WO2013099237A1 - 密閉型圧縮機およびそれを備える冷蔵庫 - Google Patents
密閉型圧縮機およびそれを備える冷蔵庫 Download PDFInfo
- Publication number
- WO2013099237A1 WO2013099237A1 PCT/JP2012/008309 JP2012008309W WO2013099237A1 WO 2013099237 A1 WO2013099237 A1 WO 2013099237A1 JP 2012008309 W JP2012008309 W JP 2012008309W WO 2013099237 A1 WO2013099237 A1 WO 2013099237A1
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- WIPO (PCT)
- Prior art keywords
- rotor
- hermetic compressor
- bearing
- shaft
- balance weight
- Prior art date
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Classifications
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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
- F04B39/0094—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 crankshaft
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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
- F04B39/0027—Pulsation and noise damping means
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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
- F04B39/02—Lubrication
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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
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0238—Hermetic compressors with oil distribution channels
- F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
Definitions
- the present invention relates to a hermetic compressor and a refrigerator including the same, and more particularly to a hermetic compressor used in a heat pump cycle such as a refrigeration cycle and a refrigerator including the same.
- a hermetic compressor that compresses a working fluid with a piston to make it into a high-temperature and high-pressure state and discharges it to a heat pump cycle is known to have a reduced thickness and reduced vibration due to the piston.
- a recess is provided on the upper surface of the rotor, and the lower portion of the support frame is fitted in the recess.
- the support frame and the recess are overlapped and the length thereof is shortened, so that the hermetic compressor is thinned.
- the crankshaft is composed of a main body shaft, an eccentric plate portion formed at the upper end of the main body shaft, and an eccentric shaft provided on the eccentric plate portion.
- the main shaft of the crankshaft is rotatably inserted into the hole of the support frame, and the lower portion of the main shaft protrudes downward from the hole of the support frame and is fixed to the rotor.
- the eccentric shaft of the crankshaft protrudes upward from the support frame, and a balance weight is attached to the upper end portion thereof.
- a piston is connected to the eccentric shaft, and is inserted into the cylinder hole of the support frame. In such a hermetic compressor, when the rotor rotates, the eccentric shaft of the crankshaft rotates eccentrically, and the piston reciprocates within the cylinder hole.
- the above hermetic compressor employs a cantilever bearing structure in which only one end of the crankshaft is supported by a support frame. Further, since the lower portion of the support frame is fitted in the recess, the range in which the rotor and the crankshaft are fixed is narrow, and the rigidity of the fixed portion is low. In such a case, the vibration that causes the crankshaft to swing is transmitted to the rotor, and the vibration of the rotor is easily amplified. Therefore, the increase in vibration and noise in the hermetic compressor due to the vibration of the crankshaft becomes more remarkable. .
- the present invention has been made to solve such problems, and an object of the present invention is to provide a thin hermetic compressor capable of reducing vibration and noise and a refrigerator including the same.
- a hermetic compressor includes an electric element including a stator and a rotor that rotates with respect to the stator, and a compression element that is driven by the electric element disposed below.
- a cylinder block including a bearing rotatably supporting the main shaft inserted into the through-hole and a cylinder having a compression chamber formed therein.
- the cylinder block is coupled to the eccentric shaft, and the compression A piston that reciprocates in a room; and a crank weight attached to an upper portion of the eccentric shaft, wherein the rotor has a cylindrical shape including a cylindrical space therein, and a lower portion of the bearing is the cylindrical shape.
- the rotor has a cylindrical shape including a cylindrical space therein, and a lower portion of the bearing is the cylindrical shape.
- Sky An upper stage portion fitted in the inner stage, and a lower stage part having an inner diameter dimension smaller than the inner diameter dimension of the upper stage part, and a lower part of the main shaft that has passed through the through hole of the bearing is inserted and fixed in the cylindrical space.
- a balance weight disposed on the opposite side of the crank weight with respect to the piston.
- the present invention has the configuration described above, and has the effect of providing a thin hermetic compressor that can reduce vibration and noise and a refrigerator including the same.
- FIG. 3B is a cross-sectional view of the rotor taken along the broken line BB in FIG. 3A. It is the external view which looked at the rotor of FIG. 3A from the lower surface side. It is a figure which shows typically the force which acts on the shaft in the hermetic compressor of FIG. It is sectional drawing which shows the hermetic compressor which concerns on Embodiment 2 of this invention. It is a figure which shows typically the force which acts on the shaft in the hermetic compressor of FIG. It is sectional drawing which shows typically the refrigerator which concerns on Embodiment 3 of this invention.
- a hermetic compressor includes an electric element including a stator and a rotor that rotates with respect to the stator, and a compression element that is driven by the electric element disposed below.
- a cylinder block including a bearing rotatably supporting the main shaft inserted into the through-hole and a cylinder having a compression chamber formed therein.
- the cylinder block is coupled to the eccentric shaft, and the compression A piston that reciprocates in a room; and a crank weight attached to an upper portion of the eccentric shaft, wherein the rotor has a cylindrical shape including a cylindrical space therein, and a lower portion of the bearing is the cylindrical shape.
- the rotor has a cylindrical shape including a cylindrical space therein, and a lower portion of the bearing is the cylindrical shape.
- a balance weight disposed on the side opposite to the crank weight with respect to the piston.
- the hermetic compressor can be thinned. This also narrows the fixing range between the lower stage portion of the rotor and the lower portion of the main shaft, and the rigidity of this fixing portion decreases.
- the force and moment acting on the shaft by the eccentric shaft and the piston are applied to the crank weight and canceled by the balance weight, vibrations that cause the shaft to swing while tilting are prevented. Therefore, it is possible to prevent the vibration of the shaft from being transmitted to the rotor from the low-rigid fixed portion and amplify the vibration of the rotor, and to reduce the vibration and noise of the hermetic compressor.
- the height dimension of the upper stage portion may be 70% or more of the height dimension of the rotor. According to this configuration, the overlap between the rotor and the bearing fitted therein is increased, and the hermetic compressor is further reduced in thickness.
- the compression element may further include a thrust ball bearing disposed on a thrust surface of the bearing. According to this configuration, friction between the thrust surface of the bearing and the eccentric shaft of the shaft is suppressed by the thrust ball bearing, and vibration and noise due to this can be reduced.
- the balance weight may be less than or equal to one fifth of the crank weight. According to this configuration, since the mass of the balance weight is small, the centrifugal force of the balance weight is reduced. Therefore, the rotor can be prevented from being deformed by the centrifugal force of the balance weight, and the occurrence of vibration and noise due to the deformation can be reduced.
- the balance weight may be disposed on a lower surface of the rotor. According to this configuration, since the balance weight arranged on the lower surface is away from the piston and the crank weight, the unbalanced moment component can be canceled out with a small mass balance weight. Therefore, it is possible to prevent the occurrence of noise and vibration due to unbalanced moment components. Further, the lower stage portion fixed to the main shaft and the balance weight are provided at the lower part of the rotor, and these positions are close to each other. Thereby, deformation of the rotor can be prevented, and generation of vibration and noise due to this deformation can be prevented.
- the balance weight may be disposed on an upper surface of the rotor. According to this configuration, the balance weight disposed on the upper surface is separated from the oil surface of the lubricating oil stored at the bottom of the sealed container. For this reason, it is prevented that the balance weight is immersed in the lubricating oil and stirred to promote foaming of the working fluid dissolved in the lubricating oil. Therefore, it is possible to prevent the occurrence of noise due to the lubricating oil contained in the foamed working fluid.
- the balance weight may be attached to the rotor by a caulking pin. According to this configuration, the balance weight can be attached to the rotor at the same time that the laminate of the plurality of steel plates constituting the rotor is fixed by the caulking pin, and the productivity is excellent.
- a refrigerator according to an eighth aspect of the present invention includes the hermetic compressor according to any one of the first to seventh aspects. According to this configuration, the internal space of the refrigerator can be enlarged or the heat insulating wall of the refrigerator can be thickened by using a thin-type hermetic compressor, thereby improving usability and heat insulation. Moreover, the noise and vibration of the refrigerator can be reduced by the hermetic compressor in which vibration is suppressed.
- FIG. 1 is a cross-sectional view showing a hermetic compressor 100.
- a direction parallel to the axis of the main shaft 123 of the shaft 119 is referred to as a vertical direction (vertical direction), and a direction orthogonal to the vertical direction is referred to as a horizontal direction.
- the hermetic compressor 100 includes a compressor main body 105 and a hermetic container 101 that accommodates the compressor main body 105.
- the compressor body 105 is elastically supported by, for example, a suspension spring 107, and includes an electric element 111 and a compression element 117 driven by the electric element 111.
- Lubricating oil 103 and working fluid are sealed in the sealed container 101.
- the lubricating oil 103 is used to lubricate the operation of the compression element 117 and is stored at the bottom of the sealed container 101.
- As the working fluid for example, hydrocarbon-based R600a (isobutane) having a low global warming potential is used.
- a suction pipe (not shown) for sucking the working fluid and a discharge pipe 104 for discharging the working fluid.
- the sealed container 101 is provided with a power supply terminal 109 connected to the electric element 111.
- the electric element 111 has a stator 113 and a rotor 115 that rotates with respect to the stator 113, and, for example, a salient pole concentrated winding type DC brushless motor is used.
- the stator 113 is formed by arranging a plurality of components in a substantially cylindrical shape. Each component is obtained by winding a copper winding with an insulating material around a plurality of magnetic pole teeth of an iron core in which thin steel plates are laminated. This winding is continuous in all components, and both ends thereof are connected to the power supply terminal 109.
- the rotor 115 has a cylindrical shape having a cylindrical space inside, and is arranged inside the stator 113.
- the rotor 115 is divided into two stages in the longitudinal direction from the viewpoint of the inner diameter dimension, and the inner diameter dimension of the upper digging portion 116 is set larger than the inner diameter dimension of the lower mounting portion 115e.
- a balance weight 170 is attached to the lower surface of the rotor 115 and is disposed on the opposite side of the crank weight 126 with respect to the piston 133.
- the compression element 117 is disposed above the electric element 111 and has a shaft 119 driven by the electric element 111.
- the shaft 119 includes a cylindrical main shaft 123.
- the lower portion of the main shaft 123 is inserted into the cylindrical space of the rotor 115 and is shrink-fitted into the mounting portion 115e of the rotor 115. Further, the lower end portion of the main shaft 123 protrudes downward from the fixed rotor 115 and is immersed in the lubricating oil 103 at the bottom portion of the sealed container 101.
- the main shaft 123 is provided with an oil supply mechanism 128.
- Examples of the oil supply mechanism 128 include a communication hole 130 b provided in the main shaft 123, a centrifugal pump 130 provided in the communication hole 130 b, and a spiral groove 127 formed on the outer peripheral surface of the main shaft 123.
- the centrifugal pump 130 is a pump that pumps the lubricating oil 103 from the lower end opening 130a of the communication hole 130b to the upper end opening as the main shaft 123 rotates.
- the communication hole 130 b is mainly provided inside the lower end portion of the main shaft 123 protruding downward from the lower end of the bearing 131.
- the lower end opening 130 a of the communication hole 130 b opens at the lower end surface of the main shaft 123, and the upper end opening opens at the outer peripheral surface of the main shaft 123.
- the upper end opening of the communication hole 130 b communicates with the lower end of the spiral groove 127.
- the spiral groove 127 extends spirally upward on the outer peripheral surface of the main shaft 123 between the outer peripheral surface of the main shaft 123 and the inner peripheral surface of the bearing 131, and the upper end of the spiral groove 127 is near the sliding portion of the compression element 117. Leads to
- the shaft 119 further includes an eccentric shaft 125 provided above the main shaft 123.
- the eccentric shaft 125 has a cylindrical shape, and the shaft does not coincide with the axis of the main shaft 123 and is provided in parallel.
- a crank weight 126 is attached to the upper end portion of the eccentric shaft 125.
- the crank weight 126 has, for example, a substantially fan shape on a surface orthogonal to the axis of the eccentric shaft 125, and a hole is provided in the center thereof.
- the crank weight 126 is fixed to the upper portion of the eccentric shaft 125 by press-fitting the upper end portion of the eccentric shaft 125 into the hole.
- the shaft 119 further includes a flange 121 between the main shaft 123 and the eccentric shaft 125.
- the flange 121 has the lower surface connected to the upper end of the main shaft 123 and the upper surface connected to the lower end of the eccentric shaft 125 to connect the main shaft 123 and the eccentric shaft 125.
- the flange 121 has, for example, a substantially fan shape centered on the eccentric shaft 125 in a plane orthogonal to the axis of the eccentric shaft 125.
- the main shaft 123 is connected to the center of the flange 121, and a substantially fan-shaped arc portion of the flange 121 protrudes from the main shaft 123 in a direction opposite to the eccentric shaft 125.
- a bearing 131 of the cylinder block 129 is disposed below the flange 121.
- the cylinder block 129 has a bearing 131 extending in the vertical direction and a cylinder 137 extending in the horizontal direction.
- the bearing 131 has a substantially cylindrical shape.
- the lower portion of the bearing 131 is inserted into the cylindrical space of the digging portion 116 of the rotor 115, and the lower end of the bearing 131 is fixed by hitting the mounting portion 115e.
- the lower portion of the bearing 131 is accommodated in the digging portion 116, and the digging portion 116 and the bearing 131 overlap each other. For this reason, without shortening the length of the bearing 131, the height dimension of the dug part 116 and the bearing 131 can be reduced, and the height dimension of the sealed container 101 can be kept low.
- the bearing 131 includes a columnar through-hole extending in the vertical direction.
- the main shaft 123 is inserted into the through hole in a rotatable state, and the bearing 131 supports the main shaft 123 in the radial direction on its inner peripheral surface.
- the lower end portion of the main shaft 123 inserted into the through hole protrudes downward from the lower end of the bearing 131 and is fixed to the attachment portion 115e of the rotor 115.
- the bearing 131 supports a longitudinal load acting on the flange 121 via a thrust ball bearing 180 on a thrust surface 196 described later.
- the longitudinal load acting on the flange 121 corresponds to a load obtained by combining the shaft 119, the crank weight 126 and the rotor 115 attached thereto, and the balance weight 170 attached to the rotor 115. .
- the cylinder 137 includes a cylindrical space extending in the lateral direction inside, and a valve plate 139 is attached to an end surface thereof.
- the valve chamber 139 closes one end of the horizontal cylindrical space, so that the compression chamber 141 is formed inside the cylinder 137.
- a cylinder head 153 is fixed to the end surface of the cylinder 137 so as to cover the valve plate 139, and a suction muffler 155 is attached between the valve plate 139 and the cylinder head 153.
- the suction muffler 155 is molded from a resin such as PBT (polybutylene terephthalate), and reduces the inflow sound of the working fluid flowing from the suction pipe by the internal silencing space.
- One end of the piston 133 is removably inserted into the compression chamber 141 in the cylinder 137, and the other end is connected to the connecting portion 143.
- the connecting portion 143 is configured such that a piston pin 135 attached to the piston 133 is fitted into a hole provided at one end, and an eccentric shaft 125 is fitted into a hole provided at the other end. 133 is connected.
- FIG. 2 is an enlarged view of region A in FIG.
- the bearing 131 of the cylinder block 129 has an annular thrust surface 196 on the upper surface thereof.
- the thrust surface 196 extends in a direction perpendicular to the central axis of the bearing 131, the center thereof coincides with the central axis of the bearing 131, and the inner diameter dimension of the thrust surface 196 is larger than the inner diameter dimension of the bearing 131.
- a tubular extension 194 is provided between the inner circle of the thrust surface 196 and the inner peripheral surface of the bearing 131.
- the tubular extension 194 has a cylindrical shape extending in the vertical direction, and its axis coincides with the central axis of the bearing 131.
- the inner peripheral surface of the tubular extension 194 is continuous with the inner peripheral surface of the main body of the bearing 131 and faces the outer peripheral surface of the main shaft 123.
- a thrust ball bearing 180 is disposed outside the tubular extension 194 of the bearing 131 between the flange 121 of the shaft 119 and the thrust surface 196 of the bearing 131.
- the thrust ball bearing 180 has a plurality of balls 186.
- the balls 186 are rolling elements, and the plurality of balls 186 have the same size.
- the ball 186 is held by the holder 188.
- another rolling bearing such as a roller bearing can be used.
- the holder 188 is an annular flat plate member and is formed of a resin material such as polyamide.
- the holder 188 has an inner peripheral surface in contact with an outer peripheral surface of the tubular extension 194 and has a plurality of holes therein.
- the plurality of holes are arranged in the circumferential direction, and a ball 186 is housed therein so as to freely roll.
- the height dimension of the holder 188 is smaller than the diameter dimension of the ball 186, and the ball 186 protrudes from the holder 188 in the vertical direction.
- the ball 186 is sandwiched and held between the upper race 182 and the lower race 190 from the vertical direction.
- the upper race 182 and the lower race 190 are annular flat plate members, and are formed of metal, preferably spring steel subjected to heat treatment.
- the upper and lower surfaces of each race 182 and 190 are parallel, and the surfaces of the upper and lower surfaces are finished smoothly.
- the upper race 182 is positioned above the ball 186 and the holder 188, and the upper surface thereof is in contact with the lower surface of the flange 121 and the lower surface is in contact with the ball 186.
- the lower race 190 is positioned below the ball 186 and the holder 188, and has an upper surface in contact with the ball 186 and a lower surface in contact with the upper surface of the support member 192.
- the support member 192 is an annular member having elasticity, and its upper surface is in contact with the lower surface of the lower race 190 and its lower surface is in contact with the thrust surface 196 of the bearing 131.
- FIG. 3A is a cross-sectional view of the rotor 115 cut along a plane perpendicular to the axis
- FIG. 3B is a cross-sectional view of the rotor 115 taken along a broken line BB in FIG. 3A.
- the rotor 115 includes an upper end plate 115c, a lower end plate 115d, and a substantially cylindrical iron core 115a sandwiched therebetween.
- the iron core 115a a plurality of thin annular electromagnetic steel plates are laminated.
- Each electromagnetic steel plate is provided with a plurality (three in this embodiment) of circular holes for caulking pins 172 and a plurality (six in this embodiment) of arc-shaped holes for permanent magnets 115b.
- the permanent magnet 115b is an arc-shaped columnar member in a plane perpendicular to the axis, and the height dimension thereof is set to be substantially the same as the height dimension of the iron core 115a.
- Each of the end plates 115c and 115d is a thin annular plate, and is provided with a circular hole for the caulking pin 172.
- the caulking pin 172 is inserted into the circular hole of the lower end plate 115d, and the iron core 115a is disposed on the lower end plate 115d so that the circular hole passes through the caulking pin 172.
- the permanent magnet 115b is inserted in the arc-shaped hole of the iron core 115a, and the upper end plate 115c is arranged on the iron core 115a.
- the upper end plate 115c, the lower end plate 115d, and the iron core 115a are fixed with caulking pins 172 so that they are in close contact with each other in the vertical direction.
- the rotor 115 is formed by magnetizing a permanent magnet 115b (more precisely, a magnet material before being magnetized) housed in the iron core 115a.
- the rotor 115 is divided into an upper digging portion 116 and a lower mounting portion 115e in the vertical direction from the viewpoint of the difference in inner diameter.
- the digging portion 116 and the attachment portion 115e are the same except that the inner diameters of the steel plates constituting them are different. Therefore, the digging portion 116 and the attachment portion 115e are integrally formed by fixing the plurality of steel plates constituting the portions 116 and 115e with the caulking pins 172.
- the inner diameter R1 of the digging portion 116 is larger than the inner diameter R2 of the mounting portion 115e, and is set slightly larger than the outer diameter of the lower portion of the bearing 131 as shown in FIG. Yes. For this reason, the lower portion of the bearing 131 is inserted into the cylindrical space of the dug portion 116.
- the height of the dug portion 116 and the bearing 131 is reduced without shortening the length of the bearing 131, and the hermetic container 101. The height can be kept low.
- the inner diameter R2 of the mounting portion 115e is smaller than the outer diameter of the lower portion of the bearing 131 and is set to be substantially the same as the outer diameter of the lower portion of the main shaft 123 of the shaft 119.
- a lower portion of the main shaft 123 that penetrates through the bearing 131 and protrudes downward is inserted into a cylindrical space of the mounting portion 115e, and is fixed to an inner peripheral surface that defines the cylindrical space.
- the ratio of the height dimension M of the digging portion 116 to 70% or more and the ratio of the height dimension N of the mounting portion 115e to the height dimension L of the iron core 115a of the rotor 115 is It is set to 30% or less.
- a digging portion 116 having a height dimension M of 30 mm and a mounting portion 115e having a height dimension N of 6 mm are provided for an iron core 115a having a height dimension L of 36 mm.
- the ratio of the height dimension M of the digging portion 116 to the iron core 115a is 83%.
- the hermetic container 101 can be thinned.
- the ratio of the attachment portion 115e to the iron core 115a becomes very small, and the fixing range between the attachment portion 115e and the main shaft 123 becomes narrow.
- the iron core 115a is a laminate in which a plurality of steel plates are stacked in the vertical direction, the rigidity in the horizontal direction of the iron core 115a to which the main shaft 123 is fixed is relatively low. Although the inclination of the main shaft 123 adversely affects such a fixed portion, the reduction is made by the balance weight 170.
- FIG. 4 is an external view of the rotor 115 as seen from the lower surface side.
- the balance weight 170 is formed of a thin metal flat plate and is disposed on the lower end plate 115 d of the rotor 115.
- the mass of the balance weight 170 is determined by the force and moment acting on the shaft 119, and is set to be smaller than the mass of the crank weight 126, for example, 1/8 of the mass of the crank weight 126.
- the balance weight 170 is substantially arc-shaped in a plane parallel to the lower surface of the rotor 115, and the arc-shaped inner curve is along the inner circumference of the lower end plate 115d, and the arc-shaped outer curve is the outer circumference of the lower end plate 115d and the iron core 115a.
- a balance weight 170 is provided so as to be symmetric with respect to a line parallel to the trajectory in which the piston 133 (FIG. 1) reciprocates as shown by a one-dot chain line C in FIG.
- the balance weight 170 is provided with two circular holes that pass through the caulking pins 172, and the two circular holes are arranged symmetrically with respect to the alternate long and short dash line C.
- the balance weight 170 is fixed on the lower surface of the rotor 115 at the same time as the rotor 115 is assembled by the caulking pin 172 inserted into each circular hole.
- a power source such as a commercial power source provided outside the sealed container 101 is connected to the power terminal 109 of the sealed container 101.
- AC power is supplied from the external power source to the electric element 111, and the rotor 115 is rotated by the magnetic field generated in the stator 113 in the electric element 111.
- the main shaft 123 of the shaft 119 fixed to the rotor 115 rotates, and the eccentric shaft 125 connected to the main shaft 123 via the flange 121 rotates eccentrically.
- the eccentric rotational motion of the eccentric shaft 125 is converted into a linear reciprocating motion by the connecting portion 143, and the piston 133 reciprocates in the compression chamber 141 of the cylinder 137.
- the volume in the compression chamber 141 closed by the piston 133 changes.
- the piston 133 moves in the direction in which the volume in the compression chamber 141 increases, the working fluid flows from the suction pipe into the sealed container 101 and is sucked into the compression chamber 141 through the suction muffler 155.
- the working fluid is compressed in the compression chamber 141 and then becomes high temperature and high pressure from the sealed container 101 via the discharge pipe 104 and the like. It is sent to a refrigeration cycle (not shown).
- the lubricating oil 103 is pumped up from the communication hole 130b by the centrifugal pump 130. Then, the lubricating oil 103 passes through the centrifugal pump 130 and rises along the inner wall of the communication hole 130b. The lubricating oil 103 reaching the upper end of the communication hole 130 b flows into the lower end of the spiral groove 127 on the surface of the main shaft 123.
- the lubricating oil 103 in the spiral groove 127 rises with a viscous force between the outer peripheral surface of the main shaft 123 and the inner peripheral surface of the bearing 131, and the sliding portion therebetween Lubricate.
- the lubricating oil 103 is supplied to each sliding portion of the compression element 117 via the eccentric shaft 125, the connecting portion 143, and the like, and lubricates each sliding portion.
- the centrifugal pump 130 causes the lubricating oil 103 to pass through the communication hole 130b and the spiral groove 127. Can be lifted up. Thereby, since the lubricating oil 103 is sufficiently supplied to each sliding part, the reliability in the hermetic compressor 100 can be improved.
- each ball 186 rolls while making point contact with the upper race 182 and the lower race 190 in the thrust ball bearing 180.
- the friction between the thrust surface 196 of the bearing 131 and the lower surface of the flange 121 of the shaft 119 is reduced. Therefore, power loss due to friction is reduced, and the mechanical efficiency of the hermetic compressor 100 can be improved.
- the thrust ball bearing 180 since the ball 186 is in point contact with the races 182 and 190, the surface pressure is locally increased, and it is necessary to supply the lubricating oil 103 to the thrust ball bearing 180. .
- the lubricating oil 103 is sufficiently supplied to the thrust ball bearing 180 due to the shortening of the communication hole 130b described above. Therefore, the lubrication of the thrust ball bearing 180 is performed smoothly, and the durability of the thrust ball bearing 180 can be improved.
- FIG. 5 is a diagram schematically showing the force acting on the shaft 119.
- the piston 133 reciprocates, an inertial force is generated in the piston 133.
- the eccentric shaft 125 is eccentrically rotated, a centrifugal force of the eccentric shaft 125 is generated. Since the reciprocating motion of the piston 133 and the eccentric rotating motion of the eccentric shaft 125 are linked, the inertia force of the piston 133 and the centrifugal force of the eccentric shaft 125 act on the shaft 119 in the same direction.
- crank weight 126 is attached to the upper end of the eccentric shaft 125 and is located in a direction opposite to the eccentric shaft 125 with respect to the main shaft 123.
- the crank weight 126 is the same rotation shaft as the eccentric shaft 125 and rotates in conjunction with the rotation of the eccentric shaft 125. For this reason, in the direction in which the piston 133 reciprocates, the centrifugal force FB of the crank weight 126 acts on the shaft 119 in the direction opposite to the unbalance component FA.
- the balance weight 170 is attached to the lower surface of the rotor 115 and is positioned in the direction opposite to the eccentric shaft 125 with respect to the main shaft 123.
- the balance weight 170 is the same rotation shaft as the main shaft 123 and rotates in conjunction with the rotation of the main shaft 123.
- the centrifugal force FC of the balance weight 170 is in the direction opposite to the unbalance component FA and in the same direction as the centrifugal force FB of the crank weight 126 via the rotor 115. Act on.
- the masses of the crank weight 126 and the balance weight 170 are set so that the difference between the total of the centrifugal force FB of the crank weight 126 and the centrifugal force FC of the balance weight 170 and the unbalance component FA is smaller, preferably 0. Is done. For this reason, these loads FA, FB, and FC are balanced.
- the vertical distance (height dimension) from the balance weight 170 to the center of the piston 133 is LAC
- the height dimension from the center of the piston 133 to the crank weight 126 is LAB.
- the centrifugal force FB of the crank weight 126 and the centrifugal force FC of the balance weight 170 are such that these moments FB ⁇ LAB, FC ⁇ LAC cancel each other, and the rotational moment M becomes smaller, preferably 0. Is set.
- the vibration of the rotor 115 is prevented from being amplified by the vibration of the shaft 119, and the noise and vibration of the hermetic compressor 100 can be further reduced.
- the balance weight 170 is further away from the piston 133 than the crank weight 126 with respect to the piston 133, so the centrifugal force FC of the balance weight 170 is smaller than the centrifugal force FB of the crank weight 126.
- the mass of the balance weight 170 is one-eighth of the mass of the crank weight 126.
- the balance weight 170 is attached to the lower surface of the rotor 115 and is disposed at a position farthest from the piston 133 in the rotor 115. For this reason, compared with the case where it attaches to other positions, such as the upper surface of the rotor 115, the mass of the balance weight 170 attached to the lower surface may be small. Therefore, the bending moment with respect to the attachment portion 115e of the rotor 115 can be reduced and the bending of the rotor 115 can be prevented, so that vibration and noise due to the deformation of the rotor 115 can be further reduced.
- the height dimension of the digging portion 116 of the rotor 115 is increased, and the total height dimension of the rotor 115 and the bearing 131 is decreased. For this reason, the distance between the piston 133 on the bearing 131 and the portion 101a that fixes the suspension spring 107 supporting the compressor main body 105 such as the piston 133 to the sealed container 101 is shortened.
- the vibration by the piston 133 as the vibration source is easily transmitted to the outside of the hermetic compressor 100 via the suspension spring 107 and the fixed portion 101a of the hermetic container 101.
- the hermetic compressor 100 according to the present embodiment since the balance weight 170 is used in addition to the crank weight 126, noise and vibration in the hermetic compressor 100 are suppressed. Noise and vibration transmitted to the outside of the machine 100 can be reduced.
- the vibration that the shaft 119 swings and the vibration in the hermetic compressor 100 are reduced, so that a biased load is prevented from acting on the ball 186 in the thrust ball bearing 180. Therefore, the durability of the thrust ball bearing 180 is improved.
- FIG. 6 is a cross-sectional view showing a hermetic compressor 100 according to the second embodiment.
- the balance weight 270 is attached to the upper surface of the rotor 115 and is disposed on the opposite side of the crank weight 126 with respect to the piston 133.
- the mass of the balance weight 270 is determined by the force and moment acting on the shaft 119, and is set smaller than the mass of the crank weight 126, for example, one fifth of the mass of the crank weight 126.
- FIG. 7 is a diagram schematically showing the force acting on the shaft 119.
- the unbalance component FA which is the sum of the inertial force on the piston 133 due to the reciprocating motion of the piston 133 and the centrifugal force due to the eccentric rotational motion of the eccentric shaft 125, is the shaft 119 in the direction in which the piston 133 reciprocates. It extends to.
- the centrifugal force FB of the crank weight 126 acts on the shaft 119 in the direction opposite to the unbalance component FA.
- the balance weight 270 is attached to the upper surface of the rotor 115 and is positioned in a direction opposite to the eccentric shaft 125 with respect to the main shaft 123.
- the balance weight 270 is the same rotation shaft as the main shaft 123 and rotates in conjunction with the rotation of the main shaft 123. For this reason, in the direction in which the piston 133 reciprocates, the centrifugal force FD of the balance weight 270 is opposite to the unbalance component FA and in the same direction as the centrifugal force FB of the crank weight 126 via the rotor 115. Acting on the shaft 119.
- the balance weight 270 is farther from the piston 133 than the crank weight 126 with respect to the piston 133, so the centrifugal force FD of the balance weight 270 is smaller than the centrifugal force FB of the crank weight 126. .
- transformation of the rotor 115 and the vibration which the shaft 119 shakes are prevented, and the vibration and noise of the hermetic compressor 100 can be prevented.
- vibration and noise transmitted from the sealed container 101 to the outside of the hermetic compressor 100 via the suspension spring 107 can be reduced.
- the balance weight 270 is located above the rotor 115 and is separated from the oil surface of the lubricating oil 103 stored at the bottom of the sealed container 101 shown in FIG. For this reason, when the rotor 115 rotates, the balance weight 270 is not immersed in the lubricating oil 103 and the lubricating oil 103 is not stirred. Further, even when the working fluid is dissolved in the lubricating oil 103, foaming of the working fluid in the lubricating oil 103 due to stirring by the balance weight 270 is reduced. For this reason, it is possible to prevent the foamed working fluid including the lubricating oil 103 from being sucked into the compression chamber 141 and compressed into the piston 133 in the compression chamber 141 to generate abnormal noise.
- FIG. 8 is a cross-sectional view schematically showing refrigerator 200 according to the third embodiment.
- the refrigerator 200 includes a heat insulating box 202 having a heat insulating space therein, and a door attached to the heat insulating box 202 so as to be opened and closed.
- the surface of the heat insulation box 202 to which the door is attached is referred to as a front surface, and the opposite surface is referred to as a back surface.
- the heat insulation box 202 has a vertically long, substantially rectangular parallelepiped shape, and includes a heat insulation wall forming a heat insulation space therein and a plurality of heat insulation spaces (five in this embodiment) 210, 212, 214, 216. , And a partition plate for partitioning into 218.
- the five heat insulation space portions 210, 212, 214, 216, and 218 are divided into four stages in the vertical direction, and the second heat insulation space part from the top is further divided into two in the left-right direction.
- the first heat insulation space portion from the top is the refrigerator compartment 210
- the two heat insulation space portions from the top second are the switching chamber 212 and the ice making room 214
- the third heat insulation space portion is the vegetable room 216.
- the fourth-stage heat-insulating space is used as the freezer compartment 218.
- These heat insulating space portions 210, 212, 214, 216, and 218 are connected to each other by a duct (not shown), and a damper (not shown) is provided in the duct.
- the air in each heat insulation space part can move mutually by this duct, and the air volume of this air is adjusted by the damper.
- temperature sensors are arranged in all or part of the heat insulating space portions 210, 212, 214, 216, and 218.
- the heat insulating box 202 includes an inner box 204 and an outer box 206 provided outside the inner box 204.
- the inner box 204 is formed by vacuum molding a resin body such as ABS.
- the inner box 204 forms an inner surface of a heat insulating wall that defines a heat insulating space and a partition plate that partitions the heat insulating space.
- the outer box 206 is made of a metal material such as a pre-coated steel plate and forms the outer surface of the heat insulating wall.
- the heat insulating body 208 is integrally foam-filled in the space between the inner box 204 and the outer box 206, and the heat insulating box 202 is made. Thereby, a heat insulation wall and a partition plate are formed simultaneously and integrally.
- foamed plastic such as rigid urethane foam, phenol foam or styrene foam is used.
- foam material for example, hydrocarbon-based cyclopentane is used from the viewpoint of preventing global warming.
- the heat insulating box 202 is provided with a recessed portion 230 in which a part of each of the back surface and the upper surface is recessed, and the hermetic compressor 100 is elastically supported by the recessed portion 230.
- a condenser (not shown) and a dryer (not shown) for removing moisture are disposed on the side surface of the heat insulating box 202 and the like.
- a capillary 234 that is a decompressor and an evaporator 238 are disposed on the back surface of the heat insulating box 202.
- a cooling fan 236 and an evaporator 238 are disposed on the back of the vegetable compartment 216 and the freezer compartment 218 in the heat insulating box 202.
- the hermetic compressor 100, the condenser, the capillary 234, and the evaporator 238 are connected in an annular shape by a pipe 240 to constitute a refrigeration cycle.
- the heat insulation box 202 is provided with a control device (not shown), and a temperature sensor disposed in the heat insulation space is connected to the control device.
- the hermetic compressor 100, the condenser, the dryer, the capillary 234, the evaporator 238, the cooling fan 236, and the evaporator 238 are connected to the control device, and the control device performs these based on the detection value of the temperature sensor. To control.
- five doors 220, 222, 224, 226, and 228 are provided in front of the heat insulation box 202 so as to cover the heat insulation space portions 210, 212, 214, 216, and 218 in the heat insulation box 202. It is attached so that it can be opened and closed.
- the refrigerating room 210 is provided with a rotary door 220, and the remaining switching room 212, ice making room 214, vegetable room 216 and freezing room 218 are provided with drawer doors 222, 224, 226 and 228, respectively.
- the rotary door 220 and the drawer doors 222, 224, 226, and 228 are formed by attaching a decorative plate to a heat insulating material such as polystyrene foam.
- Gaskets are disposed between the doors 220, 222, 224, 226, 228 and the heat insulating box 202, whereby the airtightness of the heat insulating space portions 210, 212, 214, 216, 218 is maintained.
- the control device starts and stops the cooling operation based on detection signals from the respective temperature sensors.
- the working fluid is compressed to high temperature and high pressure by the reciprocating motion of the piston 133 (FIG. 1) in the hermetic compressor 100, and is sent from the discharge pipe 104 (FIG. 1) to the refrigeration cycle through the pipe 240. It is done.
- This high-temperature and high-pressure gaseous working fluid is condensed and liquefied when heat is released by the condenser.
- the liquid working fluid is decompressed by the capillary 234 to a low temperature and a low pressure, and reaches the evaporator 238.
- each vegetable compartment 216 and freezer compartment 218 is moved by the cooling fan 236, and heat exchange between this air and the low-temperature working fluid in the evaporator 238 is performed.
- the working fluid that has reached a high temperature evaporates and returns to the hermetic compressor 100 through the pipe 240.
- the cooled air is distributed to each heat insulating space portion 210, 212, 214 by a duct.
- the flow rate distributed to each heat insulation space portion 210, 212, 214 is adjusted by the damper, so that each heat insulation space portion 210, 212, 214, 216, 218 is adjusted to an appropriate temperature.
- the refrigerator compartment 210 has a temperature that does not freeze for refrigerated storage, for example, 1 ° C. to 5 ° C.
- the switching chamber 212 is set to a temperature that can be changed by the user, and becomes this set temperature. This set temperature can be set to a predetermined temperature from the temperature zone of the freezer compartment 218 to the temperature zone of the refrigerator or the vegetable compartment 216, for example.
- the ice making chamber 214 includes an automatic ice making device (not shown), and automatically creates and stores ice. Since this purpose is to preserve the ice, the temperature of the ice making chamber 214 is adjusted to a temperature that is relatively higher than the freezing temperature zone, for example, ⁇ 18 ° C. to ⁇ 10 ° C.
- the vegetable room 216 is adjusted to a temperature equivalent to or slightly higher than the refrigeration room 210, for example, 2 ° C to 7 ° C. The lower this temperature is, the more fresh the leaf vegetables in the vegetable room 216 can be maintained.
- the freezer compartment 218 is normally adjusted to ⁇ 22 to ⁇ 18 ° C. for frozen storage. However, it may be adjusted to a low temperature such as ⁇ 30 ° C. or ⁇ 25 ° C. in order to improve the frozen storage state.
- the refrigerator 200 uses the hermetic compressor 100 provided with the crank weight 126 and the balance weights 170 and 270 shown in FIGS. 1 and 6. In this case, the force and rotational moment that cannot be canceled by the crank weight 126 alone are canceled by the balance weights 170 and 270. Therefore, since the vibration of the hermetic compressor 100 during operation is suppressed, the vibration and noise of the refrigerator 200 can be reduced.
- the rotor 115 and the bearing 131 are overlapped by the dug portion 116 shown in FIGS. 1 and 6, and the height dimension of the hermetic compressor 100 is suppressed. For this reason, the depth dimension of the recessed part 230 on the heat insulation box 202 may be small, the size of the heat insulation space in the refrigerator 200 can be enlarged, and the thickness dimension of the heat insulation body 208 can be enlarged. Therefore, the usability or the heat insulation performance is improved.
- the partition plate is foam-filled integrally with the heat insulating wall in the heat insulating box 202, the cost can be reduced and the heat insulating performance can be improved. Since the partition plate produced in this way has about twice the heat insulation performance as compared with the heat insulating member of polystyrene foam, the partition plate can be made thinner, and the heat insulation space can be expanded accordingly.
- the hermetic compressor 100 is provided in the refrigerator 200.
- the refrigeration cycle of an industrial compressor such as an air conditioner, a vending machine, other refrigeration apparatuses, and an air compressor is also used. Used in other equipment using (heat pump cycle).
- the partition plate and the heat insulation wall are integrally formed in the heat insulation box 202, but the partition plate and the heat insulation wall may be provided separately.
- the hermetic compressor and the refrigerator including the same are useful as a thin hermetic compressor and a refrigerator including the same that can reduce vibration and noise.
Abstract
Description
図1は、密閉型圧縮機100を示す断面図である。なお、説明の便宜上、シャフト119の主軸123の軸に対して平行な方向を縦方向(上下方向)と称し、縦方向に対して直交する方向を横方向と称する。
実施の形態2に係る密閉型圧縮機100の構成は実施の形態1に係る密閉型圧縮機100の構成とほぼ同じであるが、実施の形態2に係るバランスウェイト270の位置が実施の形態1に係るバランスウェイト170の位置と異なる。図6は、実施の形態2に係る密閉型圧縮機100を示す断面図である。
図8は、実施の形態3に係る冷蔵庫200を概略的に示す断面図である。図8に示すように、冷蔵庫200は、内部に断熱空間を有する断熱箱体202と、開閉可能に断熱箱体202に取り付けられた扉とにより構成されている。なお、扉が取り付けられた断熱箱体202の面を正面とし、その対向する面を背面と称する。
なお、上記実施の形態3では、密閉型圧縮機100は冷蔵庫200に設けられたが、エアーコンディショナー、自動販売機、その他の冷凍装置、さらに空気用圧縮機等の工業用圧縮機等の冷凍サイクル(ヒートポンプサイクル)を用いた他の機器に用いられる。
101 密閉容器
111 電動要素
113 固定子
115 回転子
115e 取付部(下段部)
116 掘り込み部(上段部)
117 圧縮要素
119 シャフト
123 主軸
125 偏心軸
126 クランクウェイト
129 シリンダブロック
131 軸受
133 ピストン
137 シリンダ
141 圧縮室
170 バランスウェイト
172 かしめピン
180 スラストボールベアリング
200 冷蔵庫
270 バランスウェイト
Claims (8)
- 固定子と、前記固定子に対して回転する回転子と、を含む電動要素と、
下方に配置された前記電動要素によって駆動される圧縮要素と、
前記電動要素および前記圧縮要素を収容した密閉容器と、を備え、
前記圧縮要素は、
主軸と、前記主軸に対して偏心した偏心軸と、を含むシャフトと、
上下方向に延びる貫通孔が内部に形成されかつ当該貫通孔に挿入された前記主軸を回転可能に支持している軸受と、内部に圧縮室が形成されたシリンダと、を含むシリンダブロックと、
前記偏心軸に連結され、前記圧縮室内を往復運動するピストンと、
前記偏心軸の上部に取り付けられたクランクウェイトと、を備え、
前記回転子は、内部に円柱状空間を含む円筒形状であって、
前記軸受の下部が前記円柱状空間に嵌められている上段部と、
前記上段部の内径寸法より内径寸法が小さく、かつ前記軸受の前記貫通孔を通過した前記主軸の下部が前記円柱状空間に挿入され固着されている下段部と、
前記ピストンに対して前記クランクウェイトと反対側に配置されたバランスウェイトと、を有している、密閉型圧縮機。 - 前記上段部の高さ寸法は、前記回転子の高さ寸法の70%以上である、請求項1に記載の密閉型圧縮機。
- 前記圧縮要素は、前記軸受のスラスト面上に配置されたスラストボールベアリングをさらに有している、請求項1または2に記載の密閉型圧縮機。
- 前記バランスウェイトの質量は、前記クランクウェイトの質量の5分の1以下である、請求項1~3のいずれか一項に記載の密閉型圧縮機。
- 前記バランスウェイトは、前記回転子の下面上に配置された、請求項1~4のいずれか一項に記載の密閉型圧縮機。
- 前記バランスウェイトは、前記回転子の上面上に配置された、請求項1~4のいずれか一項に記載の密閉型圧縮機。
- 前記バランスウェイトは、前記回転子にかしめピンによって取り付けられた、請求項1~6のいずれか一項に記載の密閉型圧縮機。
- 請求項1~7のいずれか一項に記載の密閉型圧縮機を備える、冷蔵庫。
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KR1020147020765A KR20140107608A (ko) | 2011-12-26 | 2012-12-26 | 밀폐형 압축기 및 그것을 구비한 냉장고 |
CN201280064825.9A CN104011385A (zh) | 2011-12-26 | 2012-12-26 | 密闭型压缩机和具备其的冷藏库 |
US14/365,845 US20140308141A1 (en) | 2011-12-26 | 2012-12-26 | Sealed compressor and refrigerator including sealed compressor |
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JP (1) | JPWO2013099237A1 (ja) |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2019019701A (ja) * | 2017-07-13 | 2019-02-07 | 日立アプライアンス株式会社 | 圧縮機 |
JP2020148109A (ja) * | 2019-03-12 | 2020-09-17 | 日立グローバルライフソリューションズ株式会社 | 圧縮機及び圧縮機を有する機器 |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2018003639A (ja) * | 2016-06-29 | 2018-01-11 | 日立アプライアンス株式会社 | 密閉型圧縮機 |
JP6143314B1 (ja) * | 2016-07-29 | 2017-06-07 | パナソニック アプライアンシズ リフリジレーション デヴァイシズ シンガポール | 密閉型冷媒圧縮機および冷凍装置 |
EP3514384A1 (de) * | 2018-01-19 | 2019-07-24 | Nidec Global Appliance Germany GmbH | Kurbelwelle |
CN217652875U (zh) * | 2021-10-25 | 2022-10-25 | 思科普有限责任公司 | 封装式制冷剂压缩机 |
CN113864156B (zh) * | 2021-10-28 | 2023-01-17 | 珠海格力电器股份有限公司 | 一种往复式压缩机 |
KR102451043B1 (ko) * | 2022-03-22 | 2022-10-06 | 주식회사 필택 | 쌍원통 펌프 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000134882A (ja) * | 1998-10-21 | 2000-05-12 | Matsushita Electric Ind Co Ltd | 永久磁石モータのロータ及びそれを搭載したコンプレッサ |
JP2005500476A (ja) * | 2001-08-31 | 2005-01-06 | エンプレサ・ブラジレイラ・デイ・コンプレソレス・エシ・ア−エンブラク | 密閉圧縮機のアキシアル軸受装置 |
JP2005269695A (ja) * | 2004-03-16 | 2005-09-29 | Matsushita Electric Ind Co Ltd | 密閉型電動圧縮機 |
JP2005307794A (ja) * | 2004-04-20 | 2005-11-04 | Matsushita Electric Ind Co Ltd | 圧縮機の防振装置 |
JP2005307845A (ja) * | 2004-04-21 | 2005-11-04 | Matsushita Electric Ind Co Ltd | 密閉型圧縮機 |
JP2010255556A (ja) * | 2009-04-27 | 2010-11-11 | Panasonic Corp | 密閉型圧縮機および冷凍装置 |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2179268A (en) * | 1937-12-16 | 1939-11-07 | Chrysler Corp | Two-cylinder compressor |
US3008629A (en) * | 1957-10-03 | 1961-11-14 | Carrier Corp | Compressor |
US4406590A (en) * | 1980-06-11 | 1983-09-27 | Tecumseh Products Company | Hermetic compressor |
US4718830A (en) * | 1982-09-30 | 1988-01-12 | White Consolidated Industries, Inc. | Bearing construction for refrigeration compresssor |
JPH11303746A (ja) * | 1998-04-20 | 1999-11-02 | Matsushita Refrig Co Ltd | 電動圧縮機 |
US6135727A (en) * | 1999-02-16 | 2000-10-24 | Tecumseh Products Company | Detachably affixed counterweight and method of assembly |
WO2000077399A2 (en) * | 1999-06-14 | 2000-12-21 | Matsushita Refrigeration Company | Hermetic motor-driven compressor |
JP4759862B2 (ja) * | 2001-07-16 | 2011-08-31 | パナソニック株式会社 | 密閉型電動圧縮機 |
JP2005023877A (ja) * | 2003-07-04 | 2005-01-27 | Matsushita Electric Ind Co Ltd | 密閉型圧縮機 |
EP1725773A1 (en) * | 2004-02-24 | 2006-11-29 | Matsushita Electric Industrial Co., Ltd. | Hermetic type compressor with wave-suppressing member in the oil reservoir |
JP4752241B2 (ja) * | 2004-11-01 | 2011-08-17 | パナソニック株式会社 | 往復動式圧縮機 |
JP4752255B2 (ja) * | 2004-12-06 | 2011-08-17 | パナソニック株式会社 | 密閉型圧縮機 |
JP4735084B2 (ja) * | 2005-07-06 | 2011-07-27 | パナソニック株式会社 | 密閉型圧縮機 |
CN1896505A (zh) * | 2005-07-13 | 2007-01-17 | 乐金电子(天津)电器有限公司 | 封闭型压缩机的曲柄轴均衡框架 |
KR100679929B1 (ko) * | 2005-07-27 | 2007-02-07 | 삼성광주전자 주식회사 | 밀폐형 압축기 |
US20070058895A1 (en) * | 2005-09-13 | 2007-03-15 | Paschoalino Marcelo R | Anti-friction thrust bearing centering device for hermetic refrigeration compressors |
JP2008516123A (ja) * | 2005-10-26 | 2008-05-15 | 松下電器産業株式会社 | 密閉型圧縮機 |
KR100874807B1 (ko) * | 2005-11-22 | 2008-12-19 | 파나소닉 주식회사 | 밀폐형 압축기 |
KR101235191B1 (ko) * | 2006-12-18 | 2013-02-20 | 삼성전자주식회사 | 밀폐형 압축기 |
US20090116982A1 (en) * | 2007-04-25 | 2009-05-07 | Kosuke Tsuboi | Hermetic reciprocating compressor with thrust ball bearing |
CN101589232A (zh) * | 2007-10-25 | 2009-11-25 | 松下电器产业株式会社 | 压缩机 |
ES2380442T3 (es) * | 2008-07-31 | 2012-05-11 | Panasonic Corporation | Compresor de tipo cerrado |
-
2012
- 2012-12-26 US US14/365,845 patent/US20140308141A1/en not_active Abandoned
- 2012-12-26 KR KR1020147020765A patent/KR20140107608A/ko not_active Application Discontinuation
- 2012-12-26 WO PCT/JP2012/008309 patent/WO2013099237A1/ja active Application Filing
- 2012-12-26 JP JP2013551245A patent/JPWO2013099237A1/ja active Pending
- 2012-12-26 CN CN201280064825.9A patent/CN104011385A/zh active Pending
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000134882A (ja) * | 1998-10-21 | 2000-05-12 | Matsushita Electric Ind Co Ltd | 永久磁石モータのロータ及びそれを搭載したコンプレッサ |
JP2005500476A (ja) * | 2001-08-31 | 2005-01-06 | エンプレサ・ブラジレイラ・デイ・コンプレソレス・エシ・ア−エンブラク | 密閉圧縮機のアキシアル軸受装置 |
JP2005269695A (ja) * | 2004-03-16 | 2005-09-29 | Matsushita Electric Ind Co Ltd | 密閉型電動圧縮機 |
JP2005307794A (ja) * | 2004-04-20 | 2005-11-04 | Matsushita Electric Ind Co Ltd | 圧縮機の防振装置 |
JP2005307845A (ja) * | 2004-04-21 | 2005-11-04 | Matsushita Electric Ind Co Ltd | 密閉型圧縮機 |
JP2010255556A (ja) * | 2009-04-27 | 2010-11-11 | Panasonic Corp | 密閉型圧縮機および冷凍装置 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2019019701A (ja) * | 2017-07-13 | 2019-02-07 | 日立アプライアンス株式会社 | 圧縮機 |
JP2020148109A (ja) * | 2019-03-12 | 2020-09-17 | 日立グローバルライフソリューションズ株式会社 | 圧縮機及び圧縮機を有する機器 |
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US20140308141A1 (en) | 2014-10-16 |
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JPWO2013099237A1 (ja) | 2015-04-30 |
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