WO2011052195A1 - 密閉型圧縮機 - Google Patents

密閉型圧縮機 Download PDF

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Publication number
WO2011052195A1
WO2011052195A1 PCT/JP2010/006337 JP2010006337W WO2011052195A1 WO 2011052195 A1 WO2011052195 A1 WO 2011052195A1 JP 2010006337 W JP2010006337 W JP 2010006337W WO 2011052195 A1 WO2011052195 A1 WO 2011052195A1
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WO
WIPO (PCT)
Prior art keywords
piston
recess
cylindrical hole
dead center
hermetic compressor
Prior art date
Application number
PCT/JP2010/006337
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
正則 小林
Original Assignee
パナソニック株式会社
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.)
Filing date
Publication date
Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to US13/498,791 priority Critical patent/US20120183419A1/en
Priority to CN201080048808.7A priority patent/CN102597518B/zh
Priority to JP2011538247A priority patent/JP5753983B2/ja
Publication of WO2011052195A1 publication Critical patent/WO2011052195A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • 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
    • 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
    • F04B39/02—Lubrication
    • F04B39/0207—Lubrication with lubrication control systems
    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • 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
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/0276—Lubrication characterised by the compressor type the pump being of the reciprocating piston type, e.g. oscillating, free-piston compressors
    • 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
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F04B39/0292—Lubrication of pistons or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block

Definitions

  • the present invention relates to a hermetic compressor used in a refrigeration cycle system such as a refrigerator-freezer.
  • the reciprocating hermetic compressor has a cylinder that forms a cylindrical compression chamber, a cylindrical piston, and a connecting rod as a compression mechanism.
  • the piston reciprocates in the cylinder.
  • the connecting rod connects the eccentric shaft portion of the shaft to the piston via a piston pin.
  • the shaft is fixed to the axis of the rotor of the electric motor unit, and the compression mechanism is activated by the rotation of the rotor.
  • Such a hermetic compressor requires a gap between the inner peripheral surface of the cylinder and the sliding surface of the piston so that both of them slide.
  • this gap is large, blow-by in which high-temperature and high-pressure refrigerant gas compressed in the compression chamber leaks occurs, and the compression efficiency decreases.
  • this gap is reduced, sliding loss increases and input / output efficiency decreases.
  • FIG. 16A shows a state where the piston is at bottom dead center
  • FIG. 16B shows a state where the piston is at top dead center.
  • the cylinder block 14 has a cylinder 16 having a central axis in a substantially horizontal direction.
  • the piston 23 inserted in a substantially horizontal direction is connected to a connecting rod 26 via a piston pin (not shown) to constitute a piston assembly 23A.
  • a valve plate (not shown) is attached to the end face (right end face in the figure) opposite to the cylinder 16 when viewed from the connecting rod 26.
  • the compression chamber 15 is formed by the piston 23, the cylinder 16 and the valve plate configured as described above.
  • the piston 23 reciprocates in the cylinder 16 through the connecting rod 26 in a substantially horizontal direction by an eccentric movement of an eccentric shaft portion (not shown) of a shaft (not shown).
  • the inner surface of the cylinder 16 has a tapered portion 17 whose inner diameter increases from Dt to Db (> Dt) from the middle of the side where the piston 23 is located at the top dead center toward the side located at the bottom dead center. Is formed.
  • the piston 23 has substantially the same outer diameter dimension over the entire length. Therefore, in the vicinity of the top dead center where the pressure in the compression chamber 15 is high, the gap of the seal portion of the piston 23 is reduced to prevent blow-by. On the other hand, since the gap increases near the bottom dead center, the sliding loss can be reduced.
  • the piston 23 configured as described above repeats reciprocating motion while slightly vibrating vertically and horizontally within the gap with the inner surface of the cylinder 16 at all times. This is because, during operation, the piston 23 is subjected to dynamic compression load, inertial force of movable members such as the piston 23 and connecting rod 26, and piston side pressure load generated by converting gravity and rotary motion into reciprocating motion. It is. In addition, forces such as sliding resistance of the sliding portion influence each other and act on the piston 23 while changing the direction and size. Such an action also causes the piston 23 to vibrate slightly vertically and horizontally within the gap with the inner surface of the cylinder 16.
  • the gap between the cylinder 16 and the tapered portion 17 is larger than the gap near the top dead center.
  • the central axis of the cylinder 16 is arranged in a substantially horizontal direction, the bottom dead center side of the piston 23 is tilted in the direction in which the piston 23 is lowered in the vertical downward direction under the influence of the gravity of the piston assembly 23A.
  • the connecting rod 26 side of the piston 23 is inclined further vertically downward.
  • the fine vibration behavior is generated by the reciprocating motion of the piston 23 and the pressure applied to the piston 23, so that the piston 23 and the taper portion 17 of the cylinder 16 cause local rubbing in the sliding portion of the piston 23. appear. Such local rubbing may cause contact noise, or may cause wear starting from the contact portion.
  • the structure in which the pistons 23 are all disposed inside the cylinder 16 when in the position of the bottom dead center relatively improves the stability of the behavior at the tapered portion 17 of the cylinder 16.
  • the compression mechanism is necessarily increased in size.
  • the whole hermetic compressor becomes large.
  • the present invention avoids local contact between the piston and the inner surface of the cylinder (cylindrical hole), and at the same time minimizes the sliding area, and generates noise and wear due to contact between the piston and the cylinder. It is a hermetic compressor that prevents local contact that is the cause of the noise and improves noise prevention and efficiency and reliability.
  • the hermetic compressor of the present invention has a hermetic container, an electric mechanism, and a compression mechanism.
  • the sealed container stores lubricating oil at the bottom.
  • the electric mechanism and the compression mechanism are disposed in the sealed container.
  • the electric mechanism drives the compression mechanism.
  • the compression mechanism includes a shaft, a cylinder block, a piston, and a connecting rod.
  • the shaft includes a main shaft portion that is rotationally driven by an electric mechanism, and an eccentric shaft portion formed on the main shaft portion.
  • the cylinder block has a cylindrical hole portion that constitutes a compression chamber, and a bearing portion that rotatably supports the main shaft portion. The cylindrical hole portion and the bearing portion are disposed so that their axis centers are orthogonal to each other.
  • the piston has a sliding surface that slides on the inner wall of the cylindrical hole, and is inserted into the cylindrical hole so as to reciprocate.
  • the connecting rod connects the eccentric shaft portion and the piston.
  • the cylindrical hole portion has a tapered portion whose inner diameter dimension gradually increases in the direction from the top dead center to the bottom dead center, and an end portion on the shaft side.
  • the reciprocating direction of the piston is substantially horizontal.
  • the sliding surface of the piston is provided with a recess that is recessed inward of the piston in the radial direction and holds lubricating oil. Further, when the piston is located at the bottom dead center, the part on the lower side in the vertical direction where the piston contacts the end of the cylindrical hole on the shaft side is a part of the sliding surface.
  • the sliding resistance of the piston can be reduced by reducing the average gap and the sliding area by the tapered portion in the cylindrical hole and the recess provided in the piston. Further, in the vicinity of the bottom dead center of the piston, the concave portion of the piston does not protrude from the end of the cylindrical hole on the shaft side. Therefore, local collision between the edge of the concave portion of the piston and the cylinder block can be avoided without causing an excessive inclination of the piston. Therefore, it is possible to suppress the occurrence of collision noise and prevent an increase in noise. Further, by holding a large amount of the lubricating oil scattered and supplied from the shaft in this recess, it is possible to supply the lubricating oil abundantly between the inner surface of the cylindrical hole and the piston surface. As a result, the lubricity and sealing performance between the cylinder and the piston are improved, so that the compression efficiency is improved. In addition, the overall length of the cylindrical hole is short.
  • FIG. 1 is a cross-sectional view of a main part of a hermetic compressor prior to Embodiment 1 of the present invention.
  • FIG. 2 is a longitudinal sectional view of an essential part of another hermetic compressor prior to the first embodiment of the present invention.
  • FIG. 3 is a top view of the main part of the hermetic compressor shown in FIG.
  • FIG. 4 is a sectional view showing a state where the piston of the hermetic compressor according to Embodiment 1 of the present invention is located at the bottom dead center.
  • FIG. 5 is a sectional view showing a state where the piston of the hermetic compressor shown in FIG. 4 is located at the top dead center.
  • 6 is a bottom view of the piston of the hermetic compressor shown in FIG. FIG.
  • FIG. 7 is a cross-sectional view of the compression portion showing a state where the piston of the hermetic compressor shown in FIG.
  • FIG. 8 is a cross-sectional view of the compression portion showing a state where the piston of the hermetic compressor according to Embodiment 2 of the present invention is located at the bottom dead center.
  • FIG. 9 is a cross-sectional view showing a state where the piston is located at the top dead center of the compression section shown in FIG.
  • FIG. 10 is a longitudinal sectional view of the piston assembly of the hermetic compressor according to the second embodiment of the present invention.
  • FIG. 11 is a partial top cross-sectional view of the compression section showing a state where the piston of the hermetic compressor according to Embodiment 2 of the present invention is in the compression stroke.
  • FIG. 12 is a characteristic diagram of the piston side pressure load with respect to the crank angle of the hermetic compressor according to the second embodiment of the present invention.
  • FIG. 13 is a characteristic diagram of the coefficient of performance with respect to the spatial volume of the concave portion of the hermetic compressor according to the second embodiment of the present invention.
  • FIG. 14 is a characteristic diagram of coefficient of performance with respect to the distance between the recesses of the hermetic compressor according to the second embodiment of the present invention.
  • FIG. 15 is a characteristic diagram of the coefficient of performance with respect to the operating frequency of the hermetic compressor according to the second embodiment of the present invention.
  • FIG. 16A is a longitudinal cross-sectional view of a compression unit showing a state where a piston of a conventional hermetic compressor is located at a bottom dead center.
  • FIG. 16B is a longitudinal sectional view of the compression unit showing a state where the piston shown in FIG. 16A is located at the top dead center.
  • FIG. 1 is a cross-sectional view of the main part of the hermetic compressor, showing a state where the piston 123 is at the bottom dead center.
  • the surface of the piston 123 is provided with thin annular grooves 141A and 141B and a concave portion 141C that is recessed radially inward.
  • the inner diameter of the cylindrical hole 116 is substantially constant.
  • the lower end portion 123B and the concave portion 141C of the piston 123 are exposed from the cylindrical hole portion 116.
  • the grooves 141 ⁇ / b> A and 141 ⁇ / b> B are partially exposed from a notch 114 ⁇ / b> A provided in the cylinder block 114.
  • FIG. 2 is a longitudinal sectional view of a main part of the hermetic compressor assuming the above-described combination.
  • FIG. 2 shows a state where the piston is at the bottom dead center.
  • FIG. 3 is a top view of the main part of the hermetic compressor shown in FIG. 2 in a state where the piston is in the compression stroke.
  • the cylindrical hole 216 has a straight part 218 and a tapered part 217.
  • the inner diameter of the cylindrical hole portion 216 is substantially constant.
  • the inner diameter dimension changes from Dt to Db (> Dt) from the middle of the side where the piston 223 is located at the top dead center (right side in the figure) toward the side located at the bottom dead center (left side in the figure). It has increased.
  • the gap between the piston 223 and the tapered portion 217 is large near the bottom dead center and small near the top dead center.
  • grooves 241A and 241B and a concave portion 241C recessed in the radial direction are provided on the surface of the piston 223. At the position near the bottom dead center, the lower end 223B and the recess 241C of the piston 223 are exposed from the inside of the cylindrical hole 216. The grooves 241A and 241B are partially exposed from the notch 214A provided in the cylinder block 214.
  • the seal portion of the piston 223 prevents blow-by due to the reduction of the gap near the top dead center and the labyrinth seal effect by the grooves 241A and 241B. Further, the concave portion 241C holds the lubricating oil scattered near the bottom dead center, and the lubricating oil is supplied from the concave portion 241C to the sliding portions of the grooves 241A and 241B and the piston 223. As the oil supply amount increases in this way, the sealing performance and lubricity can be improved.
  • the piston 223 is exposed from the tapered portion 217 of the cylindrical hole 216 near the bottom dead center.
  • the piston 223 has a sliding portion of the piston 223 inserted in the cylindrical hole portion 216 as a fulcrum, and the fulcrum supports the weight of the piston 223, a piston pin (not shown) and the connecting rod 226. It has a support structure. This is because the clearance of the connecting portion between the connecting rod 226 and the eccentric shaft (not shown) of the crankshaft and the clearance of the connecting portion between the bearing and the crankshaft (none of which are shown) are the clearances between the seal portions of the piston 223. This is because it is larger than
  • the bottom dead center where the piston 223 is most exposed from the cylindrical hole 216 the bottom dead center side of the piston 223 is vertically downward within the gap formed by the tapered portion 217 and the piston 223. Tilt in the direction to go down. This is because the inner diameter of the cylindrical hole 216 is formed to have a tapered portion 217 that increases from Dt to Db, so that the gap between the tapered portion 217 and the piston 223 is increased in the vicinity of the bottom dead center. Due to that.
  • the support length of the sliding portion that cantilever-supports the piston 223 can be secured long as indicated by L1 in FIG.
  • the recess 241C is formed, the inclination of the piston 223 increases by the amount of the recess of the recess 241C.
  • the support length of the sliding portion that cantilever-supports the piston 223 is shortened as indicated by L2 in FIG.
  • FIG. 4 is a cross-sectional view showing a state where the piston of the hermetic compressor according to Embodiment 1 of the present invention is located at the bottom dead center.
  • FIG. 5 is a cross-sectional view showing a state where the piston of the hermetic compressor is located at the top dead center.
  • FIG. 6 is a bottom view of the piston of the hermetic compressor.
  • FIG. 7 is a cross-sectional view of the compression portion showing a state where the piston is tilted and located at the bottom dead center.
  • this hermetic compressor includes a hermetic container 301, an electric mechanism 304, and a compression mechanism 305.
  • the sealed container 301 stores lubricating oil 306 at the bottom.
  • the electric mechanism 304 includes a stator 302 and a rotor 303 and is disposed in the sealed container 301.
  • the compression mechanism 305 is also disposed in the sealed container 301 and is driven by the electric mechanism 304.
  • the compression mechanism 305 includes a shaft 310, a cylinder block 314, a piston 423, and a connecting rod 326.
  • the shaft 310 includes a main shaft portion 311 that is rotationally driven by the electric mechanism 304, and an eccentric shaft portion 312 that is formed eccentric to one end of the main shaft portion 311.
  • the main shaft portion 311 is fixed to the shaft center of the rotor 303.
  • An oil supply passage 313 is provided in the shaft 310 and on the outer peripheral surface, and one end of the oil supply passage 313 is formed to extend in the axial direction at the eccentric shaft portion 312.
  • the oil supply passage 313 communicates with an oil supply passage (not shown) opened at the upper end of the eccentric shaft portion 312.
  • an oil supply passage (not shown) opened at the upper end of the eccentric shaft portion 312.
  • a branched oil passage (not shown) branched from the oil supply passage 313 in the radial direction and opened.
  • the lower end of the main shaft portion 311 extends so that the other end of the oil supply passage 313 is immersed in the lubricating oil 306 at a predetermined depth.
  • the cylinder block 314 has a substantially cylindrical cylindrical hole 316 constituting the compression chamber 315 and a bearing 320 that rotatably supports the main shaft 311.
  • the cylindrical hole portion 316 and the bearing portion 320 are disposed so as to be fixed to each other at a fixed position.
  • the cylindrical hole portion 316 and the bearing portion 320 are arranged so that their axial centers are orthogonal to each other.
  • the bearing portion 320 forms a cantilever bearing by pivotally supporting the end portion on the eccentric shaft portion 312 side of the main shaft portion 311 of the shaft 310.
  • the cylinder block 314 is provided with a notch 319 in the upper wall where the lubricating oil 306 falls on the peripheral wall of the cylindrical hole 316.
  • the piston 423 is inserted into the cylindrical hole 316 so as to be able to reciprocate, and has a sliding surface 423C that slides on the inner wall of the cylindrical hole 316 as shown in FIG.
  • the reciprocating direction of the piston 423 is substantially horizontal.
  • the connecting rod 326 connects the eccentric shaft portion 312 and the piston 423. That is, one end of the connecting rod 326 is connected to the eccentric shaft portion 312 and the other end is connected to the piston 423 through the piston pin 425 inserted into the piston pin hole 423A as shown in FIG.
  • the connecting rod 326 and the piston 423 constitute a piston assembly 440.
  • the piston 423 is provided with a piston pin hole 423A in a direction orthogonal to the axis of the piston 423.
  • the compression mechanism 305 has a piston pin 425 inserted into the piston pin hole 423A.
  • the connecting rod 326 is connected to the piston pin 425 so as to be rotatable about the axis of the piston pin 425.
  • the cylindrical hole 316 and the piston 423 will be described in detail with reference to FIGS.
  • the axial dimension of the cylindrical hole 316 is such that the end of the cylindrical hole 316 on the shaft 310 side from the end surface 316A of the piston 423 on the connecting rod 326 side.
  • the part is set to protrude.
  • the inner surface of the cylindrical hole 316 includes a straight portion 318 having a constant inner diameter dimension in the axial direction for a predetermined length L from the top dead center side, and a bottom dead center.
  • a taper portion 317 whose inner diameter increases from Dt to Db (> Dt) toward the side is formed. That is, the cylindrical hole portion 316 has a tapered portion 317 whose inner diameter dimension gradually increases in the direction in which the piston 423 moves from the top dead center to the bottom dead center.
  • the cylindrical hole 316 has an end surface 316A that is an end on the shaft 310 side.
  • the boundary between the straight portion 318 and the taper portion 317 is the starting point of the taper portion 317, and is the inflection portion 317A having a large taper angle change rate.
  • the outer diameter of the piston 423 is formed to the same dimension over the entire length. That is, it is not tapered.
  • On the outer peripheral surface (sliding surface 423C) of the piston 423 a plurality of concave portions 441A, 441B, 4411C, and 4412C are provided.
  • the recesses 441A and 441B close to the compression chamber 315 are formed in an annular shape that goes around the outer periphery of the piston 423, each space volume is formed at 6 mm 3, and the distance between them is set at 2 mm.
  • the recesses 4411C and 4412C farthest from the compression chamber 315 are not annular.
  • the recesses 4411C and 4412C are formed mainly for the purpose of reducing the contact area with the cylindrical hole 316 of the piston 423 and holding the lubricating oil 306. Since the recesses 4411C and 4412C hold the lubricating oil 306, the sliding surface of the piston 423 with the cylindrical hole 316 can be lubricated. Therefore, if it is necessary to make the piston 423 lighter, the recesses 4411C and 4412C may be formed deeper or wider.
  • FIG. 6 shows the recess 4412C as a representative, but the recess 4411C has the same shape.
  • the outline of the recess 4412C extends from the portion parallel to the recesses 441A and 441B to the end 423B side on the connecting rod 326 side while gradually narrowing the width, and the end portion is formed in a shape extending to the compression chamber 315 side. Yes.
  • the recesses 4411C and 4412C are formed symmetrically about the axis X passing through the center of the piston pin hole 423A as shown in FIG. 6, and the terminal portion extends to the piston pin hole 423A. Accordingly, the recesses 4411C and 4412C are provided so as to surround the piston pin hole 423A, and an extension portion 423D extending to the inside of the recesses 4411C and 4412C is formed in the end portion 423B. The extending portion 423D forms a part of the end portion 423B of the piston 423. In this way, the recesses 4411C and 4412C are formed so as to be recessed inward in the radial direction of the piston 423, and hold the lubricating oil 306.
  • the space volume formed by the inner surface (straight part 318) of the cylindrical hole 316 of the recesses 4411C and 4412C is formed to be 6 mm 3 or more. However, since the concave portions 4411C and 4412C do not face the straight portion 318, a virtual state is assumed.
  • An interval of 1.5 mm is provided between the recess 441B and the deepest portion of the recesses 4411C and 4412C as a base point. As described above, the volumes of the recesses 4411C and 4412C can be arbitrarily set.
  • the recesses 4411C and 4412C are provided so as to surround the piston pin hole 423A. Therefore, it communicates with the piston pin hole 423A. That is, the recesses 4411C and 4412C are a first recess and a second recess formed at positions symmetrical to the axis X of the piston 423 passing through the center of the piston pin hole 423A. The recesses 4411C and 4412C communicate with each other through the piston pin hole 423A.
  • the cross-sectional angle of the edge 442 of the recesses 4411C and 4412C is formed on an inclined surface of about 30 °.
  • the recesses 4411C and 4412C are provided at positions that are symmetrical about the axis X on the surface of the piston 423. In this case, although it is not necessary to provide the extended portion 423D in the concave portion 4411C, it is not necessary to confirm the vertical direction of the piston 423 at the time of assembling, and workability is improved.
  • the piston 423 is assembled as the compression mechanism 305 by forming the piston assembly 440 when the piston pin 425 inserted into the piston pin hole 423A penetrates the connecting rod 326.
  • the extending portion 423D is disposed on the lower surface as shown in FIG.
  • the extending portion 423D faces (abuts) the corner of the end surface 316A of the cylindrical hole portion 316.
  • the dimensional relationship between the piston 423 and the end surface 316A on the connecting rod 326 side in the cylindrical hole 316 is set to be in such a state. That is, when the piston 423 is located at the bottom dead center, the portion on the lower side in the vertical direction where the piston 423 contacts the end surface 316A which is the end of the cylindrical hole 316 on the shaft 310 side is a part of the sliding surface 423C. It is the extension part 423D which is.
  • the hermetic compressor configured as described above will be described below.
  • the electric mechanism 304 When the electric mechanism 304 is energized, the rotor 303 of the electric mechanism 304 rotates the shaft 310, and the rotational movement of the eccentric shaft portion 312 is converted into a reciprocating movement via the connecting rod 326 and transmitted to the piston 423.
  • the piston 423 inserted into the cylindrical hole 316 (compression chamber 315) of the cylinder block 314 reciprocates within the cylindrical hole 316. Due to the reciprocating motion of the piston 423, the refrigerant gas is sucked into the compression chamber 315 from the cooling system (not shown), compressed, and then discharged to the cooling system again.
  • the lower end portion of the oil supply passage 313 functions as a pump using centrifugal force by the rotation of the shaft 310. Due to this pumping action, the lubricating oil 306 at the bottom of the sealed container 301 is pumped upward through the oil supply passage 313, and is ejected in the respective directions from the oil supply passage and the branch oil passage provided in the eccentric shaft portion 312. Scatter.
  • the lubricating oil 306 ejected from the oil supply passage collides with the ceiling surface of the sealed container 301 and scatters to mainly cool the compression mechanism 305 and lubricate the sliding portion, and also lubricates the lubricating oil 306 from the branch oil passage. Is scattered substantially horizontally in the entire circumferential direction in the sealed container 301 and is mainly supplied to the piston pin 325, the piston 423, and the like to lubricate the sliding portion.
  • blow-by hardly occurs and the sliding resistance of the piston 423 is small.
  • the pressure in the compression chamber 315 further increases immediately before the piston 423 reaches a position near the top dead center. Since the gap between the sliding surface 423C of the piston 423 and the tapered portion 317 is reduced on the top dead center side, the occurrence of blow-by can be reduced.
  • the lubricating oil 306 is formed in the concave portion 4411C formed in the sliding surface 423C of the piston 423 from the notch 319 provided in the upper wall of the cylindrical hole 316. , 4412C are supplied and held abundantly. A part of the lubricating oil 306 is supplied to and held in the recesses 441A and 441B. Therefore, even when the piston 423 moves to the straight portion 318 having a narrow gap, more lubricating oil is supplied to the sliding portion formed by the piston 423 and the straight portion 318. Therefore, this lubricating oil lubricates and seals the sliding portion. As a result, the occurrence of gas leakage can be prevented and the volume efficiency can be improved.
  • the cylindrical hole portion 316 has a straight portion 318 provided on the top dead center side of the piston 423 with respect to the taper portion 317.
  • the seal portion of the piston 423 in the vicinity of the top dead center where the pressure increases most in the compression stroke can be formed in the straight portion 318 having a constant inner diameter dimension in the axial direction.
  • the axial distance of the minimum gap between the piston 423 and the cylindrical hole portion 316 is increased, the effect of preventing the occurrence of gas leakage accompanying the increase in the pressure of the refrigerant gas is great.
  • the radial gap is wide, so that the sliding loss is also reduced. As a result, high efficiency can be achieved.
  • the edge 442 of the recesses 4411C and 4412C as an inclined surface, the wedge film action of the lubricating oil 306 can be obtained, and an oil film can be reliably formed in the gap between the piston 423 and the cylindrical hole 316. .
  • the bottom dead center side of the piston 423 tilts vertically downward within the gap between the cylindrical hole 316 and the piston 423.
  • the extending portion 423D is in contact with the corner of the end surface 316A of the cylindrical hole portion 316. Therefore, the edge 442 does not shift vertically downward from the cylindrical hole 316 and collide with the lower corner of the end surface 316A due to the inclination of the piston assembly 440 due to its own weight. Therefore, the generation of collision noise can be suppressed and noise reduction can be achieved.
  • the connecting rod 326 is connected to the piston pin 425 so as to be rotatable around the axis of the piston pin 425. Therefore, the piston 423 does not rotate around the axis, and the extending portion 423D reliably contacts the corner of the end surface 316A.
  • the lubricating oil 306 splashed in the vicinity of the bottom dead center of the piston 423 forms a circulation path and cools the piston 423. Due to this cooling, the temperature of the piston 423 is lowered, and accordingly, a rise in the temperature of the compression chamber 315 is suppressed, and a decrease in volumetric efficiency due to heat reception is prevented.
  • the inverter when the inverter is driven at an operating frequency lower than the power supply frequency, the oil retention is maintained by the capillary phenomenon of the recesses 441A and 441B, the labyrinth effect vortex is formed, and the leakage flow in the refrigerant gas passes through the recesses 441A, 441B, 4411C, and 4412C.
  • the leakage of the refrigerant can be suppressed by a synergistic effect such as the formation of a deceleration flow accompanying the.
  • FIG. 8 is an enlarged cross-sectional view of the compression unit showing a state where the piston of the hermetic compressor according to Embodiment 2 of the present invention is located at the bottom dead center.
  • FIG. 9 is an enlarged cross-sectional view of the compression portion showing a state where the piston is located at the top dead center.
  • FIG. 10 is a longitudinal sectional view of the piston assembly of the hermetic compressor according to the present embodiment.
  • FIG. 11 is a top view of the compression section showing a state where the piston of the hermetic compressor in the present embodiment is in the compression stroke.
  • FIG. 12 is a characteristic diagram of piston side pressure load with respect to the crank angle of the hermetic compressor in the present embodiment.
  • the overall configuration of the compressor will be described mainly with reference to the description of the first embodiment (including reference numerals) and FIGS. 4 and 5, and the contents different from the first embodiment.
  • the part different from the first embodiment is the configuration of the recess provided in the piston, and the other configuration is the same as that of the first embodiment. Therefore, here, a description will be given mainly of pistons having different configurations.
  • the outer diameter of the piston 323 is formed to have the same dimension over the entire length, and three concave portions 341A, 341B, and 341C are provided on the surface thereof at a predetermined interval.
  • the recesses 341A, 341B, and 341C are all formed in an annular shape that goes around the circumference on the surface of the piston 323.
  • the space volume formed by the inner surface (straight portion 318) of the cylindrical hole 316 of the recess 341A formed at the position closest to the compression chamber 315 and the recess 341B at the second position is set to 6 mm 3 respectively. Has been. Further, the interval between the recess 341A and the recess 341B is set to 2 mm.
  • a space volume formed by the inner surface (straight portion 318) of the cylindrical hole 316 of the concave portion 341C at the third position is formed to be 6 mm 3 or more. However, since the concave portion 341C does not face the straight portion 318, a virtual state is assumed.
  • An interval of 1.5 mm is provided between the recess 341C and the recess 341B with the deepest portion of the recess 341C as a base point.
  • a part of the recess 341C communicates with the piston pin hole 323A.
  • the recess 341C is formed for the same purpose as the recesses 4411C and 44112C of the first embodiment. Therefore, the volume of the recess 341C can be set arbitrarily.
  • the end 323B of the piston 323 on the side opposite to the compression chamber has a length A longer than the end surface 316A on the shaft side of the cylinder block 314 as shown in FIG. Exposed.
  • the piston 323 is formed in such a dimension.
  • the axial dimension of the cylindrical hole 316 is set so that the corner of the end surface 316A of the cylindrical hole 316 contacts the end 323B when the piston 323 is located at the bottom dead center.
  • the end 323B is an outer peripheral surface between the end of the piston 323 on the connecting rod 326 side and the annular recess 341C.
  • the cylinder block 314 is provided with a notch 319 in the upper wall where the lubricating oil 306 falls on the peripheral wall of the cylindrical hole 316 as in the first embodiment.
  • the notch 319 exposes at least the recess 341C in a state where the piston 323 is located at the bottom dead center.
  • the concave portion 341C is defined as a part of the concave portion in the configuration in which the plurality of concave portions 341A, 341B, and 341C are provided.
  • all of the recesses 341 ⁇ / b> C are located on the top dead center side by a length B from the end surface 316 ⁇ / b> A of the cylindrical hole 316 when the piston 323 has reached the bottom dead center position. It is formed as follows. Further, the end surface 323C on the compression chamber 315 side of the piston 323 is positioned on the tapered portion 317 side by a distance of length C. Furthermore, as shown in FIG. 10, the edge 342 of the recess 341 ⁇ / b> C has a shape inclined at approximately 30 ° in the cross section.
  • FIG. 11 shows the arrangement of the pistons 323 when the crank angle is 320 degrees in the compression stroke.
  • This crank angle 320 deg is an angle at which the side pressure load of the piston 323 becomes maximum as shown in FIG.
  • This maximum side pressure load acts on the side pressure load sliding portion on the horizontal side surface of the cylindrical hole 316.
  • the inflection part 317A of the straight part 318 and the taper part 317 is located within the range of the width of the concave part 341C of the piston 323.
  • the clearance between the piston 323 and the straight portion 318 of the cylindrical hole 316 is greatly shown in order to make it easy to understand that the inflection portion 317A is located within the width of the recess 341C. ing.
  • the hermetic compressor configured as described above will be described below.
  • the rotor 303 of the electric mechanism 304 rotates the shaft 310, and the rotational movement of the eccentric shaft portion 312 is converted into a reciprocating movement via the connecting rod 326 and transmitted to the piston 323.
  • the piston 323 reciprocates in the cylindrical hole 316.
  • the inflection portion 317A having a large taper angle change rate which is the starting point of the taper portion 317, is located within the range of the width of the recess 341C of the piston 323.
  • the inflection portion 317A is separated from the bottom of the concave portion 341C even when facing the concave portion 341C. Therefore, even if the lateral pressure load becomes large, the lubrication state is lowered at the inflection portion 317A where it is difficult to form an oil film, and no sliding noise is generated due to local rubbing.
  • the compression stroke further proceeds, the pressure of the refrigerant gas in the compression chamber 315 gradually increases, and the pressure in the compression chamber 315 further increases immediately before the piston 323 reaches a position near the top dead center shown in FIG. To do. Since the gap between the sliding surface of the piston 323 and the tapered portion 317 is reduced on the top dead center side, occurrence of blow-by can be reduced. At this time, the straight portion 318 formed in the cylindrical hole portion 316 reduces the leakage of the refrigerant gas that has increased to a predetermined discharge pressure as compared with the taper portion 317.
  • the connecting rod 326 side of the piston 323 is formed to be exposed from the cylinder block 314.
  • the lubricating oil 306 scattered from the upper end of the shaft 310 is abundantly supplied from the notch 319 provided on the upper wall of the cylindrical hole 316 to the recess 341C formed on the sliding surface of the piston 323.
  • a part of the lubricating oil 306 is supplied to the recesses 341A and 341B.
  • the amount of lubricating oil supplied to the gap between the inner peripheral surface of the cylindrical hole 316 of the cylinder block 314 and the sliding surface of the piston 323 increases during the compression stroke.
  • the end surface 323C on the compression chamber side of the piston 323 is positioned on the taper portion 317 side at the bottom dead center by a distance of the length C in FIG. Therefore, when the piston 323 moves from the bottom dead center to the top dead center in the compression stroke, a part of the lubricating oil 306 adhering to the surface of the piston 323 moves to the top dead center side, and the surface of the cylindrical hole 316 A part of the lubricating oil 306 adhering to is also supplied by being caught in the gap between the piston 323 and the cylindrical hole 316 as the piston 323 moves.
  • the end surface of the piston 323 on the compression chamber 315 side is configured to be positioned at the tapered portion 317. Therefore, the gap between the piston 323 and the cylindrical hole 316 is larger than that when the piston 323 is positioned on the straight portion 318. Therefore, the amount of the lubricating oil 306 held in the gap space is also large.
  • the concave portion 341C is provided in an annular shape on the sliding surface of the piston 323, for example, the width of the concave portion 341C is increased in the axial direction of the piston 323 to maximize the area of the concave portion 341C. Is possible.
  • the sliding area between the cylindrical hole 316 (compression chamber 315) and the piston 323 can be reduced to the maximum, and the sliding resistance can be reduced. Further, the lubricating oil 306 can be supplied uniformly and stably to the lubricating portion and the sealing portion of the entire circumference of the piston 323. Therefore, it is possible to prevent poor lubrication and deterioration of sealing performance due to uneven and unstable oil supply.
  • the edge 342 of the recess 341C is configured by a surface inclined at about 30 ° with respect to the axial surface of the piston 323 in the cross-sectional shape. Therefore, when the piston 323 reciprocates, the lubricating oil 306 held in the recess 341C is urged in the recess 341C. Then, it is drawn into the gap between the piston 323 and the cylindrical hole 316 along the inclination of the edge 342 of the recess 341C, and acts to correct the inclination of the piston 323 by entering the gap. Thus, a so-called wedge film action occurs in the gap between the piston 323 and the cylindrical hole 316.
  • the wedge film effect by the lubricating oil 306 corrects the inclination of the piston 323 to be small, and acts so that the gap with the cylindrical hole 316 on the entire circumference of the piston 323 becomes uniform. Therefore, the lubricating oil 306 is easily carried to the sliding portion and the seal portion near the top dead center where the gap is formed narrow, and the frequency of local metal contact that is unavoidable can be reduced.
  • the angle of the edge 342 of the recess 341C is not limited to about 30 °.
  • the lubricating oil 306 held in the recess 341C may be at an angle at which a wedge film action is likely to be drawn into the gap between the piston 323 and the cylindrical hole 316. . That is, the angle of the edge 342 may be set as appropriate according to the reciprocating speed of the piston 323 and the like. In the present embodiment, the angle of the edge 342 with respect to the axial surface of the piston 323 is preferably in the range of 25 ° to 35 °.
  • the lubricating oil 306 held in the recess 341C is set to an angle that is drawn into the gap between the piston 323 and the cylindrical hole 316. Good.
  • a larger amount of lubricating oil 306 can be supplied between the cylinder block 314 and the piston 323, and the lubricating oil 306 can be held well and the sealing performance can be improved. Furthermore, with the supply of the abundant lubricating oil 306, the sliding resistance of the piston 323 can be reduced, thereby improving the compression efficiency, reducing the input, and achieving high efficiency.
  • This configuration may be applied to the recesses 4411C and 4412C of the first embodiment.
  • the connecting rod side edge 342 of the recess 341C is located on the top dead center side of the end surface 316A of the cylindrical hole 316.
  • the corners of the end portion 323B of the piston 323 and the end surface 316A of the cylindrical hole portion 316 are in contact with each other. Therefore, the edge 342 of the concave portion 341C is not shifted vertically downward from the cylindrical hole portion 316 and does not collide with the lower corner of the end surface 316A due to the inclination by the own weight of the piston assembly 340. Therefore, the generation of collision noise can be suppressed and noise reduction can be achieved.
  • a part of the recess 341C communicates with the piston pin hole 323A. That is, it is preferable that the upper side and the lower side of the recess 341C communicate with each other through the piston pin hole 323A.
  • the lubricating oil 306 splashed and supplied to the upper portion of the piston 323 near the bottom dead center passes through the annular recess 341C and is discharged downward through the end surface of the piston pin hole 323A.
  • the piston 323 heated by the high-temperature and high-pressure refrigerant gas is cooled by the lubricating oil 306 having a relatively low temperature passing through the circulation path. By this cooling, the temperature of the piston 323 is lowered, and accordingly, the temperature rise of the compression chamber 315 is suppressed, and the volumetric efficiency can be prevented from being lowered due to heat reception.
  • the inverter when the inverter is driven at an operation frequency equal to or lower than the power supply frequency, particularly in a low speed operation of 30 r / sec or less, the reciprocating motion speed of the piston 323 becomes slow, and the lubricating oil supplied by the pump action of the shaft 310. The amount of refueling at 306 decreases. Therefore, the amount of the lubricating oil 306 sprayed from the eccentric shaft portion 312 into the sealed container 301 is reduced.
  • the lubricating oil 306 is stored mainly in the recess 341C and supplied to the seal portion.
  • the oil retaining property is maintained by the capillary phenomenon of the recesses 341A and 341B, and a labyrinth eddy current is formed. Further, after the leakage flow of the refrigerant gas passes through the recesses 341A, 341B, and 341C, a deceleration flow due to the contracted flow is formed.
  • Leakage of the refrigerant can be suppressed by a synergistic effect such as the formation of the vortex of the labyrinth effect and the formation of the deceleration flow by the contraction.
  • a synergistic effect such as the formation of the vortex of the labyrinth effect and the formation of the deceleration flow by the contraction.
  • the coefficient of performance is the ratio of the refrigerating capacity to the applied input, and is generally used as an index indicating the efficiency of the compressor.
  • R600a isobutane
  • the operating frequency is 27 r / sec.
  • the evaporation temperature is ⁇ 30 ° C. and the condensation temperature is 40 ° C.
  • FIG. 13 is a characteristic diagram of coefficient of performance with respect to the spatial volume of the recesses 341A and 341B.
  • FIG. 14 is a characteristic diagram of the coefficient of performance with respect to the distance between the adjacent recesses 341A, 341B, and 341C.
  • FIG. 15 is a characteristic diagram of coefficient of performance with respect to changes in the operating frequency of the compressor.
  • the vertical axis represents the coefficient of performance of the compressor
  • the horizontal axis represents the sum of the space volumes surrounded by the cross sections of the recesses 341A and 341B and the extended surface of the outer diameter of the piston 323.
  • test results shown in FIG. 13 are results obtained by defining the concave portion on the compression chamber 315 side as a plurality of concave portions 341A and 341B having a small cross-sectional area.
  • the present invention is not limited to a plurality of recesses, but may be one recess formed in a volume that can obtain the result shown in FIG.
  • the space volume of the recesses 341A and 341B is in a range T of 0.25 mm 3 to 25 mm 3 .
  • the vertical axis represents the coefficient of performance of the compressor
  • the horizontal axis represents the distance S between the adjacent recesses 341A, 341B, 341C.
  • the coefficient of performance increases by forming the distances between the recesses 341A, 341B, and 341C apart by 1 mm or more.
  • the gap between the surface of the piston 323 and the cylindrical hole 316 becomes an aperture by setting the mutual distance S between the adjacent recesses 341A, 341B, and 341C to 1 mm or more. Therefore, the flow rate of the mixed flow of the refrigerant gas and the lubricating oil 306 is increased, so that the mixed flow is depressurized.
  • the amount of leakage from the gap between the piston 323 and the cylindrical hole 316 is further reduced. The Therefore, by reducing the amount of leakage to the anti-compression chamber, the volumetric efficiency can be prevented from being reduced and the compressor efficiency can be increased.
  • the recesses 341A, 341B, 341C are formed such that the distance between the adjacent recesses 341A, 341B, 341C is 1 mm or more.
  • the vertical axis represents the coefficient of performance of the compressor
  • the horizontal axis represents the operating frequency at which the piston is driven.
  • a compressor having the same specifications as the present embodiment cylinder volume: 10 ml, 27 r / sec operation capacity: 74 W
  • the results are shown when the operation frequency is operated in the range of about 20 to about 45 r / sec.
  • the cylindrical hole portion has no taper portion
  • the piston has no recess 341C.
  • the coefficient of performance is greatly improved as compared with the conventional compressor when the operation frequency is low and the power consumption reduction effect is large in the cooling system such as a refrigerator. Therefore, it can be seen that the sealing performance between the piston 323 and the cylindrical hole 316 is remarkably improved, and the amount of leakage can be reduced.
  • the refrigeration capacity is small, and the ratio of leakage loss from the gap between the piston 323 and the cylindrical hole 316 is large with respect to the refrigeration capacity.
  • the amount of leakage from the gap between the piston 323 and the cylindrical hole 316 can be reduced due to the stable sealing and labyrinth effect by the lubricating oil 306. Therefore, it is possible to prevent an extremely low efficiency of the compressor due to a decrease in volumetric efficiency, and to greatly reduce the power consumption of the cooling system.
  • the hermetic compressor according to the present embodiment local contact between the piston 323 and the cylindrical hole 316 is avoided, and at the same time, the sliding area is minimized and the sliding loss is minimized. be able to.
  • the lubricating oil 306 that contributes to the sealing performance between the piston 323 and the cylindrical hole 316 is stably supplied between the piston 323 and the cylindrical hole 316, and between the piston 323 and the cylindrical hole 316. It is possible to secure with certainty.
  • the overall length of the cylindrical hole 316 is shortened, the hermetic compressor is reduced in size, the generation of contact noise is prevented, and the generation of wear is reduced. can do.
  • high efficiency, low noise, and high reliability of the hermetic compressor can be achieved.
  • This hermetic compressor can be widely applied to hermetic compressors used in equipment using a refrigeration cycle such as an air conditioner or a vending machine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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PCT/JP2010/006337 2009-10-27 2010-10-27 密閉型圧縮機 WO2011052195A1 (ja)

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WO2014115530A1 (ja) * 2013-01-22 2014-07-31 パナソニック株式会社 密閉型圧縮機および冷蔵庫

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JP2012082785A (ja) * 2010-10-14 2012-04-26 Panasonic Corp 圧縮機
CN105518299B (zh) * 2013-09-03 2019-06-21 松下电器制冷装置新加坡 密闭型压缩机和装载有该压缩机的冷藏库或制冷装置
WO2015047643A1 (en) * 2013-09-24 2015-04-02 Illinois Tool Works Inc. Compressor
WO2015129184A1 (ja) * 2014-02-25 2015-09-03 パナソニックＩｐマネジメント株式会社 密閉型圧縮機および冷凍装置
CN104165133A (zh) * 2014-09-03 2014-11-26 安徽美芝制冷设备有限公司 压缩机曲轴箱和具有其的压缩机
JP6781082B2 (ja) * 2017-03-10 2020-11-04 日立建機株式会社 アキシャルピストン式液圧回転機
JP7258710B2 (ja) * 2019-10-01 2023-04-17 ジーエムシーシー アンド ウェリング アプライアンス コンポーネント （タイランド） カンパニー リミテッド 圧縮機およびこれを用いた機器
CN114109773A (zh) * 2021-12-01 2022-03-01 宁波慕品电器科技有限公司 一种充气机芯
CN114962221B (zh) * 2022-06-09 2023-02-17 珠海格力电器股份有限公司 一种气缸组件及压缩机

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WO2014115530A1 (ja) * 2013-01-22 2014-07-31 パナソニック株式会社 密閉型圧縮機および冷蔵庫
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US20120183419A1 (en) 2012-07-19
JPWO2011052195A1 (ja) 2013-03-14

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