterweight is above the piston of a hermetic compressor when the piston is in a bottom dead center position. Since the length of the eccentric shaft portion is reduced, the mass of the eccentric shaft portion can also be reduced. This reduces the required mass for the counterweight. Which in turn facilitates a thinner counter weight a hermetic compressor with reduced height to be realized.
  • a surface of the counterweight closest to the flange portion is further from the flange portion in an axial direction of the main shaft portion than the end of the eccentric shaft portion distal to the flange portion.
  • the bottom of the counterweight is above the top of the eccentric shaft portion.
  • the arm portion has two bends, a first bend between the part coupled to the end of eccentric shaft portion distal to the flange portion and the angled part, and a second bend between the angled part and the counterweight supporting part.
  • a hermetic compressor comprising an electromotive element; a compressive element; and a crankshaft according to the present disclosure configured to convert rotational motion from the electromotive element into reciprocating motion in the compressive element.
  • the compressive element comprises a piston configured to reciprocate in a cylinder, the piston being coupled to the eccentric shaft portion by a connecting rod and wherein, when the piston is in a bottom dead center position, the counterweight overlaps with and is located above the piston.
  • the hermetic compressor further comprises a hermetic container and a damping member coupled to the hermetic container, wherein the damping member is coupled to the hermetic container in a position above the counterweight.
  • FIG.1 is a sectional view of a hermetic compressor according to an embodiment of the present invention
  • FIG.2 is a sectional view of an example hermetic compressor with reference to which advantages of embodiments of the present invention will are described;
  • FIG.3A is a sectional view of the compressive element of the hermetic compressor shown in FIG.2 in a top dead center position;
  • FIG.3B is a sectional view of the compressive element of the hermetic compressor shown in FIG.2 in a bottom dead center position;
  • FIG.4A is a sectional view showing the forces acting on the compressive element of the hermetic compressor shown in FIG.2 near the top dead center position
  • FIG.4B is a sectional view showing the forces acting on the compressive element of the hermetic compressor shown in FIG.2 near the bottom dead center position;
  • FIG.5A is a sectional view of the compressive element of the hermetic compressor shown in FIG.1 in a top dead center position;
  • FIG.5B is a sectional view of the compressive element of the hermetic compressor shown in FIG.1 in a bottom dead center position
  • FIG.6 is a sectional view of a hermetic compressor according to an embodiment having an arm portion with bends of approximately 15 degrees;
  • FIG.7 is a sectional view of a hermetic compressor according to an embodiment having an arm portion with bends of approximately 90 degrees;
  • FIG.8 is a sectional view of a hermetic compressor according to an embodiment having an arm portion with bends of approximately 135 degrees; and FIG.9 is a sectional view of a hermetic compressor according to an embodiment having an arm portion with bends of approximately 180 degrees.
  • FIG.1 is a sectional view of a hermetic compressor according to an embodiment of the present invention.
  • the hermetic compressor 100 is housed within a hermetic container which is formed from an upper container portion 101 and a lower container portion 102.
  • the hermetic compressor 100 comprises an electromotive element 110 and a compression element 120.
  • the electromotive element 110 and the compression element 120 are both hermetically sealed inside the hermetic container formed form the upper container portion 101 and the lower container portion 102.
  • the electromotive element 110 comprises a stator 111 and a rotor 112.
  • the stator 111 and the rotor 112 are arranged coaxially and the rotor 112 is arranged within the stator 111.
  • the electromotive element 110 electrically coupled to an electrical connection 113 located on the lower container portion 102.
  • the compressive element 120 is arranged above the electromotive element 110.
  • the compressive element 120 comprises a cylinder block 121.
  • the cylinder block 121 has a cylindrical cavity that forms a compression chamber 123.
  • a piston 122 is movable within the cylindrical cavity.
  • the piston 122 is coupled to a connecting rod 124.
  • the connecting rod 124 is coupled to a crankshaft 130.
  • the crankshaft 130 comprises a main shaft portion 131 , a flange portion 135 and an eccentric shaft portion 136.
  • the main shaft portion 131 is attached to the rotor 112 of the electromotive element 110.
  • the main shaft portion 131 has an oil feed mechanism 132 on a lower end.
  • the oil feed mechanism 132 is immersed or partially immersed in lubricant oil 103 which is contained in the bottom of the lower container portion 102.
  • the oil feed mechanism 132 is coupled to an oil passage 133 which runs up the main shaft portion 131.
  • the main shaft portion 131 is connected to the flange portion 135.
  • the flange portion 135 is supported by a bearing formed in the cylinder block 121.
  • the eccentric shaft portion 136 is connected to the flange portion 135 such that the axis of the eccentric shaft portion 136 is offset from the axis of the main shaft portion 131.
  • the connecting rod 124 is coupled to the eccentric shaft portion 136.
  • a counterweight 138 is coupled to the top end of the eccentric shaft portion 136 by an arm portion 137.
  • the arm portion 137 includes two bends.
  • the part of the arm portion 137 that is attached to the top of the eccentric shaft portion 136 is parallel to the flange portion 135 and runs in a horizontal direction.
  • the arm portion 137 then has an upward bend to an angle approximately 60 degrees from horizontal. There is then a second bend back to the horizontal direction.
  • the counterweight 138 is attached to the second end portion of the arm portion 137.
  • a cylinder head 150 is attached to the cylinder block 121.
  • the cylinder head 150 holds a valve plate 151 in place.
  • the valve plate 151 forms an end surface of the compression chamber 123.
  • the valve plate 151 has a suction port 152 and a discharge port 153.
  • Each of the suction port 152 and the discharge port 153 have reed valves.
  • the reed valve of the suction port 152 is configured to allow a refrigerant to be drawn into the compression chamber 123 and to close when the compression chamber 123 is compressed by the piston 122.
  • the reed valve of the discharge port 153 is configured to open when the compression chamber 123 is compressed by the piston 122.
  • a suction muffler 154 is coupled to the suction port 152.
  • a discharge muffler 155 is coupled by a discharge tube to a high-pressure chamber of the cylinder head 150 which is coupled to the discharge port 153.
  • a vibration damping member 160 is attached to the upper container portion 101 and is located above the counterweight 138.
  • electrical power is supplied to the electromotive element 110 though the electrical connection 113.
  • This causes the rotor 112 to rotate relative to the stator 111.
  • the rotation of the rotor 112 causes the crankshaft 130 to rotate.
  • the rotation of the crankshaft 130 is converted into reciprocating motion by the eccentric shaft portion 136 and the connecting rod 124. This reciprocating motion causes the piston 122 to reciprocate in the cavity of the cylinder block 121.
  • a refrigerant gas is drawn into the compression chamber 123 though the suction port 152.
  • the refrigerant gas having a low pressure is guided into the closed vessel formed by the upper container portion 101 and the lower container portion 102 though a suction pipe from a refrigeration cycle.
  • the refrigerant gas is drawn into the compression chamber 123 through the suction muffler 154.
  • the piston 122 begins to move back towards the top dead center position and the refrigerant gas in the compression chamber 123 is compressed. Because the pressure in the compression chamber 123 increases, the reed valve of the suction port 152 is pressed against the valve plate 151 and the suction port 152 is closed. The increased pressure in the compression chamber 123 opens the reed valve of the discharge port 153 and the compressed refrigerant gas enters the high-pressure chamber of the cylinder head 150 and is discharged through the discharge pipe via the discharge muffler 155 to the high pressure side of a refrigeration cycle.
  • FIG.2 is a sectional view of an example hermetic compressor with reference to which advantages of embodiments of the present invention will be described.
  • the hermetic compressor 200 comprises an electromotive element 210 and a compressive element 220. Many of the parts of the hermetic compressor 200 shown in FIG.2 are the same as those of the hermetic compressor 100 shown in FIG.1 , and a description of these parts is omitted in the following.
  • the hermetic compressor 200 comprises a crankshaft 230 which has a main shaft portion 231 , a flange portion 235 and an eccentric shaft portion 236.
  • a counterweight 238 is coupled to the top end of the eccentric shaft portion 236 by an arm portion 237. As shown in FIG.2, the arm portion 237 is straight and does not include any bends.
  • a piston 222 is coupled to the eccentric shaft portion 236 by a connecting rod 224. The piston 222 reciprocates in a compression chamber 223 formed in a cylinder block 221 when the crankshaft 230 rotates.
  • a vibration damping member 260 is attached to the upper container portion of the hermetic compressor 200 and is located above the counterweight 138.
  • the vibration damping member 260 is located above the counterweight 236 and on the top shell, for the purpose of preventing hitting of the compressor body against shell during transportation.
  • crankshaft 230 of the hermetic compressor 200 The movement of the crankshaft 230 of the hermetic compressor 200 will now be described with reference to FIG.3A and FIG.3B.
  • FIG.3A is a sectional view of the compressive element 220 of the hermetic compressor 200 shown in FIG.2 in a top dead center position
  • FIG.3B is a sectional view of the compressive element 220 of the hermetic compressor 200 shown in FIG.2 in a bottom dead center position.
  • the eccentric shaft portion 236 when the piston 222 is in the top dead center position, the eccentric shaft portion 236 is in a position closest to the compression chamber 223 and the counterweight 238 is located in a position farthest from the compression chamber 223.
  • the movement of the eccentric shaft portion 236 is caused by the mounting of the eccentric shaft portion 236 in an off-center position on the flange portion 235.
  • the movement of the counterweight 238 is caused by the mounting of the counterweight 238 on the arm portion 236.
  • FIG.3B when the piston 222 is in the bottom dead center position, the volume of the compression chamber 223 is at its largest.
  • the eccentric shaft portion 236 is located in a position furthest from the compression chamber 223.
  • the counterweight 238 is in a position in which it is vertically above part of the piston 222. As shown in FIG.3B, the bottom of the arm portion 237 is vertically above the piston 222 and a clearance is provided between the top of the piston 222 and bottom of the arm portion 237 which overlaps with the piston 222.
  • FIG.4A is a sectional view showing the forces acting on the compressive element of the hermetic compressor shown in FIG.2 near the top dead center position
  • FIG.4B is a sectional view showing the forces acting on the compressive element of the hermetic compressor shown in FIG.2 near the bottom dead center position.
  • the mass of the counterweight 238 is selected such that the centrifugal force 418 acting on the counterweight 238 and the centrifugal force 412 acting on the flange portion 235 are balanced with the centrifugal force 414 acting on the eccentric shaft 236 and the inertial force 420 acting on the piston 222.
  • FIG.5A is a sectional view of the compressive element 120 of the hermetic compressor 100 shown in FIG.1 in a top dead center position
  • FIG.5B is a sectional view of the compressive element 120 of the hermetic compressor 100 shown in FIG.1 in a bottom dead center position.
  • the eccentric shaft portion 136 when the piston 122 is in the top dead center position, the eccentric shaft portion 136 is in a position closest to the compression chamber 123 and the counterweight 138 is located in a position farthest from the compression chamber 123. Comparing FIG.5A and FIG.3A, it can be seen that the eccentric shaft portion 136 shown in FIG.5A is shorter than the eccentric shaft portion 236 shown in FIG.3A.
  • FIG.5A shows the outline 510 of the additional length of the eccentric shaft portion which is omitted. Because the eccentric shaft portion 136 is shorter it has a smaller mass. Therefore, the required mass of the counterweight 138 is also smaller than the required mass of the counterweight 238 of the hermetic compressor 200 shown in FIG.2. Since the required mass of the counterweight 138 is smaller, the counterweight 138 can be made thinner.
  • the volume of the compression chamber 123 is at its largest.
  • the eccentric shaft portion 136 is located in a position furthest from the compression chamber 123.
  • the counterweight 138 is in a position in which it is vertically above part of the piston 122.
  • the top of the eccentric shaft portion 136 is below the bottom of the counterweight 138, because the arm portion 137 bends from a horizontal direction and then bends back to the horizontal direction, the counterweight 138 is supported in a position above the piston 122.
  • the extra length corresponding to the outline 510 of the eccentric shaft portion 136 is not required.
  • the length of the eccentric shaft portion 136 can be reduced. This reduces the required mass for the counterweight. Since the required mass for the counterweight is reduced, the counterweight can be made thinner. This reduces the required height for the counterweight.
  • the hermetic compressor 100 in order for the hermetic compressor 100 to operate, there must be a clearance between the top of the counterweight 138 and the vibration damping member 160. Since embodiments of the present invention allow the counterweight 138 to be made thinner, the overall height of the compressor 100 can be reduced while still allowing for the required clearance.
  • the arm portion has bends of approximately 60 degrees. In other embodiments, the angle though which the arm portion is bent can vary. This is described below with reference to FIG.6 to FIG.9. In FIG.6 to FIG.9 only features which are different from FIG.1 are described and the remaining features are as described above with reference to FIG.1.
  • FIG.6 is a sectional view of a hermetic compressor according to an embodiment having an arm portion with bends of approximately 15 degrees. As shown in FIG.6, the compressor 600 has an arm portion 637 with two bends of approximately 15 degrees. The counterweight 638 is attached to the arm portion 637.
  • FIG.7 is a sectional view of a hermetic compressor according to an embodiment having an arm portion with bends of approximately 90 degrees. As shown in FIG.7, the compressor 700 has an arm portion 737 with two bends of approximately 90 degrees. The counterweight 738 is attached to the arm portion 737.
  • FIG.8 is a sectional view of a hermetic compressor according to an embodiment having an arm portion with bends of approximately 135 degrees. As shown in FIG.8, the compressor 800 has an arm portion 837 with two bends of approximately 135 degrees. The counterweight 838 is attached to the arm portion 837.
  • FIG.9 is a sectional view of a hermetic compressor according to an embodiment having an arm portion with bends of approximately 180 degrees. As shown in FIG.9, the compressor 900 has an arm portion 937 with two bends of approximately 180 degrees. The counterweight 938 is attached to the arm portion 937.
  • the arm portion includes two bends of the same angle.
  • the part coupled of the arm portion coupled to the end of eccentric shaft portion and the part of the arm portion that supports the counterweight are parallel to one another.
  • the counterweight 138, 838, 738, 838, 938 and arm portion 137, 637, 837, 937 may be an integral part, or separate parts connected by welding, adhesive, rivet pin or other connection method.
  • a vibration damping member is provided on the inner side of the top of the shell, however, embodiments are also envisaged in which no damping member is provided and the configuration of arm portion and counterweight allows a clearance between the counterweight and the top of the inner shell to be maintained while allowing the overall height of the compressor to be reduced.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un vilebrequin pour compresseur hermétique, le vilebrequin comprenant : une partie arbre principale ; une partie bride accouplée à une extrémité de la partie arbre principale ; une partie arbre excentrique accouplée à la partie bride, la partie arbre excentrique comportant un axe principal parallèle à l'axe de rotation de la partie arbre principale et décalé par rapport audit axe de rotation ; une partie bras s'étendant à partir d'une extrémité de la partie arbre excentrique distale par rapport à la partie bride, la partie bras comportant une partie accouplée à l'extrémité de la partie arbre excentrique distale par rapport à la partie bride, une partie inclinée qui est inclinée à l'opposé de la partie bride et une partie de soutien de contrepoids parallèle à la partie accouplée à l'extrémité de l'arbre excentrique ; et un contrepoids accouplé à la partie de soutien de contrepoids de la partie bras.
PCT/SG2020/050190 2019-03-29 2020-03-30 Vilebrequin pour compresseur hermétique et compresseur hermétique WO2020204826A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2021560192A JP2022528559A (ja) 2019-03-29 2020-03-30 密閉型コンプレッサ用クランクシャフトおよび密閉型コンプレッサ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SG10201902843U 2019-03-29
SG10201902843U 2019-03-29

Publications (1)

Publication Number Publication Date
WO2020204826A1 true WO2020204826A1 (fr) 2020-10-08

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PCT/SG2020/050190 WO2020204826A1 (fr) 2019-03-29 2020-03-30 Vilebrequin pour compresseur hermétique et compresseur hermétique

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JP (1) JP2022528559A (fr)
WO (1) WO2020204826A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6195888B1 (en) * 1998-03-11 2001-03-06 Tecumseh Products Company Counterweight for hermetic compressors
US20040213682A1 (en) * 2003-04-28 2004-10-28 Samsung Gwang Ju Electronics Co., Ltd. Hermetic compressor
JP2007077896A (ja) * 2005-09-15 2007-03-29 Matsushita Electric Ind Co Ltd 冷媒圧縮機
JP2008121554A (ja) * 2006-11-13 2008-05-29 Matsushita Electric Ind Co Ltd 圧縮機
US8764416B2 (en) * 2008-07-31 2014-07-01 Panasonic Corporation Closed type compressor
WO2015066782A2 (fr) * 2013-11-07 2015-05-14 Whirlpool S.A. Ensemble contrepoids-arbre d'un compresseur alternatif
JP2018184917A (ja) * 2017-04-27 2018-11-22 日立アプライアンス株式会社 密閉型圧縮機及びこれを搭載した機器

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6195888B1 (en) * 1998-03-11 2001-03-06 Tecumseh Products Company Counterweight for hermetic compressors
US20040213682A1 (en) * 2003-04-28 2004-10-28 Samsung Gwang Ju Electronics Co., Ltd. Hermetic compressor
JP2007077896A (ja) * 2005-09-15 2007-03-29 Matsushita Electric Ind Co Ltd 冷媒圧縮機
JP2008121554A (ja) * 2006-11-13 2008-05-29 Matsushita Electric Ind Co Ltd 圧縮機
US8764416B2 (en) * 2008-07-31 2014-07-01 Panasonic Corporation Closed type compressor
WO2015066782A2 (fr) * 2013-11-07 2015-05-14 Whirlpool S.A. Ensemble contrepoids-arbre d'un compresseur alternatif
JP2018184917A (ja) * 2017-04-27 2018-11-22 日立アプライアンス株式会社 密閉型圧縮機及びこれを搭載した機器

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JP2022528559A (ja) 2022-06-14

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