JP5251061B2 - Hermetic compressor - Google Patents

Description

  The present invention relates to a hermetic compressor used in a refrigerator-freezer or the like.

  In recent years, with regard to hermetic compressors used in refrigeration apparatuses such as refrigerators and refrigerators, it is desired to improve the structure of the discharge muffler to reduce noise and improve productivity and reliability.

  Conventionally, this type of hermetic compressor includes a discharge muffler in order to reduce noise generated when refrigerant compressed for the purpose of reducing noise is discharged to the outside (for example, Patent Document 1). reference).

  Hereinafter, the conventional hermetic compressor will be described with reference to the drawings.

  7 is a longitudinal sectional view of a conventional hermetic compressor described in Patent Document 1, FIG. 8 is a partial sectional view taken along line AA in FIG. 7, and FIG. 9 is a partial sectional view taken along line BB in FIG. It is.

  7 to 9, in the sealed container 2, the lubricating oil 4 is stored at the bottom, and an electric element 10 including a stator 6 and a rotor 8, and a compression element that is rotationally driven by the electric element 10. 12, and the compression element 12 is arranged above the electric element 10 and assembled together, and the inside is filled with the refrigerant gas 14.

  Next, the main configuration of the compression element 12 will be described.

  A cylinder block 20 made of cast iron (for example, FC200) includes a substantially cylindrical compression chamber 22 and a plurality of discharge mufflers 70, and a bearing portion 26.

  The valve plate 30 seals the end surface 32 of the cylinder block 20 and includes a discharge valve device (not shown) on the opposite side of the compression chamber 22.

  The head 40 is disposed on the side of the valve plate 30 opposite to the compression chamber 22, covers the valve plate 30, and forms a discharge chamber 42.

  One end of the suction muffler 50 opens into the sealed container 2 and the other end communicates with the compression chamber 22.

  The shaft 52 includes a main shaft portion 54 and an eccentric portion 56, and includes an oil supply mechanism 60 having one end communicating with the lubricating oil 4 and the other end communicating with the opening 58 at the upper end, and is supported by the bearing portion 26 of the cylinder block 20. And fixed to the rotor 8.

  The piston 62 is inserted into the compression chamber 22 so as to be slidable back and forth, and is connected to the eccentric portion 56 by a connecting mechanism 64.

  Next, the main configuration of the discharge muffler 70 will be described.

  The discharge muffler 70 includes a first discharge muffler 70 a and a second discharge muffler 70 b, and is formed by covering each upper surface opening 72 with a muffler cover 74.

  In the muffler cover 74, the outer peripheral portion 76 is pressed and fixed to the upper surface opening 72 via the seal member 77 by fastening the muffler central portion 78 with the bolt 80.

  Further, the muffler cover 74 is formed by press-molding a steel plate, and communicates with the second discharge muffler 70b through a discharge pipe 82 that is penetrated and fixed to discharge the refrigerant gas 14 to the outside of the sealed container 2. .

  Further, the first discharge muffler 70 a communicates with the discharge chamber 42 through the communication passage 44, and the first discharge muffler 70 a and the second discharge muffler 70 b communicate with each other through the communication flow path 94.

  The communication path 44 includes a path hole 46 formed in the valve plate 30 and a guide channel 48 formed in the cylinder block 20.

  The operation of the hermetic compressor configured as described above will be described below.

  When the electric element 10 is energized from an external power source (not shown), the rotor 8 rotates and the shaft 52 rotates accordingly, and the motion of the eccentric portion 56 is transmitted to the piston 62 via the coupling mechanism 64. Thus, the piston 62 reciprocates in the compression chamber 22, and the compression element 12 performs a predetermined compression operation.

  Thereby, the refrigerant gas 14 is sucked into the compression chamber 22 from the cooling system (not shown) through the suction muffler 50 and compressed, and then discharged from the discharge valve device (not shown) of the valve plate 30 to the discharge chamber 42. The

  The high-pressure refrigerant gas 14 discharged into the discharge chamber 42 passes through the communication path 44, is once released into the discharge muffler 70, flows through the first discharge muffler 70 a to the second discharge muffler 70 b, and then is discharged from the discharge pipe 82. And is discharged to a cooling system (not shown).

At this time, the high-pressure refrigerant gas 14 is released to the discharge muffler 70 and is then throttled by the discharge pipe 82, whereby the discharge pulsation due to repeated compression is attenuated and the noise of the cooling system can be kept low.
JP 2002-48062 A

  However, in the above-described conventional configuration, the muffler cover 74 made of a steel plate covers the upper opening 72 of the discharge muffler 70, and only the outer peripheral portion 76 of the muffler cover 74 is pressed and fixed to the upper opening 72. 74 has a low rigidity, and therefore, when the pulsation of the refrigerant gas 14 in the discharge muffler 70 is large, the muffler cover 74 resonates and noise increases.

  Further, since the central portion 90 of the muffler cover 74 is fastened to the muffler central portion 78 with the bolts 80, the muffler cover 74 is deformed, and a gap is formed between the outer peripheral portion 76 and the upper surface opening 72, and the discharge muffler 70. The internal high-pressure refrigerant gas 14 leaked, and the efficiency of the hermetic compressor was reduced.

  The present invention solves the above-described conventional problems, and suppresses the generation of noise due to resonance of the muffler cover even when the pulsation of the refrigerant gas in the discharge muffler is large, and prevents the leakage of refrigerant gas from the discharge muffler. An object of the present invention is to provide a hermetic compressor that is low in noise and highly reliable.

  In order to solve the above-described conventional problems, the hermetic compressor of the present invention has a discharge muffler integrally formed on the upper part of the cylinder block, and is integrally formed on the upper part of the cylinder block having a sufficient clearance from the sealed container. Since the discharge muffler is formed, the volume of the discharge muffler can be increased and the wall thickness of the discharge muffler can be increased without increasing the size of the sealed container, so that the rigidity of the discharge muffler is increased and the pulsation of the refrigerant gas is increased. Even if it is large, it has the effect of preventing resonance of the discharge muffler and suppressing the generation of noise, and since the discharge muffler is formed integrally with the cylinder block and the number of seals of the discharge muffler is reduced, the discharge muffler is sealed from the sealed container. It has the effect | action that the leak of the refrigerant gas to the inside can be prevented.

  In the hermetic compressor of the present invention, the discharge muffler is integrally formed on the upper part of the cylinder block, the rigidity of the discharge muffler is increased, and the generation of noise due to the resonance of the discharge muffler can be suppressed. Therefore, it is possible to provide a hermetic compressor with low noise and high reliability.

The invention according to claim 1 stores lubricating oil in an airtight container, and houses an electric element and a compression element disposed above the electric element, and one end of the compression element is in the lubricating oil. A shaft provided with an oil supply mechanism in which the other end communicates with the opening at the upper end, a cylinder block provided with a bearing portion supporting the shaft and the compression chamber, a piston reciprocating in the compression chamber, A valve plate that seals the end face of the cylinder block and includes a discharge valve device on the side of the non-compression chamber, a head that forms a discharge chamber that houses the discharge valve device, one end communicating with the discharge chamber, and the other end and a communication passage communicating with the discharge muffler, the discharge muffler, the Barubupu of the discharge muffler with the formed in the cylinder block integrally at the top of the bearing portion of the cylinder block Inner wall surface other than the portion that over preparative engages are integrally formed, said communication passage includes an inlet passage provided in substantially extending direction of the compression chamber is formed in a cylinder block, of the inlet passage The wall surface has the shape of the previous compression chamber so that the wall pressure between the inlet passage and the compression chamber does not become constant so that deformation of the compression chamber due to pressure load acting on the inner wall surface reduces sliding loss of the piston. On the other hand, the inner wall surface of the inlet passage is formed in the opposite direction .

  In the above configuration, since the discharge muffler is formed integrally with the cylinder block at the upper part of the cylinder block having a sufficient gap with the sealed container, the discharge muffler can increase the volume and increase the wall thickness of the discharge muffler. This increases the rigidity of the discharge muffler. Even if the pulsation of the refrigerant gas is large, the discharge muffler can be prevented from resonating and noise generation can be suppressed, and the discharge muffler is formed integrally with the cylinder block and the discharge muffler seal Since the number of locations is reduced, it is possible to prevent leakage of refrigerant gas from the discharge muffler into the sealed container, and the discharge muffler is formed integrally with the cylinder block, so that the number of parts constituting the discharge muffler can be reduced. Providing a hermetic compressor with low noise, high reliability, and high productivity Kill.

Also, even under severe operating conditions or continuous operation, even if high-temperature refrigerant gas that has been compressed and increased in pressure passes through the inlet passage and a pressure load acts on the inner wall surface, the inner wall surface of the inlet passage remains in the compression chamber. Since it is formed in a shape that reduces deformation, deformation of the compression chamber can be prevented, and in addition to the effect of the invention according to claim 1, the sliding loss of the piston due to deformation of the compression chamber is further reduced. Therefore, it is possible to realize high efficiency and high reliability while suppressing an increase in input.

According to a second aspect of the present invention, in the invention according to any one of the first to third aspects of the present invention, the cylinder block includes a leg portion that is fastened to the electric element on the lower side. The muffler is formed to include the intermediate positions of the different leg parts, and the intermediate positions of the different leg parts where the rigidity of the cylinder block is reduced are covered with the discharge muffler and formed integrally. Since the rigidity of the intermediate position between the leg portions can be increased and the rigidity between the leg portions is unnecessarily increased, the weight does not increase. By increasing the rigidity of the cylinder block by using the discharge muffler, it is possible to further reduce the size and weight and to improve the productivity by integral formation.

According to a third aspect of the present invention, in the first or second aspect of the invention, the discharge muffler is formed at a position lower than the horizontal plane of the opening of the shaft, and a centrifugal force is generated from the opening of the shaft during operation. The lubricating oil splashed horizontally by the air jumps over the outer wall of the discharge muffler and scatters on the inner wall of the sealed container. In addition to the effect of the invention according to claim 1 or 2 , the lubricating oil is further heated to prevent the viscosity from being lowered, and the sliding portion can be prevented. Thus, the lubrication of the sliding portion can be improved, the loss of the sliding portion can be reduced, and the wear of the sliding portion can be prevented.

The invention according to claim 4 is the invention according to any one of claims 1 to 3 , wherein a recess for reducing heat conduction is formed between the discharge muffler and the compression chamber. Since a recess is formed between the compression chamber and the compression chamber, it is possible to prevent the heat of the discharge muffler, which flows at a high temperature during operation, from being conducted to the compression chamber, thereby preventing the compression chamber from becoming high temperature. Therefore, in addition to the effect of the invention according to any one of claims 1 to 3 , it is possible to further prevent a reduction in compression efficiency and realize a high compression efficiency.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The present invention is not limited to the embodiments.

(Embodiment 1)
1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention, FIG. 2 is a top sectional view of the hermetic compressor according to the same embodiment, and FIG. 3 is a hermetic type according to the same embodiment. FIG. 4 is a partial cross-sectional view taken along the line CC of FIG. 1, FIG. 5 is a partial cross-sectional view taken along the line DD of FIG. 2, and FIG. 6 is a cylinder block according to the same embodiment. FIG.

  In FIGS. 1 to 6, in the sealed container 102, the lubricating oil 104 is stored at the bottom, and an electric element 110 including a stator 106 and a rotor 108, and a compression element that is rotationally driven by the electric element 110. 112, the compression element 112 is disposed above the electric element 110 and assembled together, and the inside is filled with the refrigerant gas 114.

  Next, the main configuration of the compression element 112 will be described.

  A cylinder block 120 made of cast iron (e.g., FC200) is provided with a substantially cylindrical compression chamber 122 and a discharge muffler 124 integrally formed at an upper portion thereof and a bearing portion 126.

  The valve plate 130 seals the end surface 132 of the cylinder block 120 and includes a discharge valve device (not shown) on the compression chamber 122 side.

  The head 140 is disposed on the anti-compression chamber 122 side of the valve plate 130, covers the valve plate 130, and forms a discharge chamber 142.

  The suction muffler 170 has one end opened into the sealed container 102 and the other end communicated with the compression chamber 122.

  The shaft 172 includes a main shaft portion 174 and an eccentric portion 176, and includes an oil supply mechanism 180 having one end communicating with the lubricating oil 104 and the other end communicating with the upper end opening 178.

  The main shaft portion 174 is supported by the bearing portion 126 of the cylinder block 120 and is fixed to the rotor 108.

  The outer wall 177 of the discharge muffler 124 is formed at a position lower than the horizontal plane of the opening 178 of the shaft 172.

  The piston 182 is inserted into the compression chamber 122 so as to be slidable back and forth, and is connected to the eccentric portion 176 by a connecting mechanism 184.

  A plurality of legs 186 that are fastened to the stator 106 are formed in the lower part of the cylinder block 120. The leg portion 186 includes a front leg portion 188 below the compression chamber 122 side and a rear leg portion 190 below the anti-compression chamber 122 side.

  Next, the main configuration of the discharge muffler 124 will be described.

  The discharge muffler 124 communicates with the discharge chamber 142 through a pass hole 144 formed in the valve plate 130 and a communication path 146 formed in the cylinder block 120, and an outlet path 148 is formed on the side opposite to the head 140.

  The communication passage 146 includes an inlet passage 150 in a substantially extending direction of the compression chamber 122.

  The inner wall surface 152 of the inlet passage 150 is shaped so that the pressure load 154 acting on the inner wall surface 152 reduces the deformation of the compression chamber 122, so that the wall thickness 156 between the inlet passage 150 and the compression chamber 122 is not constant. The arc shape of the compression chamber 122 is formed in a reverse arc shape.

  The outlet passage 148 communicates with a discharge pipe 162 that is fixed by brazing to a cylindrical cover 160 formed by cutting low carbon steel. The cover 160 is fixed to the cylinder block 120 through the bolt 164 through a bolt hole 166 formed in the cover 160.

  Further, the discharge muffler 124 is formed on the upper portion of the cylinder block 120 so as to include an intermediate position 191 between the front leg portion 188 and the rear leg portion 190. Further, a recess 196 is formed between the outer wall 192 of the discharge muffler 124 and the outer wall 194 of the compression chamber 122 to reduce heat conduction between the outer wall 192 of the discharge muffler 124 and the outer wall 194 of the compression chamber 122. .

  The operation of the hermetic compressor configured as described above will be described below.

  When the electric element 110 is energized from an external power source (not shown), the rotor 108 rotates and the shaft 172 rotates accordingly, and the movement of the eccentric portion 176 is transmitted to the piston 182 via the coupling mechanism 184. Thus, the piston 182 reciprocates in the compression chamber 122, and the compression element 112 performs a predetermined compression operation.

  Accordingly, the refrigerant gas 114 is sucked into the compression chamber 122 from the cooling system (not shown) through the suction muffler 170 and compressed, and then discharged from the discharge valve device (not shown) of the valve plate 130 to the discharge chamber 142. The

  The high-pressure refrigerant gas 114 discharged into the discharge chamber 142 passes through the communication hole 146 from the pass hole 144, is once opened in the discharge muffler 124, and then discharged from the outlet passage 148 through the discharge pipe 162 to the cooling system. Is done.

  At this time, the high-pressure refrigerant gas 114 is released to the discharge muffler 124 and is then throttled by the discharge pipe 162, so that the discharge pulsation due to repeated compression is attenuated and the noise of the cooling system (not shown) is kept low. Can do.

  Here, since the discharge muffler 124 is integrally formed on the upper part of the cylinder block 120 having a sufficient gap with the sealed container 102, the discharge muffler 124 can be increased in volume and the wall thickness of the discharge muffler 124 can be increased. Therefore, the rigidity of the discharge muffler 124 is also improved, and even if the pulsation of the refrigerant gas 114 is large, resonance of the discharge muffler 124 can be prevented and generation of noise can be suppressed.

  In addition, since the discharge muffler 124 is integrally formed with the cylinder block 120 and the number of seal portions of the discharge muffler 124 is reduced, the leakage of the refrigerant gas 114 from the discharge muffler 124 into the sealed container 102 can be prevented and the discharge muffler can be prevented. 124 can be formed integrally with the cylinder block 120 and the number of parts constituting the discharge muffler 124 can be reduced.

  As a result, a hermetic compressor with low noise, high reliability, and high productivity can be provided.

  Next, a description will be given of a case where the refrigerant gas 114 whose pressure has been increased by being compressed passes through the inlet passage 150 and the pressure load 154 is applied to the inner wall surface 152 under severe operating conditions or continuous operation.

  Since the inner wall surface 152 of the inlet passage 150 is formed in an arc shape opposite to the arc shape of the compression chamber 122 so that the wall thickness 156 between the inlet passage 150 and the compression chamber 122 is not constant, the inner wall surface 152 is compressed. Even if the high-pressure refrigerant gas 114 having increased pressure passes through the inlet passage 150 and the pressure load 154 acts on the inner wall surface 152, the pressure load 154 acting on the compression chamber 122 from the inner wall surface 152 of the inlet passage 150 is dispersed. The deformation of the compression chamber 122 can be prevented.

  As a result, the sliding loss of the piston 182 due to the deformation of the compression chamber 122 can be reduced, and high efficiency and high reliability can be realized while suppressing an increase in input.

  Further, the cylinder block 120 is integrally formed by covering the middle position 191 between the front leg portion 188 and the rear leg portion 190 where the rigidity is lowest with the discharge muffler 124, so that the middle position between the leg portions 186 is minimized. The rigidity of the position 191 can be increased, and the rigidity between the leg portions 186 is not unnecessarily increased, so that the weight does not increase. Therefore, the rigidity of the cylinder block 120 can be increased using the indispensable discharge muffler 124. it can.

  As a result, it is possible to realize a reduction in size and weight and an improvement in productivity by integral formation.

  Further, since the discharge muffler 124 is formed at a position lower than the horizontal plane 179 of the opening 178 of the shaft 172, the lubricating oil 104 that has been scattered horizontally by the centrifugal force from the opening 178 of the shaft 172 during operation is a high-temperature and high-pressure refrigerant gas. 114 does not scatter on the outer wall 177 of the discharge muffler 124, which becomes hot because it passes, and scatters on the inner wall surface 102 a of the sealed container 102.

  Therefore, it is possible to prevent the lubricating oil 104 from splashing on the outer wall 177 of the discharge muffler 124 and increasing the temperature, and the lubricating oil 104 is scattered to the sealed container 102 and cooled by the inner wall surface 102a.

  As a result, it is possible to prevent the lubricating oil 104 from being heated to a high temperature and to reduce the viscosity, improve the lubrication at the sliding portion, reduce the loss of the sliding portion, and prevent the sliding portion from being worn. Can do.

  In addition, since a recess 196 for reducing heat conduction is formed between the outer wall 192 of the discharge muffler 124 and the outer wall 194 of the compression chamber 122, the discharge muffler 124 that is heated to flow high temperature refrigerant gas 114 during operation. Can be prevented from conducting heat to the compression chamber 122 and causing the compression chamber 122 to reach a high temperature. Furthermore, the refrigerant gas 114 in the sealed container 102 convects and flows through the recess 196, so that the temperature of the outer wall 192 of the discharge muffler 124 and the outer wall 194 of the compression chamber 122 can be further lowered.

  As a result, further reduction in compression efficiency can be prevented and high compression efficiency can be realized.

  Since the hermetic compressor according to the present invention is formed integrally with the discharge muffler on the upper part of the cylinder block, it is possible to provide a hermetic compressor with low noise, high reliability, and high productivity. It can also be used for applications such as vending machines, freezer showcases, and dehumidifiers.

1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. Top sectional view of a hermetic compressor in the same embodiment Top view of hermetic compressor in the same embodiment Partial sectional view taken along line CC in FIG. Partial sectional view taken along line DD in FIG. Side view of cylinder block in same embodiment Vertical section of a conventional hermetic compressor Partial sectional view taken along line AA in FIG. Partial sectional view taken along line BB in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 102 Sealing container 104 Lubricating oil 110 Electric element 112 Compression element 120 Cylinder block 122 Compression chamber 124 Discharge muffler 126 Bearing part 130 Valve plate 132 End surface 140 Head 142 Discharge chamber 146 Communication path 150 Inlet path 152 Inner wall surface 172 Shaft 178 Opening part 179 Horizontal surface 180 Refueling mechanism 182 Piston 186 Leg 196 Recess

Claims (4)

The lubricating oil is stored in an airtight container, and the electric element and the compression element disposed above the electric element are accommodated. The compression element has one end communicating with the lubricating oil and the other end having an upper end opening. A shaft having an oil supply mechanism communicating with the cylinder, a cylinder block having a bearing portion supporting the shaft and a compression chamber, a piston reciprocating in the compression chamber, and an end surface of the cylinder block are sealed. And a valve plate provided with a discharge valve device on the side of the anti-compression chamber, a head that forms a discharge chamber that accommodates the discharge valve device, and a communication path with one end communicating with the discharge chamber and the other end communicating with the discharge muffler. wherein the discharge muffler, among other than the portion to be engaged with the valve plate of the discharge muffler with the formed in the cylinder block integrally at the top of the bearing portion of the cylinder block Surface is integrally formed, said communication passage includes an inlet passage provided in substantially extending direction of the compression chamber is formed in a cylinder block, the inner wall surface of the inlet passage acts on the inner wall surface pressure The inner wall surface of the inlet passage is reversed with respect to the shape of the compression chamber so that the wall pressure between the inlet passage and the compression chamber does not become constant so that deformation of the compression chamber due to load reduces sliding loss of the piston. A hermetic compressor characterized by being formed in the direction . Cylinder block is provided with a leg which is fastened to the electric element downwardly, the the upper surface projections of the cylinder block, closed type compressor according to the discharge muffler is formed to include an intermediate position of the different legs claim 1. 3. The hermetic compressor according to claim 1, wherein the discharge muffler is formed at a position lower than a horizontal plane of the opening of the shaft.   The hermetic compressor according to any one of claims 1 to 3, wherein a recess for reducing heat conduction is formed between the discharge muffler and the compression chamber.