US20140169998A1 - Sealed compressor - Google Patents
Sealed compressor Download PDFInfo
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- US20140169998A1 US20140169998A1 US14/237,315 US201214237315A US2014169998A1 US 20140169998 A1 US20140169998 A1 US 20140169998A1 US 201214237315 A US201214237315 A US 201214237315A US 2014169998 A1 US2014169998 A1 US 2014169998A1
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- Prior art keywords
- compression chamber
- piston
- projection
- refrigerant gas
- discharge hole
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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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
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
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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
- F04B39/0005—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1066—Valve plates
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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
- F04B2201/00—Pump parameters
- F04B2201/08—Cylinder or housing parameters
- F04B2201/0808—Size of the dead volume
Definitions
- the present invention relates to a sealed compressor for use in a refrigeration cycle such as an electric refrigerator, an air conditioner, and a refrigerator-freezer.
- FIG. 7 is a longitudinal sectional view of the conventional sealed compressor disclosed in Patent Literature 1.
- FIG. 8 is a perspective view of a piston of the conventional sealed compressor.
- FIG. 9 is a cross-sectional view of major components of the conventional sealed compressor, which is taken along A-A of FIG. 8 .
- a conventional sealed compressor 1 includes a compression component 5 and an electric component 7 which are accommodated into a sealed container 3 , and its internal space is filled with a refrigerant gas 9 .
- the compression component 5 has a configuration in which a piston 13 is reciprocatingly inserted into a cylinder 11 of a substantially cylindrical shape, and is connected to an eccentric shaft 19 of a crankshaft 17 via a connecting means 15 .
- a valve plate 25 having a suction hole 21 and a discharge hole 23 is provided at an end portion of the cylinder 11 .
- the valve plate 25 is provided with a suction valve (not shown) and a discharge valve 27 to open and close the suction hole 21 and the discharge hole 23 , respectively.
- the cylinder 11 , the valve plate 25 and the piston 13 define a compression chamber 29 .
- the piston 13 reciprocates inside of the cylinder 11 , which constitute a compression mechanism for suctioning the refrigerant gas 9 into the compression chamber 29 , compressing the refrigerant gas 9 in the compression chamber 29 , and discharging the refrigerant gas 9 out of the compression chamber 29 .
- the conventional sealed compressor 1 is configured such that the piston 13 is provided with a projection 31 on an end surface (tip end surface) at the valve plate 25 side in a position in which the projection 31 enters (moves into) the discharge hole 23 , to reduce a dead volume (region expressed as meshed pattern) of the discharge hole 23 .
- side surfaces of the projection 31 of the piston 13 are set such that a gradient thereof changes continuously in a circumferential direction, is minimum in a region of a side surface 33 and is maximum in a region of a side surface 35 .
- An inner peripheral surface 37 of the discharge hole 23 has a gradient (slope) set so that the inner peripheral surface 37 is substantially parallel to the side surface 33 and the side surface 35 of the projection 31 of the piston 13 .
- Non-patent Literature 1 discloses a technique for reducing a loss of the fluid in a peripheral region of an entrance of a discharge hole through which the fluid is discharged, which loss is caused by a flow of the fluid, by forming a bell mouth having a circular-arc cross-section in the peripheral region of the entrance (see, e.g., Non-patent Literature 1).
- the side surface 33 having a gentle slope (small gradient) in the projection 31 can reduce a change in the refrigerant gas 9 in the flow direction 39 .
- the projection 31 has a truncated cone shape, a portion of the refrigerant gas 9 which should flow from the suction hole 21 to the discharge hole 23 flows toward peripheral walls (side surfaces) of the projection 31 .
- Non-patent Literature 1 It is assumed that the configuration disclosed in the above mentioned Non-patent Literature 1 is applied to the discharge hole 23 of the above described conventional sealed compressor 1 . However, it is estimated that adequate advantages cannot be expected due to a loss of the refrigerant gas (complicated behavior of the refrigerant gas) in the vicinity of the discharge hole 23 , which is associated with the projection 31 .
- the present invention is directed to solving the above described problem associated with the prior art, and an object of the present invention is to provide a sealed compressor which can attain a high efficiency, in which a dead volume is reduced to reduce a loss caused by re-expansion of a refrigerant gas, and a flow of the refrigerant gas is improved to reduce a loss of a discharged refrigerant gas in an interior of a compression chamber and a discharge hole.
- a sealed compressor of the present invention comprises an electric component; a compression component actuated by the electric component; and a sealed container accommodating the electric component and the compression component; wherein the compression component includes: a cylinder block defining a compression chamber; a piston which reciprocates in an interior of the compression chamber; and a valve plate disposed to close an opening end of the compression chamber and having a suction hole through which a refrigerant gas to be compressed in the interior of the compression chamber flows into the interior of the compression chamber, and a discharge hole through which the refrigerant gas compressed in the interior of the compression chamber is discharged from the interior of the compression chamber; wherein the piston is provided with a projection on a tip end surface which faces the valve plate; and wherein the projection is configured such that side surfaces thereof include at least one flat surface and a gradient ⁇ of the flat surface with respect to the tip end surface of the piston is smaller than a gradient ⁇ of another side surface of the projection with respect to the tip end surface of the piston.
- the amount of the refrigerant gas left in the interior of the compression chamber without being discharged, at the end of a compression stroke, can be lessened, and a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged, can be reduced.
- a sealed compressor of the present invention is capable of reducing a loss of a flow of a discharged gas in an interior of a compression chamber and a discharge hole and of reducing a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged. Therefore, the sealed compressor of the present invention can increase its efficiency.
- FIG. 1 is a longitudinal sectional view of a sealed compressor according to Embodiment 1.
- FIG. 2 is a perspective view showing major components of a piston of the sealed compressor according to Embodiment 1.
- FIG. 3 is a cross-sectional view of the piston of the sealed compressor according to Embodiment 1, which is taken along B-B of FIG. 2 .
- FIG. 4 is a schematic view showing a tip end surface of the piston of the sealed compressor according to Embodiment 1, when viewed from a direction in which the piston retracts.
- FIG. 5 is a view showing a characteristic indicating a relationship between a gradient ⁇ of a side surface of a projection, and coefficient of performance COP in the sealed compressor according to Embodiment 1.
- FIG. 6 is a perspective view showing major components of a piston according to a modified example of Embodiment 1.
- FIG. 7 is a longitudinal sectional view of a sealed compressor disclosed in Patent Literature 1.
- FIG. 8 is a perspective view of a piston of the sealed compressor disclosed in Patent Literature 1.
- FIG. 9 is a cross-sectional view of the piston of the sealed compressor disclosed in Patent Literature 1, which is taken along A-A of FIG. 8 .
- a sealed compressor of the present invention comprises an electric component; a compression component actuated by the electric component; and a sealed container accommodating the electric component and the compression component; wherein the compression component includes: a cylinder block defining a compression chamber; a piston which reciprocates in an interior of the compression chamber; and a valve plate disposed to close an opening end of the compression chamber and having a suction hole through which a refrigerant gas to be compressed in the interior of the compression chamber flows into the interior of the compression chamber, and a discharge hole through which the refrigerant gas compressed in the interior of the compression chamber is discharged from the interior of the compression chamber; wherein the piston is provided with a projection on a tip end surface which faces the valve plate; and wherein the projection is configured such that side surfaces thereof include at least one flat surface and a gradient ⁇ of the flat surface with respect to the tip end surface of the piston is smaller than a gradient ⁇ of another side surface of the projection with respect to the tip end surface of the piston.
- the refrigerant gas colliding against the flat surface and is prevented from flowing toward the peripheral walls by the flat surface can be efficiently guided toward the discharge hole. Therefore, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of a compression stroke, can be lessened, and a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged, can be reduced. Thus, efficiency of the sealed compressor can be improved.
- the flat surface having the gradient ⁇ may be placed to face the suction hole.
- the refrigerant gas flowing into the compression chamber through the suction hole can be more efficiently guided to flow toward the discharge hole along the flat surface.
- the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke can be further reduced.
- a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged can be reduced.
- efficiency of the sealed compressor can be further improved.
- the discharge hole may have an opening area which increases from the compression chamber side toward an opposite side of the compression chamber.
- an area of a flow passage defined by the side surface of the projection and the inner peripheral surface of the discharge hole can be increased. Because of this, it becomes possible to reduce a passage resistance of the refrigerant gas flowing through the discharge hole. As a result, the compressed refrigerant gas can be smoothly discharged from the discharge hole, excessive compression of the refrigerant gas during the compression stroke can be reduced, and the amount of electric power input to the sealed compressor can be reduced.
- an opening portion of the discharge hole in the valve plate, which opening portion is at the compression chamber side may have a circular-arc cross-section.
- the refrigerant gas can be guided to the discharge hole more smoothly.
- the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke can be reduced. Therefore, a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged can be reduced, and hence efficiency of the sealed compressor can be further improved.
- a cross-section of the projection which is taken along a plane which is substantially parallel to the tip end surface of the piston may have a polygonal shape.
- the refrigerant gas collides against plural flat surfaces defining the polygonal shape, and is prevented from flowing toward the side surfaces of the projection by the flat surfaces.
- the portions of the refrigerant gas colliding against the plural flat surfaces flow along the flat surfaces, and therefore can be guided toward the discharge hole.
- the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke can be further reduced.
- a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged can be reduced, and hence efficiency of the sealed compressor can be further improved.
- a cross-section of the projection which is taken along a plane which is substantially parallel to the tip end surface of the piston may have a rectangular shape.
- the refrigerant gas flowing toward the discharge hole is guided along the four flat surfaces defining the projection. Therefore, the flow to the side surfaces of the projection can be suppressed, and the refrigerant gas can be smoothly guided toward the discharge hole. Moreover, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke, can be reduced, and a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged, can be reduced. As a result, efficiency of the sealed compressor can be further improved.
- the gradient ⁇ may be in a range of 65 degrees ⁇ 80 degrees.
- the refrigerant gas can be flowed smoothly toward the discharge hole. Especially, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke, can be reduced, a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged can be reduced, and efficiency of the sealed compressor can be further improved.
- FIG. 1 is a longitudinal sectional view of a sealed compressor according to Embodiment 1.
- FIG. 2 is a perspective view showing major components of a piston of the sealed compressor according to Embodiment 1.
- FIG. 3 is a cross-sectional view of the piston of the sealed compressor according to Embodiment 1, which is taken along B-B of FIG. 2 .
- FIG. 4 is a schematic view showing a tip end surface of the piston of the sealed compressor according to Embodiment 1, when viewed from a direction in which the piston retracts.
- a refrigerant gas 103 is filled into a sealed container 101 .
- the sealed container 101 accommodates a compression component 107 and an electric component 105 for actuating the compression component 107 .
- the compression component 107 and the electric component 105 are elastically supported on the sealed container 101 by means of a suspension spring 109 .
- the compression component 107 mainly includes a crankshaft 111 for converting a rotational motion of the electric component 105 into a reciprocation motion, and a cylinder block 115 including a cylinder 113 defining a compression chamber 135 of a substantially cylindrical shape.
- the crankshaft 111 includes a main shaft section 119 to which a rotor 117 of the electric component 105 is fastened and an eccentric section 121 having a center axis which is eccentric with respect to the main shaft section 119 .
- the main shaft section 119 is supported on a main shaft bearing unit 123 of the cylinder block 115 .
- a piston 125 is reciprocatingly inserted into the cylinder 113 .
- the piston 125 is connected to the eccentric section 121 of the crankshaft 111 via a connecting means 127 . That is, one end of the connecting means 127 is rotatably connected to the eccentric section 121 of the crankshaft 111 , while the other end thereof is rotatably connected to a piston pin 129 attached to the piston 125 .
- This allows the connecting means 127 to convert a rotational motion of the eccentric section 121 caused by a rotation of the crankshaft 111 into a reciprocation motion and transmit the reciprocation motion to the piston 125 .
- a valve plate 133 is attached to an end portion 131 of the cylinder 113 .
- the valve plate 133 closes the end portion 131 (compression chamber 135 ) of the cylinder 113 .
- the valve plate 133 is provided with a suction hole 137 and a discharge hole 139 each of which has a circular opening. A shape of the discharge hole 139 will be described later.
- the valve plate 133 is provided with a suction valve (not shown) for opening and closing the suction hole 137 and a discharge valve 145 (see FIG. 3 ) for opening and closing the discharge hole 139 .
- a configuration (shape) of the suction valve and a configuration (shape) of the discharge valve 145 are well-known, and therefore detailed description thereof will be omitted.
- the valve plate 133 is covered with a cylinder head 141 . Inside of the cylinder head 141 , a discharge chamber 147 communicated with the discharge hole 139 is provided. A discharge pipe 149 is connected to the discharge chamber 147 . An exit pipe 151 is connected to the discharge pipe 149 such that the exit pipe 151 extends to outside of the sealed container 101 . Furthermore, as shown in FIG. 1 , a suction muffler 143 is retained between the cylinder head 141 and the valve plate 133 .
- the discharge hole 139 provided in the valve plate 133 is formed such that its opening area increases in a direction from the compression chamber 135 side toward an opposite side (discharge chamber 147 side) of the compression chamber 135 .
- An opening portion 173 of the discharge hole 139 in the valve plate 133 which opening portion is at the compression chamber 135 side, has a circular-arc cross-section.
- the cross-section of the opening portion 173 which is taken along a direction in which the piston 125 moves has a circular-arc shape which is round.
- a radius of the circular-arc of the opening portion 173 of the discharge hole 139 may be set as desired.
- the opening portion 173 of the circular-arc shape will be referred to as a bell mouth portion 173 .
- the discharge hole 139 has a size to allow a projection 155 of the piston 125 to easily move thereinto. As shown in FIG. 4 , the discharge hole 139 is provided in a position of a center axis 159 which is eccentric outward relative to a center axis 157 of the compression chamber 135 .
- a center axis 161 of the projection 155 is provided in a position so that the projection 155 closes and exposes the discharge hole 139 during the reciprocation motion of the piston 125 , and (substantially) conforms to the center axis 159 of the discharge hole 139 . That is, the center axis 161 of the projection 155 is in the position which is eccentric outward relative to the center axis 157 of the compression chamber 135 and the center axis 163 of the piston 125 (substantially) conforming to the center axis 157 .
- the projection 155 (discharge hole 139 ) and the suction hole 137 provided in the valve plate 133 do not overlap with each other when viewed from the direction in which the piston 125 moves.
- the suction hole 137 is positioned within a projection plane (hatched region) from a line X which is an extended line of a side of the projection 155 (bottom of a side wall 165 a as will be described later) which is closest to the center axis 163 of the piston 125 to a region which is beyond the center axis 163 of the piston 125 .
- a tip end surface 153 of the piston 125 at the valve plate 133 side is provided with the projection 155 such that the projection 155 overlaps with the discharge hole 139 when viewed from the direction in which the piston 125 moves.
- the projection 155 is integral with the piston 125 , and closes and exposes the discharge hole 139 according to the reciprocation motion of the piston 125 .
- the projection 155 has a rectangular shape in cross-section which is taken along a plane parallel to the tip end surface 153 of the piston 125 , i.e., substantially rectangular-parallelepiped shape (including truncated pyramid shape), and has four flat surfaces (hereinafter will be referred to as side walls) 165 a , 165 b , 165 c , 165 d , and a top surface 167 .
- the projection 155 has a shape in which the top surface 167 perpendicular to the center axis 163 of the piston 125 has a substantially rectangular shape.
- the projection 155 is configured such that a gradient (slope) formed between the four side walls 165 a , 165 b , 165 c , 165 d , and the tip end surface 153 of the piston 125 is less than 90 degrees.
- the projection 155 is configured such that the cross-section which is taken along a plane parallel to the tip end surface 153 of the piston 125 has an area which is reduced toward a top portion (top surface 167 ) which is distant from the tip end surface 153 of the piston 125 .
- the side wall 165 a of the projection 155 is oriented such that an angle ⁇ (hereinafter will be referred to as placement angle) formed between the line X and a line Y passing through the center axis (center) 169 of the suction hole 137 and the center axis (center) 163 of the piston 125 , is set to about 52 degrees.
- placement angle an angle formed between the line X and a line Y passing through the center axis (center) 169 of the suction hole 137 and the center axis (center) 163 of the piston 125 .
- the placement angle ⁇ may be defined as a placement relationship in which a line Z which is perpendicular to the side wall 165 a and passes through a center of the side wall 165 a crosses the line Y passing through the center axis 169 of the suction hole 137 and the center axis 163 of the piston 125 at a predetermined angle.
- a gradient (slope) a formed between the side wall 165 a and the tip end surface 153 of the piston 125 is set to 70 degrees.
- the gradient ⁇ may be set to a desired value in a range of 65 degrees ⁇ 80 degrees, and may be ⁇ 79 degrees. Note that there is a little tolerance in the gradient ⁇ because the piston 125 and the projection 155 are molded using a die.
- a gradient (slope) ⁇ formed between other side walls 165 b , 165 c , 165 d , and the tip end surface 153 of the piston 125 is set to about 85 degrees.
- the gradient ⁇ is an angle except for a draft angle (about 5 degrees) during the above stated die molding, and may be set to a desired value.
- the gradient ⁇ and the gradient ⁇ are set such that the gradient ⁇ is smaller than the gradient ⁇ .
- a curved surface 171 having a specified diameter is formed in a portion (base end portion of the projection 155 ) of the tip end surface 153 of the piston 125 which the side wall 165 a of the projection 155 crosses.
- the side wall 165 a of the projection 155 partially has the curved surface 171 .
- a refrigerant circuit connecting a condenser (not shown), a pressure-reducer (not shown), and an evaporator (not shown) is connected between a suction pipe (not shown) and the exit pipe 161 , thus constituting a well-known refrigeration cycle.
- R 600 a is used as the refrigerant gas 103 to be compressed.
- the volume of the compression chamber 135 increases according to the motion of the piston 125 toward the crankshaft 111 . Therefore, the pressure in the interior of the compression chamber 135 decreases. Due to a pressure difference between an interior of the suction muffler 143 and the interior of the compression chamber 135 , the suction valve (not shown) opens, so that the compression chamber 135 and the suction muffler 143 are communicated with each other via the suction hole 137 . Thereby, the refrigerant gas 109 is guided from the refrigerant circuit to the interior of the sealed container 101 , and suctioned into the interior of the compression chamber 135 through the suction muffler 143 and the suction hole 137 .
- the volume of the compression chamber 135 decreases according to the motion of the piston 125 toward the valve plate 133 . Therefore, the pressure in the interior of the compression chamber 135 increases. Due to a pressure difference between the interior of the suction muffler 143 and the interior of the compression chamber 135 , the suction valve (not shown) closes. Then, the refrigerant gas 103 in the interior of the compression chamber 135 is compressed, and the pressure in the interior of the compression chamber 135 further increases.
- the discharge valve 145 opens due to a pressure difference between an interior of the discharge chamber 147 and the interior of the compression chamber 135 .
- the compressed refrigerant gas 103 is discharged from the discharge hole 139 to the discharge chamber 147 inside of the cylinder head 141 .
- the refrigerant gas 103 discharged to the discharge chamber 147 flows through the discharge pipe 149 and is sent out from the exit pipe 151 to the refrigerant circuit outside of the sealed container 101 , thus forming a refrigeration cycle.
- the piston 125 moves in the direction in which the projection 155 moves into the discharge hole 139 .
- the tip end surface 153 of the piston 125 gets closer to the valve plate 133 , and the projection 155 gets closer to the discharge hole 139 which faces the projection 155 .
- the discharge valve 145 opens.
- the refrigerant gas 103 compressed in the interior of the compression chamber 135 is discharged to the interior of the discharge chamber 147 inside of the cylinder head 141 all at once via the discharge hole 139 , as indicated by arrows in FIG. 3 .
- the projection 155 of the piston 125 moves into the discharge hole 139 .
- the compression stroke finishes in a state in which a portion of the compressed refrigerant gas 103 is left within the dead volume (portion expressed as meshed pattern) defined by the projection 155 and the discharge hole 139 .
- the flow of the refrigerant gas 103 in the interior of the compression chamber 135 in the compression stroke is a three-dimensional flow in which a flow velocity and a flow direction change significantly, and which exhibits a complicated behavior.
- the refrigerant gas 9 flows toward the peripheral walls (side walls) of the projection 31 , which causes a turbulent (disordered) flow.
- the projection 155 provided on the tip end surface 153 of the piston 125 has a substantially rectangular parallelepiped shape having the four side walls 165 a , 165 b , 165 c , 165 d , the refrigerant gas 103 is less likely to flow toward the peripheral portions of the projection 155 .
- a flow passage (portion expressed as meshed pattern in FIG. 3 ) defined by the discharge hole 139 and the projection 155 is narrower, as the piston 125 moves in the direction in which the projection 155 moves into the discharge hole 139 .
- the refrigerant gas 103 present in the vicinity of the inner wall of the cylinder 113 flows toward the discharge hole 139 along the tip end surface 153 and its flow is blocked by the side walls 165 b , 165 d of the projection 155 (collides against the side walls 165 b , 165 d of the projection 155 ).
- the refrigerant gas 103 flows along the side walls 165 b , 165 d and is guided to inside of the discharge hole 139 . It is estimated that at corner portions formed by the side walls 165 b , 165 d and the adjacent side walls 165 a , 165 c , a turbulent flow occurs, but a flow component guided to inside of the discharge hole 139 increases.
- a base portion of the tip end surface 153 of the piston 125 from which the projection 155 projects is the curved surface 171 .
- the volume of the dead volume defined by the projection 155 and the discharge hole 139 significantly affects the efficiency of the sealed compressor 100 .
- the shape of the projection 155 of the piston 125 affects the efficiency of the sealed compressor 100 , to a degree equal to or more than that of the volume of the dead volume.
- FIG. 5 is a view showing a characteristic indicating a relationship between the gradient ⁇ of the side surface of the projection, and coefficient of performance COP in the sealed compressor according to Embodiment 1.
- a horizontal axis indicates the gradient ⁇ formed between the side wall 165 a of the projection 155 and the tip end surface 153 of the piston 125
- a vertical axis indicates the coefficient of performance COP.
- a measurement result of FIG. 5 is of the compressor 100 having a cylinder volume of 6.0 cc and an operating frequency of 50 Hz. As can be seen from FIG. 5 , it was confirmed through the experiment that the efficiency was higher when the gradient ⁇ of the side wall 165 a of the projection 155 was in a range of 65 degrees ⁇ 80 degrees.
- the gradient ⁇ formed between the side wall 165 a facing the suction hole 137 and having a larger area and the tip end surface 153 of the piston 125 is set in a range of 65 degrees ⁇ 80 degrees. This causes a passage area of a flow passage defined by the side wall 165 a and the inner peripheral surface of the discharge hole 139 to be greater than a passage area of a flow passage defined by each of the side walls 165 b , 165 c , 165 d and the inner peripheral surface of the discharge hole 139 .
- the gradient ⁇ of the side wall 165 a is set smaller than the gradient ⁇ of the side walls 165 b , 165 c , 165 d . This reduces a passage resistance of the flow of the refrigerant gas along the side wall 165 a , which allows the refrigerant gas 103 of a larger amount to be guided to the discharge hole 139 .
- the passage resistance of the refrigerant gas 103 which is caused by the structure in which the projection 155 and the inner peripheral surface of the discharge hole 139 are close to each other, is reduced.
- the flow of the refrigerant gas 103 is more effectively faired, the amount of the refrigerant gas 103 left in the interior of the compression chamber 135 without being discharged, is reduced, and a suction loss which would otherwise be caused by re-expansion of the refrigerant gas 103 left in the interior of the compression chamber without being discharged, at a time point just before the suction stroke starts, is reduced.
- electric input to the compressor 100 can be effectively reduced (coefficient of performance COP can be improved).
- the refrigerant gas 103 guided toward the discharge hole 139 along the side wall 165 a increases in amount.
- the refrigerant gas 103 guided toward the discharge hole 139 along the side wall 165 a interferes with the refrigerant gas 103 guided toward the discharge hole 139 along the side wall 165 c , causing a turbulent flow. Thereby, all of the refrigerant gas 103 does not flow out of the compression chamber 135 and a portion of the refrigerant gas 103 is left (remains) in the compression chamber 135 .
- the result of the experiment supports that in addition to the volume of the dead volume, the shape of the discharge hole 139 , and the shape of the projection 155 of the piston 125 , the gradient ⁇ formed between the side wall 165 a closest to the center axis 169 of the suction hole 137 , among the four side walls 165 a , 165 b , 165 c , 165 d of the projection 155 , and the tip end surface 153 of the piston 125 , affects the efficiency of the compressor 100 .
- Embodiment 1 It was also confirmed through the experiment that the projection 155 of Embodiment 1 is able to improve the efficiency of the compressor 100 in operating frequencies which is near the operating frequency of 50 Hz described with reference to FIG. 5 , although there is a difference in improvement of efficiency among the operating frequencies.
- the compressor 100 of Embodiment 1 is able to achieve further energy saving in the case of using the setting of the gradient ⁇ of the side wall 165 a of the projection 155 and inverter actuation control by plural operating frequencies including 50 Hz.
- the refrigerant gas 103 is smoothly guided toward the discharge hole 139 by providing the bell mouth portion 173 in the periphery of the entrance of the discharge hole 139 , a loss in the entrance of the discharge hole 139 can be lessened.
- the flow of the refrigerant gas 103 is made smooth by a synergetic effect produced by the projection 155 and the bell mouth portion 173 . Therefore, the refrigerant gas 103 left in the interior of the compression chamber 135 without being discharged, at the end of the compression stroke, is reduced.
- valve plate 133 is provided with the bell mouth portion 173 , the present invention is not limited to this.
- the valve plate 133 may not be provided with the opening 173 .
- Embodiment 1 by forming the discharge hole 139 such that its opening area increases from the compression chamber 135 side toward an opposite side of the compression chamber 135 (discharge chamber 147 side), the area of the flow passage defined by the projection 155 and the inner wall of the discharge hole 139 can be increased, and thus, the passage resistance of the refrigerant gas 103 flowing through the discharge hole 139 can be reduced.
- the cross-sectional area of the flow passage defined by the projection 155 and the inner wall of the discharge hole 139 increases toward an exit of the discharge hole 139 (discharge chamber 147 ). Because of this, the passage resistance is reduced, which allows the refrigerant gas 103 to easily flow into the discharge chamber 147 . In this way, the refrigerant gas 103 left in the interior of the compression chamber 135 without being discharged, at the end of the compression stroke, can be reduced, and hence a loss which would otherwise be caused by re-expansion of the refrigerant gas 103 left in the interior of the compression chamber 135 without being discharged, can be reduced. As a result, electric power input to the compressor 100 can be reduced in amount.
- Embodiment 1 the discharge hole 139 is formed such that its opening area increases from the compression chamber 135 side toward an opposite side of the compression chamber 135 , the present invention is not limited to this. It is expected that even the discharge hole 139 of a cylindrical shape having a uniform opening area can improve the efficiency as compared to the conventional sealed compressor 1 , although there is some difference in improvement of the efficiency from that of the structure in which the opening area increases from the compression chamber 135 side toward an opposite side of the compression chamber 135 . Therefore, this configuration may be used.
- FIG. 6 is a perspective view showing major components of a piston according to modified example of Embodiment 1.
- the compressor 100 according to Modified example 1 has basically the same configuration as that of the compressor 100 of Embodiment 1, but is different from the same in shape of the projection 155 of the piston 125 .
- the projection 155 has substantially a truncated cone shape, and a flat surface 155 a is formed on a portion of the truncated cone shape.
- the flat surface 155 a is formed such that a gradient of the flat surface 155 a with respect to the tip end surface 153 of the piston 125 is the gradient ⁇ .
- the compressor 100 according to Modified example 1 so configured can achieve the same advantages as those of the compressor 100 of Embodiment 1.
- a sealed compressor of the present invention is a sealed compressor which has a high productivity and a high efficiency and is inexpensive, and is applicable to a sealed compressor for use in a refrigeration cycle and incorporated in various refrigeration units.
- An article storage device incorporating such a sealed compressor is used as various devices such as refrigerators for household uses, dehumidification machines, show cases, and vending machines, and is applicable as various storage devices which can lessen electric power consumption.
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Abstract
Description
- The present invention relates to a sealed compressor for use in a refrigeration cycle such as an electric refrigerator, an air conditioner, and a refrigerator-freezer.
- In recent years, energy-saving refrigerators for household use have been developed. Sealed compressors incorporated into the refrigerators for household use have been developed to attain higher efficiency.
- Under the circumstances, conventionally, there is a sealed compressor incorporated into the refrigerator for household use, in which to improve efficiency, a piston is provided with a projection to reduce a dead volume of a discharge hole, to reduce a loss which would otherwise be caused by re-expansion of a compressed gas, and to thereby suppress a reduction of a refrigeration ability (see, e.g., Patent Literature 1).
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FIG. 7 is a longitudinal sectional view of the conventional sealed compressor disclosed inPatent Literature 1.FIG. 8 is a perspective view of a piston of the conventional sealed compressor.FIG. 9 is a cross-sectional view of major components of the conventional sealed compressor, which is taken along A-A ofFIG. 8 . - As shown in
FIGS. 7 to 9 , a conventional sealedcompressor 1 includes acompression component 5 and anelectric component 7 which are accommodated into a sealed container 3, and its internal space is filled with a refrigerant gas 9. - The
compression component 5 has a configuration in which apiston 13 is reciprocatingly inserted into acylinder 11 of a substantially cylindrical shape, and is connected to aneccentric shaft 19 of acrankshaft 17 via aconnecting means 15. - A
valve plate 25 having asuction hole 21 and adischarge hole 23 is provided at an end portion of thecylinder 11. Thevalve plate 25 is provided with a suction valve (not shown) and adischarge valve 27 to open and close thesuction hole 21 and thedischarge hole 23, respectively. - The
cylinder 11, thevalve plate 25 and thepiston 13 define acompression chamber 29. According to a rotation of thecrankshaft 17 for transmitting a rotational power of theelectric component 7, thepiston 13 reciprocates inside of thecylinder 11, which constitute a compression mechanism for suctioning the refrigerant gas 9 into thecompression chamber 29, compressing the refrigerant gas 9 in thecompression chamber 29, and discharging the refrigerant gas 9 out of thecompression chamber 29. - As shown in detail in
FIGS. 8 and 9 , the conventional sealedcompressor 1 is configured such that thepiston 13 is provided with aprojection 31 on an end surface (tip end surface) at thevalve plate 25 side in a position in which theprojection 31 enters (moves into) thedischarge hole 23, to reduce a dead volume (region expressed as meshed pattern) of thedischarge hole 23. - To reduce a change in the refrigerant gas 9 in a
flow direction 39 of the refrigerant gas 9, side surfaces of theprojection 31 of thepiston 13 are set such that a gradient thereof changes continuously in a circumferential direction, is minimum in a region of aside surface 33 and is maximum in a region of aside surface 35. - An inner
peripheral surface 37 of thedischarge hole 23 has a gradient (slope) set so that the innerperipheral surface 37 is substantially parallel to theside surface 33 and theside surface 35 of theprojection 31 of thepiston 13. - Regarding a fluid technique, there is known a book which discloses a technique for reducing a loss of the fluid in a peripheral region of an entrance of a discharge hole through which the fluid is discharged, which loss is caused by a flow of the fluid, by forming a bell mouth having a circular-arc cross-section in the peripheral region of the entrance (see, e.g., Non-patent Literature 1).
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- U.S. Pat. No. 5,980,223 specification
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- Non-patent Literature 1: Basic Engineering Fluid Dynamics Third revision version (Baifukan 1990 p. 184 to 185)
- In the structure shown in
FIG. 9 , theside surface 33 having a gentle slope (small gradient) in theprojection 31 can reduce a change in the refrigerant gas 9 in theflow direction 39. However, since theprojection 31 has a truncated cone shape, a portion of the refrigerant gas 9 which should flow from thesuction hole 21 to thedischarge hole 23 flows toward peripheral walls (side surfaces) of theprojection 31. - Because of this, on an end surface (tip end surface) of the
projection 31, portions of the refrigerant gas 9 flowing from the entire side surfaces interfere with each other, which causes a turbulent (disordered) flow. This results in a situation in which some of the refrigerant gas 9 does not flow out of thecompression chamber 29 into thedischarge hole 23, but is left in the interior of thecompression chamber 29, and the refrigerant gas 9 left (remaining) in the interior of thecompression chamber 29 without being discharged re-expands according to a suction operation of thepiston 13. As a result, a suction loss or the like is generated. Under the circumstances, the dead volume cannot be reduced effectively, and the flow of the refrigerant gas cannot be improved effectively in the sealedcompressor 1. - It is assumed that the configuration disclosed in the above mentioned Non-patent
Literature 1 is applied to thedischarge hole 23 of the above described conventional sealedcompressor 1. However, it is estimated that adequate advantages cannot be expected due to a loss of the refrigerant gas (complicated behavior of the refrigerant gas) in the vicinity of thedischarge hole 23, which is associated with theprojection 31. - The present invention is directed to solving the above described problem associated with the prior art, and an object of the present invention is to provide a sealed compressor which can attain a high efficiency, in which a dead volume is reduced to reduce a loss caused by re-expansion of a refrigerant gas, and a flow of the refrigerant gas is improved to reduce a loss of a discharged refrigerant gas in an interior of a compression chamber and a discharge hole.
- To solve the problem associated with the prior art, a sealed compressor of the present invention comprises an electric component; a compression component actuated by the electric component; and a sealed container accommodating the electric component and the compression component; wherein the compression component includes: a cylinder block defining a compression chamber; a piston which reciprocates in an interior of the compression chamber; and a valve plate disposed to close an opening end of the compression chamber and having a suction hole through which a refrigerant gas to be compressed in the interior of the compression chamber flows into the interior of the compression chamber, and a discharge hole through which the refrigerant gas compressed in the interior of the compression chamber is discharged from the interior of the compression chamber; wherein the piston is provided with a projection on a tip end surface which faces the valve plate; and wherein the projection is configured such that side surfaces thereof include at least one flat surface and a gradient α of the flat surface with respect to the tip end surface of the piston is smaller than a gradient β of another side surface of the projection with respect to the tip end surface of the piston.
- In this configuration, since the projection provided on the tip end surface of the piston enters (moves into) the discharge hole, a dead volume can be reduced, and re-expansion of the refrigerant gas can be reduced. As a result, efficiency of the compressor can be improved. In addition, in the flow of the refrigerant gas from the suction hole toward the discharge hole, the refrigerant gas collides against the flat surface and is prevented from flowing toward the peripheral walls extending in an axial direction of the projection. The refrigerant gas can be efficiently guided toward the discharge hole along the flat surface. Therefore, the amount of the refrigerant gas left in the interior of the compression chamber without being discharged, at the end of a compression stroke, can be lessened, and a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged, can be reduced.
- A sealed compressor of the present invention is capable of reducing a loss of a flow of a discharged gas in an interior of a compression chamber and a discharge hole and of reducing a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged. Therefore, the sealed compressor of the present invention can increase its efficiency.
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FIG. 1 is a longitudinal sectional view of a sealed compressor according toEmbodiment 1. -
FIG. 2 is a perspective view showing major components of a piston of the sealed compressor according toEmbodiment 1. -
FIG. 3 is a cross-sectional view of the piston of the sealed compressor according toEmbodiment 1, which is taken along B-B ofFIG. 2 . -
FIG. 4 is a schematic view showing a tip end surface of the piston of the sealed compressor according toEmbodiment 1, when viewed from a direction in which the piston retracts. -
FIG. 5 is a view showing a characteristic indicating a relationship between a gradient α of a side surface of a projection, and coefficient of performance COP in the sealed compressor according toEmbodiment 1. -
FIG. 6 is a perspective view showing major components of a piston according to a modified example ofEmbodiment 1. -
FIG. 7 is a longitudinal sectional view of a sealed compressor disclosed inPatent Literature 1. -
FIG. 8 is a perspective view of a piston of the sealed compressor disclosed inPatent Literature 1. -
FIG. 9 is a cross-sectional view of the piston of the sealed compressor disclosed inPatent Literature 1, which is taken along A-A ofFIG. 8 . - A sealed compressor of the present invention comprises an electric component; a compression component actuated by the electric component; and a sealed container accommodating the electric component and the compression component; wherein the compression component includes: a cylinder block defining a compression chamber; a piston which reciprocates in an interior of the compression chamber; and a valve plate disposed to close an opening end of the compression chamber and having a suction hole through which a refrigerant gas to be compressed in the interior of the compression chamber flows into the interior of the compression chamber, and a discharge hole through which the refrigerant gas compressed in the interior of the compression chamber is discharged from the interior of the compression chamber; wherein the piston is provided with a projection on a tip end surface which faces the valve plate; and wherein the projection is configured such that side surfaces thereof include at least one flat surface and a gradient α of the flat surface with respect to the tip end surface of the piston is smaller than a gradient β of another side surface of the projection with respect to the tip end surface of the piston.
- With this configuration, a dead volume formed in the discharge hole can be reduced, and a suction loss which would otherwise be caused by re-expansion of the refrigerant gas can be reduced. As a result, efficiency of the compressor can be improved. In addition, the refrigerant gas is prevented from flowing toward the side surfaces of the projection by the flat surface having the gradient α. Moreover, since the gradient α of the flat surface is set smaller than the gradient β of another side surface, a passage resistance of the flow of the refrigerant gas along the flat surface can be reduced.
- As a result, the refrigerant gas colliding against the flat surface and is prevented from flowing toward the peripheral walls by the flat surface can be efficiently guided toward the discharge hole. Therefore, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of a compression stroke, can be lessened, and a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged, can be reduced. Thus, efficiency of the sealed compressor can be improved.
- In the sealed compressor of the present invention, the flat surface having the gradient α may be placed to face the suction hole.
- In such a configuration, the refrigerant gas flowing into the compression chamber through the suction hole can be more efficiently guided to flow toward the discharge hole along the flat surface. In particular, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke, can be further reduced. As a result, a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged, can be reduced. Thus, efficiency of the sealed compressor can be further improved.
- In the sealed compressor of the present invention, the discharge hole may have an opening area which increases from the compression chamber side toward an opposite side of the compression chamber.
- In this configuration, an area of a flow passage defined by the side surface of the projection and the inner peripheral surface of the discharge hole can be increased. Because of this, it becomes possible to reduce a passage resistance of the refrigerant gas flowing through the discharge hole. As a result, the compressed refrigerant gas can be smoothly discharged from the discharge hole, excessive compression of the refrigerant gas during the compression stroke can be reduced, and the amount of electric power input to the sealed compressor can be reduced.
- In the sealed compressor of the present invention, an opening portion of the discharge hole in the valve plate, which opening portion is at the compression chamber side, may have a circular-arc cross-section.
- In this configuration, the refrigerant gas can be guided to the discharge hole more smoothly. As a result, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke, can be reduced. Therefore, a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged can be reduced, and hence efficiency of the sealed compressor can be further improved.
- In the sealed compressor of the present invention, a cross-section of the projection which is taken along a plane which is substantially parallel to the tip end surface of the piston may have a polygonal shape.
- In this configuration, the refrigerant gas collides against plural flat surfaces defining the polygonal shape, and is prevented from flowing toward the side surfaces of the projection by the flat surfaces. The portions of the refrigerant gas colliding against the plural flat surfaces flow along the flat surfaces, and therefore can be guided toward the discharge hole. Thus, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke, can be further reduced. As a result, a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged can be reduced, and hence efficiency of the sealed compressor can be further improved.
- In the sealed compressor of the present invention, a cross-section of the projection which is taken along a plane which is substantially parallel to the tip end surface of the piston may have a rectangular shape.
- In this configuration, the refrigerant gas flowing toward the discharge hole is guided along the four flat surfaces defining the projection. Therefore, the flow to the side surfaces of the projection can be suppressed, and the refrigerant gas can be smoothly guided toward the discharge hole. Moreover, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke, can be reduced, and a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged, can be reduced. As a result, efficiency of the sealed compressor can be further improved.
- In the sealed compressor of the present invention, the gradient α may be in a range of 65 degrees≦α≦80 degrees.
- In this configuration, the refrigerant gas can be flowed smoothly toward the discharge hole. Especially, the amount of the refrigerant gas left (remaining) in the interior of the compression chamber without being discharged, at the end of the compression stroke, can be reduced, a suction loss which would otherwise be caused by re-expansion of the refrigerant gas left in the interior of the compression chamber without being discharged can be reduced, and efficiency of the sealed compressor can be further improved.
- Hereinafter, embodiments of the present invention will be described with reference to the drawings. Throughout the drawings, the same or corresponding components are designated by the same reference symbols, and will not be described in repetition. In addition, throughout the drawings, components required to describe the present invention are depicted and the other components are not illustrated. Moreover, the present invention is not limited to the embodiments described below.
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FIG. 1 is a longitudinal sectional view of a sealed compressor according toEmbodiment 1.FIG. 2 is a perspective view showing major components of a piston of the sealed compressor according toEmbodiment 1.FIG. 3 is a cross-sectional view of the piston of the sealed compressor according toEmbodiment 1, which is taken along B-B ofFIG. 2 .FIG. 4 is a schematic view showing a tip end surface of the piston of the sealed compressor according toEmbodiment 1, when viewed from a direction in which the piston retracts. - As shown in
FIG. 1 , in a sealed compressor (hereinafter will be referred to as a compressor) 100, arefrigerant gas 103 is filled into a sealedcontainer 101. The sealedcontainer 101 accommodates acompression component 107 and anelectric component 105 for actuating thecompression component 107. Thecompression component 107 and theelectric component 105 are elastically supported on the sealedcontainer 101 by means of asuspension spring 109. - The
compression component 107 mainly includes acrankshaft 111 for converting a rotational motion of theelectric component 105 into a reciprocation motion, and acylinder block 115 including acylinder 113 defining acompression chamber 135 of a substantially cylindrical shape. - The
crankshaft 111 includes amain shaft section 119 to which arotor 117 of theelectric component 105 is fastened and aneccentric section 121 having a center axis which is eccentric with respect to themain shaft section 119. Themain shaft section 119 is supported on a mainshaft bearing unit 123 of thecylinder block 115. - A
piston 125 is reciprocatingly inserted into thecylinder 113. Thepiston 125 is connected to theeccentric section 121 of thecrankshaft 111 via a connectingmeans 127. That is, one end of the connecting means 127 is rotatably connected to theeccentric section 121 of thecrankshaft 111, while the other end thereof is rotatably connected to apiston pin 129 attached to thepiston 125. This allows the connecting means 127 to convert a rotational motion of theeccentric section 121 caused by a rotation of thecrankshaft 111 into a reciprocation motion and transmit the reciprocation motion to thepiston 125. - A
valve plate 133 is attached to anend portion 131 of thecylinder 113. Thevalve plate 133 closes the end portion 131 (compression chamber 135) of thecylinder 113. Thevalve plate 133 is provided with asuction hole 137 and adischarge hole 139 each of which has a circular opening. A shape of thedischarge hole 139 will be described later. - The
valve plate 133 is provided with a suction valve (not shown) for opening and closing thesuction hole 137 and a discharge valve 145 (seeFIG. 3 ) for opening and closing thedischarge hole 139. A configuration (shape) of the suction valve and a configuration (shape) of thedischarge valve 145 are well-known, and therefore detailed description thereof will be omitted. - The
valve plate 133 is covered with acylinder head 141. Inside of thecylinder head 141, adischarge chamber 147 communicated with thedischarge hole 139 is provided. Adischarge pipe 149 is connected to thedischarge chamber 147. Anexit pipe 151 is connected to thedischarge pipe 149 such that theexit pipe 151 extends to outside of the sealedcontainer 101. Furthermore, as shown inFIG. 1 , asuction muffler 143 is retained between thecylinder head 141 and thevalve plate 133. - As shown in
FIG. 3 , thedischarge hole 139 provided in thevalve plate 133 is formed such that its opening area increases in a direction from thecompression chamber 135 side toward an opposite side (discharge chamber 147 side) of thecompression chamber 135. Anopening portion 173 of thedischarge hole 139 in thevalve plate 133, which opening portion is at thecompression chamber 135 side, has a circular-arc cross-section. In more detail, the cross-section of theopening portion 173 which is taken along a direction in which thepiston 125 moves has a circular-arc shape which is round. A radius of the circular-arc of theopening portion 173 of thedischarge hole 139 may be set as desired. Hereinafter, theopening portion 173 of the circular-arc shape will be referred to as abell mouth portion 173. - The
discharge hole 139 has a size to allow aprojection 155 of thepiston 125 to easily move thereinto. As shown inFIG. 4 , thedischarge hole 139 is provided in a position of acenter axis 159 which is eccentric outward relative to acenter axis 157 of thecompression chamber 135. - Therefore, a
center axis 161 of theprojection 155 is provided in a position so that theprojection 155 closes and exposes thedischarge hole 139 during the reciprocation motion of thepiston 125, and (substantially) conforms to thecenter axis 159 of thedischarge hole 139. That is, thecenter axis 161 of theprojection 155 is in the position which is eccentric outward relative to thecenter axis 157 of thecompression chamber 135 and thecenter axis 163 of the piston 125 (substantially) conforming to thecenter axis 157. - As shown in
FIG. 4 , the projection 155 (discharge hole 139) and thesuction hole 137 provided in thevalve plate 133 do not overlap with each other when viewed from the direction in which thepiston 125 moves. Specifically, thesuction hole 137 is positioned within a projection plane (hatched region) from a line X which is an extended line of a side of the projection 155 (bottom of aside wall 165 a as will be described later) which is closest to thecenter axis 163 of thepiston 125 to a region which is beyond thecenter axis 163 of thepiston 125. - As shown in
FIGS. 2 to 4 , atip end surface 153 of thepiston 125 at thevalve plate 133 side (surface facing the valve plate 133) is provided with theprojection 155 such that theprojection 155 overlaps with thedischarge hole 139 when viewed from the direction in which thepiston 125 moves. Theprojection 155 is integral with thepiston 125, and closes and exposes thedischarge hole 139 according to the reciprocation motion of thepiston 125. - The
projection 155 has a rectangular shape in cross-section which is taken along a plane parallel to thetip end surface 153 of thepiston 125, i.e., substantially rectangular-parallelepiped shape (including truncated pyramid shape), and has four flat surfaces (hereinafter will be referred to as side walls) 165 a, 165 b, 165 c, 165 d, and atop surface 167. Theprojection 155 has a shape in which thetop surface 167 perpendicular to thecenter axis 163 of thepiston 125 has a substantially rectangular shape. - The
projection 155 is configured such that a gradient (slope) formed between the fourside walls tip end surface 153 of thepiston 125 is less than 90 degrees. In other words, theprojection 155 is configured such that the cross-section which is taken along a plane parallel to thetip end surface 153 of thepiston 125 has an area which is reduced toward a top portion (top surface 167) which is distant from thetip end surface 153 of thepiston 125. - As shown in
FIG. 4 , theside wall 165 a of theprojection 155 is oriented such that an angle θ (hereinafter will be referred to as placement angle) formed between the line X and a line Y passing through the center axis (center) 169 of thesuction hole 137 and the center axis (center) 163 of thepiston 125, is set to about 52 degrees. - The placement angle θ may be defined as a placement relationship in which a line Z which is perpendicular to the
side wall 165 a and passes through a center of theside wall 165 a crosses the line Y passing through thecenter axis 169 of thesuction hole 137 and thecenter axis 163 of thepiston 125 at a predetermined angle. - As shown in
FIG. 3 , a gradient (slope) a formed between theside wall 165 a and thetip end surface 153 of thepiston 125 is set to 70 degrees. According to a result of an experiment as described later, the gradient α may be set to a desired value in a range of 65 degrees≦α≦80 degrees, and may be α≦79 degrees. Note that there is a little tolerance in the gradient α because thepiston 125 and theprojection 155 are molded using a die. - A gradient (slope) β formed between
other side walls tip end surface 153 of thepiston 125 is set to about 85 degrees. The gradient β is an angle except for a draft angle (about 5 degrees) during the above stated die molding, and may be set to a desired value. The gradient α and the gradient β are set such that the gradient α is smaller than the gradient β. - A
curved surface 171 having a specified diameter is formed in a portion (base end portion of the projection 155) of thetip end surface 153 of thepiston 125 which theside wall 165 a of theprojection 155 crosses. In other words, theside wall 165 a of theprojection 155 partially has thecurved surface 171. - [Operation and Advantage of Sealed Compressor]
- Next, operation and advantages of the sealed
compressor 100 configured as described above will be described. In thecompressor 100, as should be well-known, a refrigerant circuit connecting a condenser (not shown), a pressure-reducer (not shown), and an evaporator (not shown) is connected between a suction pipe (not shown) and theexit pipe 161, thus constituting a well-known refrigeration cycle. As therefrigerant gas 103 to be compressed, R600 a is used. - When the
electric component 105 is supplied with an electric current, therotor 117 rotates and thecrankshaft 111 rotates. A rotational motion of theeccentric section 121 of thecrankshaft 111 is transmitted to thepiston 125 via the connectingmeans 127. This causes thepiston 125 to reciprocate inside of thecylinder 113. - In a suction (intake) stroke in which the
piston 125 moves from a top dead center toward a bottom dead center, the volume of thecompression chamber 135 increases according to the motion of thepiston 125 toward thecrankshaft 111. Therefore, the pressure in the interior of thecompression chamber 135 decreases. Due to a pressure difference between an interior of thesuction muffler 143 and the interior of thecompression chamber 135, the suction valve (not shown) opens, so that thecompression chamber 135 and thesuction muffler 143 are communicated with each other via thesuction hole 137. Thereby, therefrigerant gas 109 is guided from the refrigerant circuit to the interior of the sealedcontainer 101, and suctioned into the interior of thecompression chamber 135 through thesuction muffler 143 and thesuction hole 137. - Then, in a compression stroke in which the
piston 125 moves from the bottom dead center toward the top dead center, the volume of thecompression chamber 135 decreases according to the motion of thepiston 125 toward thevalve plate 133. Therefore, the pressure in the interior of thecompression chamber 135 increases. Due to a pressure difference between the interior of thesuction muffler 143 and the interior of thecompression chamber 135, the suction valve (not shown) closes. Then, therefrigerant gas 103 in the interior of thecompression chamber 135 is compressed, and the pressure in the interior of thecompression chamber 135 further increases. - When the pressure in the interior of the
compression chamber 135 increases to a value which is equal to or higher than the pressure in the interior of thedischarge chamber 147, thedischarge valve 145 opens due to a pressure difference between an interior of thedischarge chamber 147 and the interior of thecompression chamber 135. Until thepiston 125 reaches the top dead center, the compressedrefrigerant gas 103 is discharged from thedischarge hole 139 to thedischarge chamber 147 inside of thecylinder head 141. - The
refrigerant gas 103 discharged to thedischarge chamber 147 flows through thedischarge pipe 149 and is sent out from theexit pipe 151 to the refrigerant circuit outside of the sealedcontainer 101, thus forming a refrigeration cycle. - The above described suction, compression and discharge strokes are repeated each time the
crankshaft 111 rotates, and therefrigerant gas 103 circulates within the refrigeration cycle. - The flow of the
refrigerant gas 103 discharged from thedischarge hole 139 in the above described discharge stroke, will be described in detail with reference toFIG. 3 . Herein, a description will be given of a case where it is assumed that the discharge stroke is included in the compression stroke based on the motion of thepiston 125, for the sake of convenience. - The
piston 125 moves in the direction in which theprojection 155 moves into thedischarge hole 139. In a latter half of the compression stroke, as shown inFIG. 3 , thetip end surface 153 of thepiston 125 gets closer to thevalve plate 133, and theprojection 155 gets closer to thedischarge hole 139 which faces theprojection 155. Then, according to an increase in the pressure in the interior of thecompression chamber 135, thedischarge valve 145 opens. - Upon the
discharge valve 145 opening, therefrigerant gas 103 compressed in the interior of thecompression chamber 135 is discharged to the interior of thedischarge chamber 147 inside of thecylinder head 141 all at once via thedischarge hole 139, as indicated by arrows inFIG. 3 . - When the compression stroke progresses, the
projection 155 of thepiston 125 moves into thedischarge hole 139. The compression stroke finishes in a state in which a portion of the compressedrefrigerant gas 103 is left within the dead volume (portion expressed as meshed pattern) defined by theprojection 155 and thedischarge hole 139. - The flow of the
refrigerant gas 103 in the interior of thecompression chamber 135 in the compression stroke is a three-dimensional flow in which a flow velocity and a flow direction change significantly, and which exhibits a complicated behavior. As described above, in the compressor disclosed inPatent Literature 1, since theprojection 31 has the truncated cone shape, the refrigerant gas 9 flows toward the peripheral walls (side walls) of theprojection 31, which causes a turbulent (disordered) flow. - However, in
Embodiment 1, since theprojection 155 provided on thetip end surface 153 of thepiston 125 has a substantially rectangular parallelepiped shape having the fourside walls refrigerant gas 103 is less likely to flow toward the peripheral portions of theprojection 155. - In particular, at a time point which is near the end of the compression stroke, a flow passage (portion expressed as meshed pattern in
FIG. 3 ) defined by thedischarge hole 139 and theprojection 155 is narrower, as thepiston 125 moves in the direction in which theprojection 155 moves into thedischarge hole 139. This makes the flow velocity of therefrigerant gas 103 flowing through the flow passage higher. It is estimated that this causes the refrigerant gas in the interior of thecompression chamber 135 to be guided to thedischarge hole 139 along theside walls - Specifically, the
refrigerant gas 103 present in the vicinity of the inner wall of thecylinder 113 flows toward thedischarge hole 139 along thetip end surface 153 and its flow is blocked by theside walls side walls side walls refrigerant gas 103 flows along theside walls discharge hole 139. It is estimated that at corner portions formed by theside walls adjacent side walls discharge hole 139 increases. - It is also estimated that portions of the
refrigerant gas 103 flowing from the corner portions toward theside wall 165 c of theprojection 155 collide against each other, and a portion therefrigerant gas 103 is guided to thedischarge hole 139 along the surface of theside wall 165 c. - It is estimated that the
refrigerant gas 103 flowing toward thedischarge hole 139 along thetip end surface 153 collides against theside wall 165 a, its flow is blocked by theside wall 165 a, and a flow component ofrefrigerant gas 103 which is guided to thedischarge hole 139 along the surface of theside wall 165 a increases. - In
Embodiment 1, a base portion of thetip end surface 153 of thepiston 125 from which theprojection 155 projects is thecurved surface 171. With this structure, it is expected that the flows of therefrigerant gas 103 along theside walls - It is well known that the volume of the dead volume defined by the
projection 155 and thedischarge hole 139 significantly affects the efficiency of the sealedcompressor 100. In addition, in the present invention, through an experiment, it was discovered that the shape of theprojection 155 of thepiston 125 affects the efficiency of the sealedcompressor 100, to a degree equal to or more than that of the volume of the dead volume. - Hereinafter, advantages achieved by the shape of the
projection 155 of thepiston 125 will be described. -
FIG. 5 is a view showing a characteristic indicating a relationship between the gradient α of the side surface of the projection, and coefficient of performance COP in the sealed compressor according toEmbodiment 1. InFIG. 5 , a horizontal axis indicates the gradient α formed between theside wall 165 a of theprojection 155 and thetip end surface 153 of thepiston 125, while a vertical axis indicates the coefficient of performance COP. - A measurement result of
FIG. 5 is of thecompressor 100 having a cylinder volume of 6.0 cc and an operating frequency of 50 Hz. As can be seen fromFIG. 5 , it was confirmed through the experiment that the efficiency was higher when the gradient α of theside wall 165 a of theprojection 155 was in a range of 65 degrees≦α≦80 degrees. - Next, the experiment result of the gradient α shown in
FIG. 5 will be considered, and estimation will be made as follows. - Among the four
side walls projection 155, the gradient α formed between theside wall 165 a facing thesuction hole 137 and having a larger area and thetip end surface 153 of thepiston 125, is set in a range of 65 degrees≦α≦80 degrees. This causes a passage area of a flow passage defined by theside wall 165 a and the inner peripheral surface of thedischarge hole 139 to be greater than a passage area of a flow passage defined by each of theside walls discharge hole 139. Because of this, it becomes possible to reduce a passage resistance in the flow passage defined by theside wall 165 a and the inner peripheral surface of thedischarge hole 139, and hence increase therefrigerant gas 103 guided to thedischarge hole 139, along theside wall 165 a of theprojection 155. - Furthermore, the gradient α of the
side wall 165 a is set smaller than the gradient β of theside walls side wall 165 a, which allows therefrigerant gas 103 of a larger amount to be guided to thedischarge hole 139. - That is, the passage resistance of the
refrigerant gas 103, which is caused by the structure in which theprojection 155 and the inner peripheral surface of thedischarge hole 139 are close to each other, is reduced. In association with this, the flow of therefrigerant gas 103 is more effectively faired, the amount of therefrigerant gas 103 left in the interior of thecompression chamber 135 without being discharged, is reduced, and a suction loss which would otherwise be caused by re-expansion of therefrigerant gas 103 left in the interior of the compression chamber without being discharged, at a time point just before the suction stroke starts, is reduced. As a result, electric input to thecompressor 100 can be effectively reduced (coefficient of performance COP can be improved). - If the gradient β is set smaller than 65 degrees, the
refrigerant gas 103 guided toward thedischarge hole 139 along theside wall 165 a increases in amount. However, therefrigerant gas 103 guided toward thedischarge hole 139 along theside wall 165 a interferes with therefrigerant gas 103 guided toward thedischarge hole 139 along theside wall 165 c, causing a turbulent flow. Thereby, all of therefrigerant gas 103 does not flow out of thecompression chamber 135 and a portion of therefrigerant gas 103 is left (remains) in thecompression chamber 135. Therefrigerant gas 103 left in the interior of thecompression chamber 135 without being discharged re-expends according to a suction operation of thepiston 125, and as a result, a suction loss is generated. In this way, in the sealedcompressor 100, the dead volume cannot be effectively reduced, and the flow of the refrigerant gas cannot be effectively improved. - The result of the experiment supports that in addition to the volume of the dead volume, the shape of the
discharge hole 139, and the shape of theprojection 155 of thepiston 125, the gradient α formed between theside wall 165 a closest to thecenter axis 169 of thesuction hole 137, among the fourside walls projection 155, and thetip end surface 153 of thepiston 125, affects the efficiency of thecompressor 100. - It was also confirmed through the experiment that the
projection 155 ofEmbodiment 1 is able to improve the efficiency of thecompressor 100 in operating frequencies which is near the operating frequency of 50 Hz described with reference toFIG. 5 , although there is a difference in improvement of efficiency among the operating frequencies. - Therefore, it is expected that the
compressor 100 ofEmbodiment 1 is able to achieve further energy saving in the case of using the setting of the gradient α of theside wall 165 a of theprojection 155 and inverter actuation control by plural operating frequencies including 50 Hz. - In addition, in
Embodiment 1, therefrigerant gas 103 is smoothly guided toward thedischarge hole 139 by providing thebell mouth portion 173 in the periphery of the entrance of thedischarge hole 139, a loss in the entrance of thedischarge hole 139 can be lessened. - The
refrigerant gas 103 faired in an axial direction of thedischarge hole 139 by the side walls (flat surfaces) 165 a, 165 b, 165 c, 165 d of theprojection 155 easily flows along the circular-arc contour of thebell mouth portion 173 and smoothly flows through thedischarge hole 139. - In other words, the flow of the
refrigerant gas 103 is made smooth by a synergetic effect produced by theprojection 155 and thebell mouth portion 173. Therefore, therefrigerant gas 103 left in the interior of thecompression chamber 135 without being discharged, at the end of the compression stroke, is reduced. - Therefore, in addition to the reduction of the dead volume in the
discharge hole 139 because of theprojection 155, a loss which would otherwise be caused by re-expansion of therefrigerant gas 103 left in thecompression chamber 135 without being discharged, can be reduced, and hence the input to thecompressor 100 can be reduced. Although inEmbodiment 1, thevalve plate 133 is provided with thebell mouth portion 173, the present invention is not limited to this. Thevalve plate 133 may not be provided with theopening 173. - Furthermore, in
Embodiment 1, by forming thedischarge hole 139 such that its opening area increases from thecompression chamber 135 side toward an opposite side of the compression chamber 135 (discharge chamber 147 side), the area of the flow passage defined by theprojection 155 and the inner wall of thedischarge hole 139 can be increased, and thus, the passage resistance of therefrigerant gas 103 flowing through thedischarge hole 139 can be reduced. - The cross-sectional area of the flow passage defined by the
projection 155 and the inner wall of thedischarge hole 139, which is taken along the plane parallel to thetip end surface 153, increases toward an exit of the discharge hole 139 (discharge chamber 147). Because of this, the passage resistance is reduced, which allows therefrigerant gas 103 to easily flow into thedischarge chamber 147. In this way, therefrigerant gas 103 left in the interior of thecompression chamber 135 without being discharged, at the end of the compression stroke, can be reduced, and hence a loss which would otherwise be caused by re-expansion of therefrigerant gas 103 left in the interior of thecompression chamber 135 without being discharged, can be reduced. As a result, electric power input to thecompressor 100 can be reduced in amount. - Although in
Embodiment 1 thedischarge hole 139 is formed such that its opening area increases from thecompression chamber 135 side toward an opposite side of thecompression chamber 135, the present invention is not limited to this. It is expected that even thedischarge hole 139 of a cylindrical shape having a uniform opening area can improve the efficiency as compared to the conventional sealedcompressor 1, although there is some difference in improvement of the efficiency from that of the structure in which the opening area increases from thecompression chamber 135 side toward an opposite side of thecompression chamber 135. Therefore, this configuration may be used. - Next, a sealed compressor of Modified example 1 of
Embodiment 1 will be described. -
FIG. 6 is a perspective view showing major components of a piston according to modified example ofEmbodiment 1. - As shown in
FIG. 6 , thecompressor 100 according to Modified example 1 has basically the same configuration as that of thecompressor 100 ofEmbodiment 1, but is different from the same in shape of theprojection 155 of thepiston 125. Specifically, in Modified example 1, theprojection 155 has substantially a truncated cone shape, and aflat surface 155 a is formed on a portion of the truncated cone shape. Theflat surface 155 a is formed such that a gradient of theflat surface 155 a with respect to thetip end surface 153 of thepiston 125 is the gradient α. - The
compressor 100 according to Modified example 1 so configured can achieve the same advantages as those of thecompressor 100 ofEmbodiment 1. - Numeral modifications and alternative embodiments of the present invention will be apparent to those skilled in the art in view of the foregoing description. Accordingly, the description is to be construed as illustrative only, and is provided for the purpose of teaching those skilled in the art the best mode of carrying out the invention. The details of the structure and/or function may be varied substantially without departing from the spirit of the invention.
- A sealed compressor of the present invention is a sealed compressor which has a high productivity and a high efficiency and is inexpensive, and is applicable to a sealed compressor for use in a refrigeration cycle and incorporated in various refrigeration units. An article storage device incorporating such a sealed compressor is used as various devices such as refrigerators for household uses, dehumidification machines, show cases, and vending machines, and is applicable as various storage devices which can lessen electric power consumption.
-
-
- 100 sealed compressor
- 101 sealed container
- 103 refrigerant gas
- 105 electric component
- 107 compression component
- 115 cylinder block
- 125 piston
- 133 valve plate
- 135 compression chamber
- 137 suction hole
- 139 discharge hole
- 153 tip end surface
- 155 projection
- 165 a side wall (flat surface)
- 165 b side wall (flat surface)
- 165 c side wall (flat surface)
- 165 d side wall (flat surface)
- 173 bell mouth portion
- α gradient
- β gradient
Claims (7)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011-172767 | 2011-08-08 | ||
JP2011172767A JP5828136B2 (en) | 2011-08-08 | 2011-08-08 | Hermetic compressor |
PCT/JP2012/005036 WO2013021634A1 (en) | 2011-08-08 | 2012-08-08 | Hermetic type compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140169998A1 true US20140169998A1 (en) | 2014-06-19 |
Family
ID=47668169
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/237,315 Abandoned US20140169998A1 (en) | 2011-08-08 | 2012-08-08 | Sealed compressor |
Country Status (4)
Country | Link |
---|---|
US (1) | US20140169998A1 (en) |
JP (1) | JP5828136B2 (en) |
CN (1) | CN103732919A (en) |
WO (1) | WO2013021634A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160047368A1 (en) * | 2013-04-01 | 2016-02-18 | Panasonic Intellectual Property Management Co., Ltd. | Sealed compressor and refrigeration device |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105570087B (en) * | 2016-02-26 | 2017-09-29 | 广州万宝集团压缩机有限公司 | A kind of freezer compressor Split piston |
JP6876463B2 (en) * | 2017-02-24 | 2021-05-26 | 株式会社前川製作所 | Compressor piston, compressor and heat pump unit |
CN110821785B (en) * | 2019-08-27 | 2021-05-18 | 加西贝拉压缩机有限公司 | Discharge valve runner structure that refrigerator compressor was used |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5980223A (en) * | 1995-04-28 | 1999-11-09 | Danfoss Computers Gmbh | Refrigerant compressor having an asymmetrically contoured piston |
US6623258B1 (en) * | 1999-05-25 | 2003-09-23 | Danfoss Compressors Gmbh | Axial piston refrigerant compressor with piston front face projection |
US20100316515A1 (en) * | 2009-06-12 | 2010-12-16 | Panasonic Corporation | Hermetic compressor and refrigeration system |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002130131A (en) * | 2000-10-18 | 2002-05-09 | Hitachi Ltd | Closed type motor-driven compressor |
JP2010090705A (en) * | 2008-10-03 | 2010-04-22 | Panasonic Corp | Refrigerant compressor |
CN102011724B (en) * | 2010-12-27 | 2011-12-14 | 黄石东贝电器股份有限公司 | Full enclosed reciprocating type piston refrigeration compressor |
-
2011
- 2011-08-08 JP JP2011172767A patent/JP5828136B2/en active Active
-
2012
- 2012-08-08 US US14/237,315 patent/US20140169998A1/en not_active Abandoned
- 2012-08-08 WO PCT/JP2012/005036 patent/WO2013021634A1/en active Application Filing
- 2012-08-08 CN CN201280038801.6A patent/CN103732919A/en active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5980223A (en) * | 1995-04-28 | 1999-11-09 | Danfoss Computers Gmbh | Refrigerant compressor having an asymmetrically contoured piston |
US6623258B1 (en) * | 1999-05-25 | 2003-09-23 | Danfoss Compressors Gmbh | Axial piston refrigerant compressor with piston front face projection |
US20100316515A1 (en) * | 2009-06-12 | 2010-12-16 | Panasonic Corporation | Hermetic compressor and refrigeration system |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20160047368A1 (en) * | 2013-04-01 | 2016-02-18 | Panasonic Intellectual Property Management Co., Ltd. | Sealed compressor and refrigeration device |
US10641259B2 (en) * | 2013-04-01 | 2020-05-05 | Panasonic Appliances Refrigeration Devices Sinapore | Sealed compressor and refrigeration device |
Also Published As
Publication number | Publication date |
---|---|
JP2013036381A (en) | 2013-02-21 |
CN103732919A (en) | 2014-04-16 |
JP5828136B2 (en) | 2015-12-02 |
WO2013021634A1 (en) | 2013-02-14 |
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