WO2015011906A1 - Compresseur étanche et dispositif de réfrigération - Google Patents

Compresseur étanche et dispositif de réfrigération Download PDF

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Publication number
WO2015011906A1
WO2015011906A1 PCT/JP2014/003803 JP2014003803W WO2015011906A1 WO 2015011906 A1 WO2015011906 A1 WO 2015011906A1 JP 2014003803 W JP2014003803 W JP 2014003803W WO 2015011906 A1 WO2015011906 A1 WO 2015011906A1
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WO
WIPO (PCT)
Prior art keywords
discharge
reed valve
valve
hermetic compressor
compression chamber
Prior art date
Application number
PCT/JP2014/003803
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English (en)
Japanese (ja)
Inventor
賢治 金城
小林　正則
Original Assignee
パナソニックＩｐマネジメント株式会社
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.)
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Priority claimed from JP2013151397A external-priority patent/JP2016169604A/ja
Priority claimed from JP2013169523A external-priority patent/JP2016169605A/ja
Application filed by パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Publication of WO2015011906A1 publication Critical patent/WO2015011906A1/fr

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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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
    • 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

Definitions

  • the present invention relates to a hermetic compressor used for a home electric refrigerator-freezer, a showcase, and the like, and a refrigeration apparatus using the same.
  • the conventional hermetic compressor is designed to improve efficiency by reducing loss when refrigerant gas is discharged from the compression chamber (see, for example, Patent Document 1).
  • FIG. 12 is a longitudinal sectional view of a conventional hermetic compressor.
  • FIG. 13 is an exploded perspective view of a discharge valve device of a conventional hermetic compressor.
  • FIG. 14 is a front view of a valve plate of a conventional hermetic compressor.
  • oil 503 is stored at the bottom of the hermetic container 501.
  • the airtight container 501 is filled with a refrigerant gas 505.
  • the compressor main body 507 is elastically supported in the sealed container 501 by a suspension spring (not shown).
  • the compressor main body 507 includes an electric element 511 including a stator 515 and a rotor 517, and a compression element 513 disposed above the electric element 511.
  • the compression element 513 includes a cylinder block 521 in which a cylinder 519 is integrally formed, a piston 523 that reciprocates within the cylinder 519, and a valve plate 525 that seals an end surface of the cylinder 519.
  • the compression element 513 includes a cylinder head 527 that covers the valve plate 525, a crankshaft 535 that includes an eccentric shaft 531 and a main shaft 533, and a connecting means 537 that connects the eccentric shaft 531 and the piston 523. ing.
  • a compression chamber 539 is formed by the cylinder 519, the valve plate 525, and the piston 523.
  • a discharge space 541 is formed by the valve plate 525 and the cylinder head 527.
  • the valve plate 525 has a recess 543 formed on the opposite side of the cylinder 519.
  • a discharge hole 545 for discharging the refrigerant gas 505 compressed in the compression chamber 539 into the discharge space 541 is provided in the recess 543.
  • a discharge reed valve 547 that opens and closes the discharge hole 545 is disposed.
  • the recess 543 extends over almost the entire region exposed to the discharge space 541 of the valve plate 525. Therefore, a sufficient space is formed around the discharge reed valve 547.
  • the refrigerant gas 505 discharged from the compression chamber 539 through the discharge hole 545 can be smoothly discharged to the discharge space 541. Therefore, the discharge efficiency of the refrigerant gas 505 can be increased.
  • the region where the concave portion 543 faces the compression chamber 539 the region where the thickness of the bottom surface of the concave portion 543 becomes thin becomes wider, and the strength of the valve plate 525 decreases. Then, due to the pressure difference between the compression chamber 539 and the discharge space 541, the bottom surface of the recess 543 of the valve plate 525 is deformed, and the discharge hole 545 is also deformed accordingly. However, there is a problem that the volumetric efficiency is lowered and the efficiency of the hermetic compressor is lowered.
  • Patent Document 2 discloses a conventional compressor technology.
  • JP 2009-299491 A Japanese Utility Model Publication No. 63-108573
  • the present invention solves the conventional problems, and provides a hermetic compressor with improved volume efficiency and improved efficiency by improving the sealing performance while ensuring the strength of the bottom surface of the concave portion of the valve plate. .
  • the hermetic compressor of the present invention includes an electric element and a compression element driven by the electric element in a hermetic container.
  • the compression element includes a crankshaft having a main shaft and an eccentric shaft, a cylinder block that supports the main shaft of the crankshaft and includes a cylinder, and a piston that reciprocates within the cylinder. Further, a connecting portion that connects the eccentric shaft of the crankshaft and the piston, and a valve plate that is disposed at the end of the cylinder and that forms a compression chamber with the piston are provided. Further, a discharge space formed by a cylinder head that covers the opposite side of the compression chamber of the valve plate is provided.
  • the valve plate includes a suction hole, a recess formed on the opposite side of the compression chamber, a discharge hole provided in the recess, a discharge reed valve that opens and closes the discharge hole, and a stopper that restricts the movement of the discharge reed valve.
  • a refrigerant gas guiding portion that guides the refrigerant gas from the concave portion to the discharge space is provided on the side wall of the concave portion.
  • the hermetic compressor of the present invention can prevent deformation of the bottom surface of the concave portion of the valve plate and accompanying deformation of the discharge hole. Therefore, the sealing performance between the discharge hole and the discharge reed valve can be improved, the volume efficiency can be improved, and the efficiency of the hermetic compressor can be improved.
  • FIG. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is an exploded perspective view of the discharge valve device of the hermetic compressor according to the first embodiment of the present invention.
  • FIG. 3 is a sectional view of the discharge valve device of the hermetic compressor according to the first embodiment of the present invention.
  • FIG. 4 is a front view of the valve plate of the hermetic compressor according to the first embodiment of the present invention.
  • FIG. 5 is a cross-sectional view of the discharge valve device of the hermetic compressor according to the second embodiment of the present invention.
  • FIG. 6 is a schematic diagram showing the configuration of the refrigeration apparatus in Embodiment 3 of the present invention.
  • FIG. 7 is a longitudinal sectional view of a compressor according to Embodiment 4 of the present invention.
  • FIG. 8 is an exploded perspective view of the discharge valve device according to Embodiment 4 of the present invention.
  • FIG. 9A is a cross-sectional view of the discharge valve device according to Embodiment 4 of the present invention when the discharge reed valve is closed.
  • FIG. 9B is a cross-sectional view of the discharge valve device according to Embodiment 4 of the present invention when the discharge reed valve is open.
  • FIG. 10 is a front view of a discharge valve device according to Embodiment 4 of the present invention.
  • FIG. 11 is a schematic cross-sectional view of the refrigerator in the fifth embodiment of the present invention.
  • FIG. 12 is a longitudinal sectional view of a conventional hermetic compressor.
  • FIG. 13 is an exploded perspective view of a discharge valve device of a conventional hermetic compressor.
  • FIG. 14 is a front view of a valve plate of
  • FIG. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is an exploded perspective view of the discharge valve device of the hermetic compressor according to the first embodiment of the present invention.
  • FIG. 3 is a sectional view of the discharge valve device of the hermetic compressor according to the first embodiment of the present invention.
  • FIG. 4 is a front view of the valve plate of the hermetic compressor according to the first embodiment of the present invention.
  • the hermetic compressor according to the first embodiment mainly includes an electric element 103 and a compression element 105 driven by the electric element 103 inside a hermetic container 101 formed by drawing a steel plate.
  • a compressor main body 107 is disposed.
  • the compressor body 107 is elastically supported by a suspension spring 109.
  • a refrigerant gas 111 such as hydrocarbon-based R600a having a low global warming potential is in a relatively low temperature state at a pressure equivalent to the low pressure side of the refrigeration apparatus (not shown). It is enclosed with. Lubricating oil 113 is sealed in the bottom of the sealed container 101.
  • the sealed container 101 is compressed by a compression element 105 and a suction pipe (not shown) whose one end communicates with the space inside the sealed container 101 and the other end is connected to a refrigeration apparatus (not shown). And a discharge pipe 115 that guides the refrigerant gas 111 to a refrigeration apparatus (not shown).
  • the compression element 105 includes a crankshaft 117, a cylinder block 119, a piston 121, a connecting portion 123, and the like.
  • the crankshaft 117 includes an eccentric shaft 125, a main shaft 127, and an oil supply mechanism 129.
  • the oil supply mechanism 129 supplies the oil 113 from the lower end of the main shaft 127 immersed in the oil 113 to the upper end of the eccentric shaft 125.
  • the oil supply mechanism 129 includes a spiral groove 131 formed on the surface of the main shaft 127.
  • the cylinder 135 is integrally formed with the cylinder block 119.
  • the cylinder block 119 includes a bearing portion 137 that rotatably supports the main shaft 127.
  • valve plate 143 having a suction hole 139 and a discharge hole 141, a suction reed valve 145 for opening and closing the suction hole 139, and a valve plate 143 are covered on the end face of the cylinder 135 opposite to the opening of the crankshaft 117.
  • the cylinder head 147 is fixed together by a head bolt (not shown).
  • a compression chamber 133 is formed by the piston 121, the cylinder 135, and the valve plate 143.
  • a discharge space 149 for expanding the refrigerant gas 111 discharged from the discharge hole 141 is formed between the cylinder head 147 and the valve plate 143.
  • the discharge space 149 communicates directly with the discharge pipe 115 via the discharge pipe 151.
  • a suction muffler 153 is sandwiched and fixed between the valve plate 143 and the cylinder head 147.
  • the electric element 103 includes a stator 155 and a rotor 157.
  • the stator 155 is fixed below the cylinder block 119 with bolts (not shown).
  • the rotor 157 is disposed on the inner side of the stator 155 and coaxially with the stator 155, and is fixed to the main shaft 127 by shrink fitting or the like.
  • the electric element 103 is connected to an external inverter drive circuit (not shown) and is inverter-driven at a plurality of operation frequencies.
  • the discharge valve device of the present embodiment includes a valve plate 143, a discharge reed valve 159, a spring reed valve 161, and a stopper 163.
  • the valve plate 143 has a recess 165 formed on the opposite side of the cylinder 135.
  • a discharge hole 141 for discharging the refrigerant gas 111 compressed in the compression chamber 133 into the discharge space 149 is formed in the recess 165.
  • the discharge reed valve 159, the spring reed valve 161, and the stopper 163 are sequentially arranged so that the discharge hole 141 opens and closes.
  • Refrigerant gas guiding portions 167 are formed on the side walls of the curved surface so that the refrigerant gas 111 is guided from the concave portion 165 to the discharge space 149 on both side walls facing the longitudinal direction of the discharge reed valve 159 of the recess 165.
  • the recess 165 is formed in a region having an area of about half the area of the region exposed to the discharge space 149 of the valve plate 143.
  • the suction pipe (not shown) and the discharge pipe 115 are connected to a refrigeration apparatus (not shown) having a known configuration to constitute a refrigeration cycle.
  • the piston 121 reciprocates, the refrigerant gas 111 is sucked, compressed, and discharged in the compression chamber 133.
  • the suction reed valve 145 starts to open due to the difference between the pressure in the compression chamber 133 and the pressure in the suction muffler 153.
  • the low-temperature refrigerant gas 111 returned from the refrigeration cycle is once released into the sealed container 101 from the suction pipe (not shown), and then flows into the compression chamber 133 through the suction muffler 153. .
  • the discharge reed valve 159 starts to open due to the difference between the pressure in the compression chamber 133 and the pressure in the discharge space 149.
  • the compressed refrigerant gas 111 is discharged from the discharge hole 141 to the discharge space 149 until the piston 121 reaches top dead center. Then, the refrigerant gas 111 discharged into the discharge space 149 passes through the discharge pipe 151 and the discharge pipe 115 sequentially, and is sent out to a refrigeration apparatus (not shown).
  • the reciprocating hermetic compressor as in the present embodiment has a dead volume due to the piston 121, the cylinder 135, the valve plate 143, the discharge hole 141, and the discharge reed valve 159 at the end of the discharge stroke. Is formed. In the dead volume, the compressed refrigerant gas 111 remains slightly without being discharged.
  • the remaining refrigerant gas 111 is re-expanded when the piston 121 moves from the top dead center toward the bottom dead center, and the volume of the refrigerant gas 111 newly sucked is reduced. For this reason, volume efficiency falls.
  • the recess 165 is formed in the valve plate 143, and the discharge hole 141 is formed in the recess 165, so that the height of the discharge hole 141 is reduced and the volume of the discharge hole 141 is increased. It is decreasing. As a result, the dead volume is reduced.
  • valve plate 143 is exposed to the low pressure compression chamber 133 and the high pressure discharge space 149 during the intake stroke. For this reason, if the recessed part 165 is formed in the valve plate 143 by the thin bottom face, the intensity
  • the recess 165 can be provided with the discharge reed valve 159, the spring reed valve 161, and the stopper 163, and ensures a minimum gap through which the refrigerant gas 111 discharged from the discharge hole 141 can flow into the discharge space 149. .
  • the recessed part 165 is formed so that the area
  • the side wall of the recess 165 is generally formed substantially perpendicular to the bottom surface of the recess 165.
  • the gap between the side wall of the recess 165 and the discharge reed valve 159 is narrowed. Further, when the refrigerant gas 111 flows out toward the side wall that rises substantially vertically, the flow path resistance increases. As a result, the pressure drop in the recess 165 is delayed, and the refrigerant gas 111 cannot be completely discharged from the compression chamber 133. For this reason, volume efficiency falls.
  • the refrigerant gas guiding portion 167 having a curved surface on the side wall of the concave portion 165 is formed so that the refrigerant gas 111 easily flows out from the concave portion 165 to the discharge space 149.
  • the refrigerant gas 111 discharged from the compression chamber 133 through the discharge hole 141 can be smoothly discharged into the discharge space 149 along the curved surface of the refrigerant gas guiding portion 167. . Therefore, the flow path resistance of the refrigerant gas 111 can be reduced and the discharge efficiency can be improved.
  • the refrigerant gas guiding portion 167 can be formed on the side wall of the curved surface without expanding the bottom surface of the concave portion 165. Therefore, the deformation of the bottom surface of the recess 165 of the valve plate 143 and the accompanying deformation of the discharge hole 141 can be reduced.
  • the sealing performance between the discharge hole 141 and the discharge reed valve 159 can be improved.
  • the gap between the discharge reed valve 159 and the side wall of the recess 165 can be widened.
  • the flow resistance of the refrigerant gas 111 can be reduced and the volume efficiency can be improved.
  • the refrigerant gas 111 flows out to the side walls on both sides facing the longitudinal direction of the discharge reed valve 159.
  • the refrigerant gas guiding portion 167 is formed on the side wall facing the longitudinal direction of the discharge reed valve 159, the discharge loss can be more effectively reduced and the volume efficiency can be improved.
  • the discharge loss is effectively reduced and the efficiency of the hermetic compressor is effectively reduced at high speed rotation where the refrigerant circulation amount increases. Be improved.
  • the hermetic compressor includes the electric element 103 and the compression element 105 driven by the electric element 103 in the hermetic container 101.
  • the compression element 105 includes a crankshaft 117 having a main shaft 127 and an eccentric shaft 125, a cylinder block 119 that supports the main shaft 127 of the crankshaft 117 and has a cylinder 135, and a piston 121 that reciprocates within the cylinder 135. . Further, a connecting portion 123 that connects the eccentric shaft 125 of the crankshaft 117 and the piston 121, and a valve plate 143 that is disposed at the end of the cylinder 135 and forms the compression chamber 133 with the piston 121.
  • a discharge space 149 formed by a cylinder head 147 that covers the opposite side of the valve plate 143 to the compression chamber 133 is provided.
  • the valve plate 143 includes a suction hole 139, a recess 165 formed on the opposite side of the compression chamber 133, a discharge hole 141 provided in the recess 165, a discharge reed valve 159 for opening and closing the discharge hole 141, and a discharge lead. And a stopper 163 that restricts the movement of the valve 159.
  • a refrigerant gas guide 167 that guides the refrigerant gas from the recess 165 to the discharge space is provided on the side wall of the recess 165.
  • the refrigerant gas discharged from the compression chamber 133 through the discharge hole 141 can smoothly flow out into the discharge space without expanding the bottom area of the recess 165 provided in the valve plate 143. Therefore, the deformation of the bottom surface of the concave portion 165 of the valve plate 143 and the accompanying deformation of the discharge hole 141 can be prevented. Therefore, the sealing performance between the discharge hole 141 and the discharge reed valve 159 is improved, and the volume efficiency can be improved.
  • the refrigerant gas guiding portion 167 is formed with a curved side wall.
  • the refrigerant gas guiding portion can be formed on the side wall of the curved surface without expanding the bottom surface of the recess.
  • the strength reduction of the bottom surface of the concave portion of the valve plate can be reduced.
  • the refrigerant gas guiding portion 167 is formed on at least one side wall in the longitudinal direction of the discharge reed valve 159. Thereby, discharge loss can be reduced more effectively and volume efficiency can be improved.
  • the electric element 103 is inverter-driven at a plurality of operating frequencies. As a result, the discharge loss is effectively reduced at high speed rotation in which the amount of refrigerant circulation increases, so that the efficiency of the hermetic compressor can be improved.
  • the hermetic compressor of the present embodiment can include the configuration of the compressor of the fourth embodiment described later. That is, the hermetic compressor includes the following configuration.
  • the valve plate 143 has a reed valve seat portion 331 formed on the opposite side of the discharge hole 141.
  • the discharge reed valve 159 has a fixed portion fixed in contact with the valve plate 143 and an opening in a part on the fixed portion side.
  • the stopper 163 has at least one end fixed on the extension line of the central axis of the discharge reed valve 159 connecting the reed valve seat portion 331 and the fixed portion, and has an opening in a range including the reed valve seat portion 331 on the central axis.
  • the contact area between the discharge reed valve 159 and the valve plate 143 can be reduced, and the oil adhesive force can be reduced. Therefore, the delay in opening the discharge reed valve 159 can be prevented. Further, the refrigerant gas can be passed through the openings of the discharge reed valve 159 and the stopper 163, and the discharge loss can be reduced. Therefore, the performance of the hermetic compressor is improved.
  • the spring reed valve 161 provided between the discharge reed valve 159 and the stopper 163 has an opening in a range including the reed valve seat 331 on the central axis.
  • FIG. 5 is a cross-sectional view of the discharge valve device of the hermetic compressor according to the second embodiment of the present invention.
  • the refrigerant gas guiding portion 167 provided on the side wall of the concave portion 165 of the valve plate 143 is not a curved surface but an inclined surface.
  • the inclined surface has a straight section.
  • the refrigerant gas guiding portion 167 is formed as an inclined surface, the same effect as that of the curved surface can be expected.
  • the deformation of the bottom surface of the recess 165 of the valve plate 143 and the accompanying deformation of the discharge hole 141 can be further reduced. Therefore, the volumetric efficiency can be further improved, and the efficiency of the hermetic compressor can be further improved.
  • the refrigerant gas guiding portion 167 is formed by the side wall of the inclined surface. Accordingly, the refrigerant gas guiding portion can be formed on the side wall of the inclined surface without expanding the bottom surface of the recess. Moreover, the strength reduction of the bottom surface of the concave portion of the valve plate can be reduced.
  • FIG. 6 is a schematic diagram showing the configuration of the refrigeration apparatus in Embodiment 3 of the present invention.
  • the hermetic compressor described in Embodiment 1 or 2 is mounted in the refrigerant circuit 209. An outline of the basic configuration of the refrigeration apparatus of the present embodiment will be described.
  • the refrigeration apparatus includes a main body 201 including a heat-insulating box having an opening on one side and a door that opens and closes the opening.
  • the main body 201 includes therein an article storage space 203, a machine room 205, a partition wall 207 that partitions the main body 201 into the storage space 203 and the machine room 205, and a refrigerant circuit 209 that cools the inside of the storage space 203. It has.
  • the refrigerant circuit 209 has a configuration in which the compressor 211, the radiator 213, the decompression device 215, and the heat absorber 217 described in the first embodiment are connected in a ring shape as a hermetic compressor.
  • the heat absorber 217 is arrange
  • the cooling heat of the heat absorber 217 is agitated so as to circulate in the storage space 203 by the blower as indicated by an arrow, and the storage space 203 is cooled.
  • the compressor 211 described in the first embodiment of the present invention is mounted on the refrigeration apparatus described above as a hermetic compressor, the compressor 211 is provided with a refrigerant gas guiding portion provided on the side wall of the recess 165 of the valve plate 143.
  • the discharge efficiency of the refrigerant gas 111 is improved. Therefore, power consumption of the refrigeration apparatus can be reduced, and energy saving of the refrigeration apparatus can be realized.
  • the refrigeration apparatus of the present embodiment includes the refrigerant circuit 209 in which the hermetic compressor, the radiator 213, the decompressor 215, and the heat absorber 217 are connected in a ring shape by piping.
  • the power consumption of the refrigeration apparatus can be reduced and energy saving can be realized by mounting the hermetic compressor with improved volumetric efficiency.
  • FIG. 7 is a longitudinal sectional view of a compressor according to Embodiment 4 of the present invention.
  • FIG. 8 is an exploded perspective view of the discharge valve device 326 according to Embodiment 4 of the present invention.
  • FIG. 9A is a cross-sectional view of the discharge valve device according to Embodiment 4 of the present invention when the discharge reed valve is closed.
  • FIG. 9B is a cross-sectional view of the discharge valve device according to Embodiment 4 of the present invention when the discharge reed valve is open.
  • FIG. 10 is a front view of a discharge valve device according to Embodiment 4 of the present invention.
  • the compressor 300 stores the oil 302 in the sealed container 301.
  • the compressor 300 accommodates an electric compression element 305 that includes an electric element 303 and a compression element 304 disposed above the electric element 303.
  • the sealed container 301 is filled with a hydrocarbon-based R600a refrigerant 306, and a low-viscosity oil 302 of VG3 to VG10 is sealed at the bottom.
  • the electric element 303 includes a rotor 311 and a stator 312 and is driven by an inverter (not shown) at a plurality of operation frequencies including at least an operation frequency equal to or higher than the power supply frequency.
  • the maximum operating frequency for driving the electric element 303 is 80 Hz, and the minimum operating frequency is 17 Hz.
  • the compression element 304 includes a crankshaft 316, a cylinder block 320, a piston 322, a connecting portion 321, a valve plate 324, and a discharge valve device 326.
  • the crankshaft 316 includes a main shaft 313 that is arranged in the vertical direction and fixes the rotor 311, an eccentric shaft 314, and an oil supply mechanism 315.
  • the cylinder block 320 includes a main bearing 317 that supports the main shaft 313 of the crankshaft 316 and a cylinder 319 that forms a compression chamber 318.
  • the piston 322 reciprocates within the cylinder 319.
  • the connecting portion 321 connects the piston 322 and the eccentric shaft 314.
  • the valve plate 324 is provided at the end 323 of the compression chamber 318.
  • the discharge valve device 326 is formed on the opposite side of the compression chamber of the valve plate 324.
  • the valve plate 324 is formed with a discharge hole 330 and a reed valve seat portion 331 that is annular on the opposite side of the discharge hole 330 from the compression chamber.
  • the discharge valve device 326 includes a discharge reed valve 333 made of a leaf spring material, a spring reed valve 335 made of a leaf spring material, and a stopper 337.
  • One end of the discharge reed valve 333 has an opening / closing part 333a for opening and closing the reed valve seat part 331, and the other end has a fixing part 333b.
  • One end of the spring reed valve 335 is disposed in parallel with the discharge reed valve 333 with a gap, and the other end elastically fixes the fixing portion 333 b of the discharge reed valve 333.
  • the stopper 337 is fixed on an extension line of the central shaft 334 of the discharge reed valve 333 that connects the reed valve seat portion 331 and the fixed portion 333b at both ends, and restricts the opening amounts of the discharge reed valve 333 and the spring reed valve 335.
  • the discharge reed valve 333 has an opening 333c between the opening / closing part 333a and the fixing part 333b. Further, the spring reed valve 335 and the stopper 337 have openings 335c and 337c in ranges including the opening / closing part 333a and the opening 333c of the discharge reed valve 333, respectively.
  • the rotor 311 of the electric element 303 rotates the crankshaft 316.
  • the rotational motion of the eccentric shaft 314 provided on the crankshaft 316 is transmitted to the piston 322 via the connecting portion 321.
  • the piston 322 reciprocates the cylinder 319.
  • the refrigerant 306 returns from the cooling system (not shown) into the sealed container 301, is sucked and compressed in the compression chamber 318, and is then discharged again to the cooling system via the discharge valve device 326.
  • Oil 302 is pumped upward by an oil supply mechanism 315 formed on the crankshaft 316 and supplied to a sliding surface between the main bearing 317 and the main shaft 313.
  • the oil 302 is horizontally scattered from the scattering hole (not shown) formed at the end of the eccentric shaft 314 in the entire circumferential direction in the sealed container 301 and is also supplied to the piston 322.
  • the compression element 304 is lubricated.
  • the refrigerant 306 is sucked from the suction hole 328 into the compression chamber 318. Since the opening / closing part 333 a of the discharge reed valve 333 closes the reed valve seat part 331, the discharged refrigerant 306 does not flow out of the compression chamber 318.
  • compressed gas is discharged from the gap 340 between the reed valve seat portion 331 and the opening / closing portion 333a while the discharge reed valve 333 is open in the discharge stroke.
  • the compressed gas also flows from the discharge reed valve 333, the spring reed valve 335, and the openings 333c, 335c, and 337c of the stopper 337.
  • the behavior of the discharge reed valve 333 in the compression stroke is such that the pressure in the compression chamber 318 is the pressure on the opposite side of the compression chamber, the spring load of the discharge reed valve 333, the inertial force of the opening / closing portion 333a, and the reed valve seat portion.
  • opening begins.
  • the discharge reed valve 333 has a maximum opening amount near the top dead center of the piston 322.
  • the resultant force of the spring load of the discharge reed valve 333 and the inertial force of the opening / closing portion 333a is the resultant of the differential pressure load inside and outside the compression chamber 318 and the oil adhesive force of the contact surface 339b of the discharge reed valve 333 and the spring reed valve 335. If it exceeds, it will begin to close.
  • the discharge reed valve 333 has an opening 333c between the opening / closing part 333a and the fixing part 333b. For this reason, the area of the contact surface 339a with the valve plate 324 is reduced by the opening 333c, whereby the oil adhesive force is reduced.
  • the opening amount of the discharge reed valve 333 increases, and the area of the contact surface 339 between the discharge reed valve 333 and the spring reed valve 335 increases.
  • the frequency increases. For this reason, the oil adhesive force tends to increase, and the closing of the discharge reed valve 333 tends to occur.
  • a compressor for a refrigeration cycle using R600a refrigerant is used.
  • a compressor using another type of refrigerant or a compression mechanism may be used as long as the compressor discharges compressed gas using a discharge valve device during a compression stroke.
  • the discharge valve device 326 has the discharge reed valve 333, the spring reed valve 335, and the stopper 337 as the components, but the same operation and effect can be achieved even in a configuration in which the spring reed valve 335 is omitted. Obtainable.
  • both ends of the stopper 337 are fixed to the valve plate 324.
  • fixing only one side does not affect the behavior of the discharge reed valve 333, and is similar to fixing both ends. The effect of can be obtained.
  • the hermetic compressor 300 includes the oil 302, the electric element 303, and the compression element 304 driven by the electric element 303 in the hermetic container 301.
  • the compression element 304 includes a cylinder block 320 that forms a cylinder 319 and a piston 322 that reciprocates within the cylinder 319. Further, the end of the cylinder 319 is sealed, the valve plate 324 that forms the compression chamber 318 with the piston 322, and formed on the opposite side of the compression chamber 318 of the valve plate 324, and the compressed gas is discharged from the compression chamber 318.
  • a discharge valve device 326 is a discharge valve device 326.
  • the discharge valve device 326 includes a valve plate 324 having a discharge hole 330 communicating with the compression chamber 318 and a reed valve seat portion 331 formed on the opposite side of the discharge hole 330.
  • an opening / closing part 333a for opening and closing the reed valve seat part 331 and a discharge reed valve 333 having a fixing part 333b fixed in contact with the valve plate 324 are provided.
  • at least one end is provided with a stopper 337 that is fixed on an extension line of the central axis of the discharge reed valve 333 that connects the reed valve seat portion 331 and the fixed portion 333b and restricts the opening amount of the discharge reed valve 333.
  • the discharge reed valve 333 has an opening 333c in a part on the fixed portion 333b side, and the stopper 337 has an opening 337c in a range including the reed valve seat 331 on the central axis.
  • the contact area between the discharge reed valve 333 and the valve plate 324 is reduced, and the oil adhesive force can be reduced. Therefore, the delay in opening the discharge reed valve 333 can be prevented.
  • the compressed gas can be passed through the discharge reed valve 333 and the openings 333c and 337c of the stopper 337, and the discharge loss can be reduced. Therefore, the performance of the hermetic compressor 300 is improved.
  • the hermetic compressor 300 further includes a spring reed valve 335 made of a leaf spring material between the discharge reed valve 333 and the stopper 337.
  • the spring reed valve 335 includes a reed valve seat 331 on the central axis. An opening 335c is provided in the range.
  • the compressed gas can be passed through the discharge reed valve 333, the spring reed valve 335, and the openings 333c, 335c, and 337c of the stopper 337, and the discharge loss can be reduced. Therefore, the performance of the hermetic compressor 300 is improved.
  • the electric element 303 is driven at a plurality of rotation speeds by an inverter circuit.
  • the contact area between the discharge reed valve 333, the spring reed valve 335, and the stopper 337 is reduced even if the opening amount of the discharge reed valve 333 is increased during the discharge stroke.
  • the oil adhesive force can be reduced. Therefore, the closing delay of the discharge reed valve 333 can be prevented. Therefore, the performance of the hermetic compressor 300 is improved.
  • FIG. 11 is a schematic cross-sectional view of the refrigerator in the fifth embodiment of the present invention.
  • a heat insulating box 380 is a heat insulating body that foams and fills a space formed by an inner box 382 obtained by vacuum molding a resin body such as ABS and an outer box 384 using a metal material such as a pre-coated steel plate.
  • Reference numeral 386 denotes a heat insulating wall injected.
  • the heat insulator 386 for example, rigid urethane foam, phenol foam, styrene foam, or the like is used.
  • As the heat insulator for foam filling it is better to use hydrocarbon-based cyclopentane from the viewpoint of preventing global warming.
  • the heat insulation box 380 is divided into a plurality of heat insulation sections, and has a structure in which the upper part is a revolving door type and the lower part is a drawer type. From the top, there are a refrigerating room 388, a drawer type switching room 390 and an ice making room 392 provided side by side, a drawer type vegetable room 394, and a drawer type freezer room 396. Each heat insulation section is provided with a heat insulation door via a gasket. From the top are the refrigerating room rotary door 398, the switching room drawer door 400, the ice making room drawer door 402, the vegetable room drawer door 404, and the freezer compartment drawer door 406.
  • the outer box 384 of the heat insulating box 380 includes a recessed portion 408 having a recessed top surface.
  • the refrigeration cycle includes a compressor 300, a condenser (not shown), a capillary 412, a dryer (not shown), an evaporator 416, and a suction pipe 418 that are connected in a ring shape. .
  • the compressor 300 is elastically supported by the recess 408.
  • the condenser (not shown) is provided on the side surface of the heat insulating box 380 or the like.
  • the capillary 412 is a decompressor.
  • a dryer removes moisture.
  • the evaporator 416 is disposed in the vicinity of the cooling fan 414 on the back of the vegetable compartment 394 and the freezer compartment 396.
  • the refrigerator compartment 388 is usually set to 1 ° C. to 5 ° C. with the lower limit of the temperature at which it does not freeze for refrigerated storage.
  • the switching room 390 can change the temperature setting by the user.
  • the switching chamber 390 can be set to a predetermined temperature from the freezer compartment temperature zone to the refrigerator compartment temperature zone and the vegetable compartment temperature zone.
  • the ice making room 392 is an independent ice storage room.
  • the ice making chamber 392 includes an automatic ice making device (not shown).
  • the ice making chamber 392 automatically creates and stores ice.
  • the ice making chamber 392 is a freezing temperature zone for storing ice, but may be set in a freezing temperature zone of ⁇ 18 ° C. to ⁇ 10 ° C., which is relatively higher than the freezing temperature zone for storing ice. Is possible.
  • the vegetable room 394 is often set to 2 ° C. to 7 ° C., which is the same as or slightly higher than the refrigerated room 388. It is possible to maintain the freshness of leafy vegetables for a long period of time as the temperature is lowered so that it does not freeze.
  • the freezer room 396 is normally set at ⁇ 22 to ⁇ 18 ° C. for frozen storage. However, in order to improve the frozen storage state, it may be set at a low temperature of, for example, -30 ° C or -25 ° C.
  • Each room is separated by a heat insulating wall 387 in order to efficiently maintain different temperature settings.
  • a heat insulating wall 387 in order to efficiently maintain different temperature settings.
  • the heat insulator 386 it is possible to achieve a heat insulation performance that is approximately twice that of using a heat insulating member such as polystyrene foam, and the storage volume can be increased by thinning the partition.
  • the cooling operation is started and stopped by signals from a temperature sensor (not shown) and a control board (not shown) according to the set temperature in the storage.
  • the compressor 300 performs a predetermined compression operation according to the instruction of the cooling operation.
  • the discharged high-temperature and high-pressure refrigerant gas dissipates heat in a condenser (not shown) and is condensed and liquefied, and is reduced in pressure by the capillary 412 to become a low-temperature and low-pressure liquid refrigerant and reaches the evaporator 416.
  • the cooling fan 414 exchanges heat with the air in the cabinet, and the refrigerant gas in the evaporator 416 is evaporated.
  • Each room is cooled by distributing low-temperature cold air subjected to heat exchange by a damper (not shown) or the like.
  • the refrigerator of the fifth embodiment is equipped with the compressor described in the fourth embodiment.
  • the compressor 300 prevents the delay in opening and closing by reducing the oil adhesive force by reducing the contact area of the discharge reed valve 333. As a result, the reduction in over-compression loss and the performance degradation due to the backflow of the discharge gas to the compression chamber 318 are suppressed, and the efficiency of the compressor 300 is improved. Therefore, the refrigerator equipped with the compressor 300 can reduce its power consumption.
  • the refrigeration apparatus of the present embodiment uses the hermetic compressor 300 of the fourth embodiment. Thereby, the power consumption of a freezing apparatus can be reduced.
  • the hermetic compressor and the refrigeration apparatus according to the present invention can increase the discharge efficiency of the refrigerant gas and improve the efficiency of the hermetic compressor. Therefore, the hermetic compressor and the refrigeration apparatus according to the present invention can be widely applied not only to household use such as an electric refrigerator or an air conditioner but also to a refrigeration apparatus such as a commercial showcase and a vending machine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

La présente invention concerne un compresseur étanche dans lequel un élément électromoteur, un vilebrequin entraîné par ledit élément électromoteur, un bloc-cylindres supportant l'arbre principal du vilebrequin, un piston qui se déplace en va-et-vient à l'intérieur du cylindre, une partie de liaison reliant le piston et l'arbre à excentrique du vilebrequin, et une plaque porte-soupape (143) agencée au niveau de l'extrémité du cylindre et formant une chambre de compression, sont disposés dans un contenant étanche. En outre, une soupape flexible d'évacuation (159, 333) qui ouvre/ferme un orifice d'évacuation (141, 330), et un élément d'arrêt (163, 337) qui limite le mouvement de la soupape flexible d'évacuation, sont disposés à l'intérieur d'un évidement (165) formé dans la plaque porte-soupape sur le côté situé en regard de la chambre de compression. Une partie de guidage (167) de gaz réfrigérant qui guide un gaz réfrigérant à partir de l'évidement vers un espace d'évacuation est prévue sur une paroi latérale de l'évidement, une partie de la soupape flexible d'évacuation comporte une ouverture (333c), et l'élément d'arrêt comporte une ouverture (337c).
PCT/JP2014/003803 2013-07-22 2014-07-17 Compresseur étanche et dispositif de réfrigération WO2015011906A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2013-151397 2013-07-22
JP2013151397A JP2016169604A (ja) 2013-07-22 2013-07-22 密閉型圧縮機および冷凍装置
JP2013169523A JP2016169605A (ja) 2013-08-19 2013-08-19 圧縮機及びそれを用いた冷凍装置
JP2013-169523 2013-08-19

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WO2015011906A1 true WO2015011906A1 (fr) 2015-01-29

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017191229A1 (fr) 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
WO2017191228A1 (fr) 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
EP3835581A1 (fr) * 2019-12-11 2021-06-16 Ananke Plaque à clapets d'admission et d'échappement à faibles irréversibilités, et compresseur comportant une telle plaque

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5853892U (ja) * 1981-10-09 1983-04-12 松下冷機株式会社 回転式圧縮機
JPH02291485A (ja) * 1989-03-09 1990-12-03 Empresa Brasileira De Compressores Sa Embraco 転動ピストン回転圧縮機のための出口弁
JPH04105674U (ja) * 1991-02-25 1992-09-11 三輪精機株式会社 リード弁装置
JP2005508480A (ja) * 2001-11-09 2005-03-31 エルジー エレクトロニクス インコーポレイティド 吐出バルブ及びこれを利用した圧縮機
JP2005090495A (ja) * 2003-09-17 2005-04-07 Lg Electronics Inc 圧縮機の吐出弁
JP2013057284A (ja) * 2011-09-08 2013-03-28 Panasonic Corp 密閉型圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5853892U (ja) * 1981-10-09 1983-04-12 松下冷機株式会社 回転式圧縮機
JPH02291485A (ja) * 1989-03-09 1990-12-03 Empresa Brasileira De Compressores Sa Embraco 転動ピストン回転圧縮機のための出口弁
JPH04105674U (ja) * 1991-02-25 1992-09-11 三輪精機株式会社 リード弁装置
JP2005508480A (ja) * 2001-11-09 2005-03-31 エルジー エレクトロニクス インコーポレイティド 吐出バルブ及びこれを利用した圧縮機
JP2005090495A (ja) * 2003-09-17 2005-04-07 Lg Electronics Inc 圧縮機の吐出弁
JP2013057284A (ja) * 2011-09-08 2013-03-28 Panasonic Corp 密閉型圧縮機

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017191229A1 (fr) 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
WO2017191228A1 (fr) 2016-05-05 2017-11-09 Arcelik Anonim Sirketi Compresseur hermétique à performances accrues
EP3835581A1 (fr) * 2019-12-11 2021-06-16 Ananke Plaque à clapets d'admission et d'échappement à faibles irréversibilités, et compresseur comportant une telle plaque

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