JP5716161B2 - Hermetic compressor - Google Patents

Description

  The present invention relates to an improvement in an oil supply mechanism of a hermetic compressor mounted on a refrigeration apparatus such as a refrigerator or an air conditioner.

  In recent years, due to demands for the global environment, household refrigerators and air conditioners are increasingly moving toward energy saving.

  As a conventional hermetic compressor, instead of a centrifugal pump, as a viscous pump that can easily achieve stable pumping performance even at low speed rotation, a hollow hole is provided in the shaft, and a member is inserted to a position that penetrates the rotor. Some members have spiral grooves (see, for example, Patent Document 1).

  Similar to the configuration, there is one in which a member having a spiral groove is inserted into a sleeve attached to the lower end of the shaft (see, for example, Patent Document 2).

  The prior art hermetic compressor will be described below with reference to the drawings. In the following description, the upper and lower relationships are based on a state in which the hermetic compressor is installed in a normal posture.

  FIG. 6 is a longitudinal sectional view of a conventional hermetic compressor described in Patent Document 1. As shown in FIG.

  In FIG. 6, lubricating oil 4 is stored at the bottom of the sealed container 2, and the compressor body 6 is elastically supported by the suspension container 8 with respect to the sealed container 2.

  The compressor body 6 includes an electric element 10 and a compression element 12 disposed above the electric element 10. The electric element 10 includes a stator 14 and a rotor 16.

  The shaft 18 of the compression element 12 includes a main shaft portion 20 having a cylindrical hollow portion 60 that is a cylindrical hole inside, and an eccentric shaft portion 22 that extends above the main shaft portion 20. The rotor 16 is fitted to the main bearing 26 of the cylinder block 24 so as to be rotatable.

  The insertion portion 66 inserted into the cylindrical cavity portion 60 of the shaft 18 up to a position penetrating the rotor 16 forms a helical groove on the outer periphery, and forms a lubricating oil passage with the inner surface of the cylindrical cavity portion 60. . The lower end of the insertion portion 66 is fixed to the central portion of the bracket 64. The bracket 64 has a substantially U shape with a recessed central portion, is formed of an elastic material, and both end portions are fixed to the stator 14.

  FIG. 7 is a cross-sectional view of a main part of a conventional hermetic compressor described in Patent Document 2.

  In FIG. 7, a sleeve 62 is fixed to the lower end of the shaft 18. The sleeve 62 is a cylindrical member that is immersed at least in the lubricating oil 4 and rotates integrally with the shaft 18.

  The insertion portion 66 inserted into the sleeve 62 forms a spiral groove on the outer periphery and forms a lubricating oil passage with the sleeve 62. The lower end of the insertion portion 66 is formed of an elastic material, and both end portions are fixed to the central portion of the bracket 64 fixed to the stator 14.

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

  When the electric element 10 is energized, the rotor 16 rotates, and the shaft 18 rotates accordingly, and the compression element 12 performs a predetermined compression operation. The lubricating oil 4 is viscous in the lubricating oil passage formed between the spiral groove formed on the outer periphery of the insertion portion 66 and the cylindrical cavity 60 or the sleeve 62 as the shaft 18 and the sleeve 62 rotate. Is pulled up to the space formed above the insertion portion 66 to lubricate each sliding portion (not shown).

JP-T-2002-519589 International Publication No. 96/29516

  However, in the configuration of FIG. 6 described in Patent Document 1, since the insertion portion 66 penetrates the rotor 16 and the insertion allowance in the cylindrical cavity portion 60 is long, the acting viscous friction is increased. Further, the bracket 64 that holds the long insertion portion 66 at the lower end as described above needs to have relatively high rigidity.

  Therefore, since the degree of freedom of the insertion portion 66 is lost, the insertion portion 66 becomes difficult to move smoothly, and the friction between the cylindrical cavity portion 60 and the friction increases, resulting in an increase in input and efficiency. Had the problem of decreasing. Furthermore, the sliding surface in the cylindrical cavity 60 needs to be processed smoothly in order to prevent friction and wear with the insertion portion 66. However, the processing of the inner surface of a deep hole also reduces productivity. Have.

  Further, in the configuration of FIG. 7 described in Patent Document 2, the insertion portion 66 is short and the generated friction is small, but the lubricating oil 4 flows into the space formed above the insertion portion 66 and passes through the space. If not satisfied, it is not supplied to the sliding portion between the main shaft portion 20 and the main bearing 26. Therefore, particularly immediately after the start of operation, it takes a long time until the lubricating oil 4 is supplied to the sliding portion, which has a problem of adversely affecting the reliability.

  The present invention solves the above-mentioned conventional problems, improves the efficiency by reducing friction and improving the reliability by shortening the time until the lubricating oil is supplied to the sliding portion at the time of start-up. The purpose is to do.

  In order to solve the above-described conventional problems, a hermetic compressor according to the present invention includes a viscous pump and a centrifugal pump at a lower portion of a shaft, and the viscous pump is formed in a cylindrical cavity formed in the shaft; An insertion part inserted into the cylindrical cavity part, a spiral groove formed in a direction in which the lubricating oil rises between the inner periphery of the cylindrical cavity part and the outer periphery of the insertion part, and restraining means for preventing rotation of the insertion part The centrifugal pump is provided with a rotation synchronization means that is provided above the insertion portion in the cylindrical cavity and that brings the flow rate of the lubricating oil close to the rotational speed of the shaft. .

  Thus, by combining the viscous pump and the centrifugal pump, the length of the insertion portion of the viscous pump can be shortened, and the friction when the insertion portion slides with the cylindrical cavity portion can be reduced. In addition, by arranging a centrifugal pump above the viscous pump, a centrifugal force is applied to the flow of the lubricating oil located in the space above the insertion portion of the cylindrical cavity by the rotation synchronization means, and in a short time. The effect | action which supplies lubricating oil to an upper sliding part is acquired.

  The hermetic compressor of the present invention can reduce input by reducing friction caused by the insertion portion, improve efficiency, and shorten the time until lubricating oil is supplied to the sliding portion during startup. By doing so, generation | occurrence | production of the abrasion in a sliding part can be suppressed and reliability can be improved.

1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. Sectional drawing of the principal part of the oil supply mechanism of the hermetic compressor in the first embodiment Sectional drawing of the oil supply mechanism by the AA line of FIG. 2 of the hermetic type compressor in Embodiment 1 The perspective view of the insertion part which comprises the oil supply mechanism of the hermetic compressor in Embodiment 1 The perspective view of the rotation synchronizing means which comprises the oil supply mechanism of the hermetic compressor in Embodiment 1 Longitudinal sectional view of hermetic compressor described in Patent Document 1 Cross-sectional view of the main part of the hermetic compressor described in Patent Document 2

  According to a first aspect of the present invention, lubricating oil is stored in an airtight container, an electric element including a stator and a rotor, and a compression element disposed above the electric element are accommodated, and the compression element is A main shaft portion to which a rotor is fixed, a shaft having an eccentric shaft portion, a cylinder block having a cylinder, a piston inserted in a reciprocating manner inside the cylinder, and the piston and the eccentric shaft portion. A connecting means for connecting; a main bearing formed on the cylinder block and supporting the main shaft portion of the shaft; and a viscous pump and a centrifugal pump at a lower portion of the shaft, wherein the viscous pump is connected to the shaft A cylindrical cavity formed in the cylindrical cavity, an insertion part inserted into the cylindrical cavity, and a spiral formed between the inner periphery of the cylindrical cavity and the outer periphery of the insertion part. And a constraining means for preventing rotation of the insertion portion, wherein the centrifugal pump is disposed above the viscous pump, and the flow rate of the lubricating oil in the cylindrical cavity portion is brought close to the rotation speed of the shaft. The rotation synchronization means is provided.

  By adopting such a configuration, the length of the viscous pump can be shortened by combining the viscous pump and the centrifugal pump, and the friction when the insertion portion slides with the cylindrical cavity portion can be reduced.

  Further, by disposing a centrifugal pump above the viscous pump, a centrifugal force is applied to the lubricating oil in the space above the insertion portion in the cylindrical cavity by the rotation synchronizing means, and the sliding oil moves upward in a short time. Lubricating oil can be supplied to the moving part.

  Therefore, by reducing the friction by the insertion part, the input is reduced, the efficiency is improved, and the time until the lubricating oil is supplied to the sliding part at the start-up is shortened, so that the wear at the sliding part is reduced. Can be suppressed and reliability can be improved.

  According to a second invention, in the first invention, the rotation synchronization means includes a partition plate that divides a space in the cylindrical cavity portion into upper and lower portions and has a hole portion that communicates the upper and lower spaces in a central portion. It is what.

With this configuration, the lubricating oil that has reached the upper side of the partition plate through the hole is rotated with the surrounding wall surface integrated with the shaft. Due to the force, the oil level of the lubricating oil rises toward the outer peripheral side of the cylindrical cavity, and the lubricating oil is reliably and quickly supplied to each sliding part via the communication hole that communicates the cylindrical cavity and the outer surface of the main spindle. Can be supplied.

  Therefore, the occurrence of wear at each sliding portion can be suppressed, and in addition to the effect of the first invention, the effect of further improving the reliability can be expected.

  According to a third invention, in the first or second invention, the rotation synchronizing means is provided with a honeycomb plate provided in the cylindrical cavity and rotating integrally with a shaft.

  By adopting such a configuration, the lubricating oil that has reached the upper space in the cylindrical cavity is reliably given a rotational angular velocity by the honeycomb plate that rotates at the same speed as the shaft, and is in a state in which more centrifugal force acts.

  Therefore, the oil level of the lubricating oil rises toward the outer peripheral side of the cylindrical cavity, and the lubricating oil passes to the sliding parts in a shorter time via the communication holes that connect the cylindrical cavity and the outer surface of the main shaft part. And reliably supplied. As a result, the effect of suppressing the occurrence of wear in each sliding portion can be promoted, and the reliability can be further improved.

  According to a fourth invention, in any one of the first to third inventions, a second viscous pump communicating with the centrifugal pump is provided above the centrifugal pump.

  With such a configuration, even when the centrifugal pump has a small stroke capacity, the second viscous pump provided at the top of the centrifugal pump can supply the lubricating oil to the upper sliding portion, and the fluctuation of the power source, etc. Accordingly, even when the rotational speed of the electric element is reduced, the lubricating oil can be continuously supplied to the sliding portion, and reliability can be ensured.

  According to a fifth invention, in the fourth invention, the second viscous pump is formed by a lead groove carved on the outer periphery of the main shaft portion of the shaft and an inner peripheral surface of the main bearing that pivotally supports the main shaft portion. Formed.

  With this configuration, the lubricating oil can be supplied to the upper sliding portion while lubricating the sliding portion of the main shaft portion and the main bearing. Further, the second viscous pump can be formed integrally with the shaft in the processing step, and productivity can be improved.

  According to a sixth invention, in any one of the first to fifth inventions, the electric element is driven and controlled at a plurality of frequencies including a frequency less than a commercial frequency.

  This makes it possible to reliably supply oil to each sliding part in a short time with a viscous pump, especially when performing a low speed operation at half or less of the commercial frequency, and to suppress the occurrence of wear in the sliding part. It is possible to ensure or improve the reliability at low speed operation.

  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)
FIG. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. FIG. 2 is a cross-sectional view of a main part showing an oil supply mechanism of the hermetic compressor according to the first embodiment, and FIG. 3 is a cross-sectional view of the oil supply mechanism taken along line AA of FIG. FIG. 4 is a perspective view of an insertion portion constituting the oil supply mechanism.

  In FIG. 1 to FIG. 4, lubricating oil 104 is stored at the bottom in the sealed container 102, and the compressor main body 106 is suspended by a suspension spring 108. Furthermore, the sealed container 102 is filled with R600a (isobutane), which is a refrigerant with a low warming potential.

  The compressor body 106 includes an electric element 110 and a compression element 112 driven by the electric element 110, and a power supply terminal 113 for supplying power to the electric element 110 is attached to the sealed container 102.

  First, the electric element 110 will be described.

  The electric element 110 includes a stator 114 in which a winding (not shown) is wound directly around a plurality of magnetic pole teeth of an iron core in which steel plates are laminated via an insulating material, an inner diameter side of the stator 114, and a permanent magnet. This is a salient pole concentrated winding type DC brushless motor having a rotor 116 with a built-in magnet (not shown), and the winding of the stator 114 is connected to a power source (see FIG. (Not shown) and a conductor.

  Next, the compression element 112 will be described.

  The compression element 112 is disposed above the electric element 110. The shaft 118 constituting the compression element 112 includes a main shaft portion 120 and an eccentric shaft portion 122 extending from the upper end of the main shaft portion 120 and parallel to the main shaft portion 120. Further, the rotor 116 is fixed to the main shaft portion 120 by a method such as shrink fitting.

  The cylinder block 124 includes a main bearing 126 having a cylindrical inner surface, and the shaft 118 is supported by the main shaft 126 being inserted into the main bearing 126 in a rotatable state. The compression element 112 has a configuration of a cantilever bearing that supports the load acting on the eccentric shaft portion 122 by the main shaft portion 120 and the main bearing 126 arranged below the eccentric shaft portion 122. The front end portion of the main bearing 126 is inserted into a recess 127 provided on the inner diameter side of the rotor 116, and the width of the fitting portion between the main shaft portion 120 and the rotor 116 is less than half the height of the iron core of the rotor 116. Is set to

  The cylinder block 124 includes a cylinder 134 that is a cylindrical hole, and a piston 130 is reciprocally inserted into the cylinder 134. Further, the connecting means 136 connects the eccentric shaft portion 122 and the piston 130 by the holes provided at both ends being rotatably inserted into the piston pin 138 and the eccentric shaft portion 122 attached to the piston 130, respectively. ing.

  A valve plate 140 is attached to the end face of the cylinder 134 and forms a compression chamber 142 together with the cylinder 134 and the piston 130. Further, a cylinder head 144 is fixed so as to cover the valve plate 140 and cover it. The suction muffler 146 is molded from a resin such as PBT, forms a silencing space inside, and is attached to the cylinder head 144.

  Next, the oil supply mechanism will be described.

  The shaft 118 has a cylindrical cavity 160 inside the main shaft 120, and the opening at the lower end of the cylindrical cavity 160 is immersed in the lubricating oil 104 stored in the bottom of the sealed container 102.

  The insertion portion 166 is a substantially cylindrical member, and is provided with a thread-like spiral groove 176 on the surface and a horizontal lateral hole 177 on the lower side. Further, the outer diameter of the insertion portion 166 is slightly smaller than the inner diameter of the cylindrical cavity portion 160. The insertion portion 166 is formed of a plastic material having resistance to refrigerant and oil and having lower thermal conductivity than the metal material forming the shaft 118, such as PPS, PBT, PEEK, and the like.

  A bracket 164 serving as a restraining means for the insertion portion 166 has a substantially U shape with a recessed central portion, is formed of an elastic wire, and both end portions are fixed to the stator 114.

  The insertion portion 166 is inserted below the cylindrical cavity portion 160, and the insertion portion 166 is held at the center portion of the bracket 164 by the bracket 164 passing through the lateral hole 177 of the insertion portion 166. The insertion portion 166 is flexibly supported in the cylindrical cavity 160 of the shaft 118 by the bracket 164, and is prevented from rotating without falling off the shaft 118. Further, the height of the portion where the insertion portion 166 is inserted into the cylindrical cavity portion 160 is half or less of the entire cylindrical cavity portion 160.

  A viscous pump 150 including a helical oil supply passage is formed by the helical groove 176 of the insertion portion 166 and the cylindrical cavity portion 160.

  Further, on the upper side of the viscous pump 150, that is, on the upper side of the insertion portion 166 in the internal space of the cylindrical cavity 160, a partition plate 180 and a honey plate 182 are disposed as the rotation synchronization means 178 to form the centrifugal pump 152. .

  The partition plate 180 is a circular flat plate having a hole 181 at the center, and is fixed to the inner wall of the cylindrical cavity 160 in a substantially horizontal state with the outer diameter portion in contact with the inner surface of the cylindrical cavity 160. The space in the cylindrical cavity 160 is divided into upper and lower parts, and the upper and lower spaces communicate with each other through a hole 181. Further, the honeycomb plate 182 is a flat plate having a spring property that is disposed substantially in parallel with the central axis of the main shaft, and is fixed to the inner wall of the cylindrical cavity portion 160 with both ends pressed against the inner surface of the cylindrical cavity portion 160. It is arranged above the partition plate 180.

  Further, the shaft 118 includes a lead groove 184 that is a spiral groove on the outer surface of the main shaft portion 120, and as shown in FIG. 2, a communication that connects the lower end of the lead groove 184 and the upper space of the cylindrical cavity 160. It has a hole 170. A second viscous pump 154 formed of a spiral oil supply passage is formed by the lead groove 184 of the main shaft portion 120 and the inner surface of the main bearing 126.

  In addition, a gas vent hole 172 that communicates with the upper portion of the main shaft 120 is provided at the center of the top surface of the cylindrical cavity 160.

  With the above configuration, the lubricating oil 104 stored in the inner bottom portion of the hermetic container 102 passes through the viscous pump 150, the centrifugal pump 152, the communication hole 170, and the second viscous pump 154, and the eccentric shaft portion further upward. Each sliding portion is supplied with oil by a series of oil supply mechanisms up to 122 and the like.

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

When the electric element 110 is energized from the power supply terminal 113, the rotor 116 rotates together with the shaft 118 by the magnetic field generated in the stator 114. The eccentric rotation of the eccentric shaft portion 122 accompanying the rotation of the main shaft portion 120 is converted into a reciprocating motion by the connecting means 136, and the piston 130 is reciprocated in the cylinder 134. Then, when the volume of the compression chamber 142 changes, a compression operation is performed in which the refrigerant in the sealed container 102 is sucked into the compression chamber 142 and compressed.

  In the suction stroke accompanying this compression operation, the refrigerant in the hermetic container 102 is intermittently sucked into the compression chamber 142 via the suction muffler 146, compressed in the compression chamber 142, and then high-temperature and high-pressure refrigerant. Is sent to the refrigeration cycle (not shown) from the sealed container 102 via the discharge pipe 148 and the like.

  Next, operation | movement and an effect | action of an oil supply mechanism are demonstrated.

  First, in the viscous pump 150, the lower end of the shaft 118 is immersed in the lubricating oil 104. Therefore, as the shaft 118 rotates, the lubricating oil 104 in the spiral groove 176 of the insertion portion 166 rises as the cylindrical cavity portion 160 rotates. The lubricating oil 104 that has reached the upper end of the insertion portion 166 is temporarily accumulated in the space between the insertion portion 166 and the partition plate 180.

  Next, the lubricating oil 104 reaches the space above the partition plate 180 through the hole 181 at the center of the partition plate 180.

  When there is no partition plate 180 as in the prior art, the lubricating oil 104 accumulated on the upper portion of the insertion portion 166 is in contact with the upper surface of the insertion portion 166 that does not rotate, and viscous friction acts between the insertion portion 166 and the insertion portion 166. The rotational angular velocity is smaller than that of the main shaft portion 120.

  However, in the configuration of the first embodiment, the partition plate 180 divides the space in the cylindrical cavity 160 into upper and lower parts, and therefore, the surrounding wall surface is entirely connected to the main shaft 120 in the space above the partition plate 180. As the oil rotates at the same speed, the lubricating oil 104 rotates at (substantially) the same speed as the main shaft 120.

  In addition, since the lubricating oil is given a rotational angular velocity by the spring plate 182 that rotates integrally with the inner wall of the cylindrical cavity 160, the lubricating oil approaches the same speed as the main shaft 120 and rotates more reliably.

  As a result, a large centrifugal force acts on the lubricating oil 104, forms a parabolic oil surface 190 as shown in FIG. 1, and configures a centrifugal pump 152 that quickly supplies the lubricating oil 104 to the communication hole 170 in the upper space. can do.

  Thereafter, the lubricating oil 104 reaches the outer surface of the main shaft portion 120 through the communication hole 170, and is caused by the second viscous pump 154 on the lead groove 184 on the outer surface of the main shaft portion 120 and the inner peripheral surface of the main bearing 126. The formed lubricating oil passage is further lifted by the centrifugal force accompanying the rotation of the main shaft portion 120 and the pushing-up action, and is conveyed to each sliding portion such as the upper eccentric shaft portion 122 for lubrication.

  In this manner, by combining the viscous pump 150, the centrifugal pump 152, and the second viscous pump 154, the oil supply speed can be improved while preventing an increase in friction at the insertion portion 166.

  The configuration of the first embodiment is an inverter-driven hermetic compressor that uses a salient pole concentrated winding DC brushless motor as the electric element 110, and is driven at a plurality of frequencies including frequencies below the commercial frequency. However, by using the viscosity pump 150 and the centrifugal pump 152 in combination, it is possible to reliably supply oil even when the rotation speed is very low, such as half or less the commercial frequency, and the diameter of the main shaft 120 is small. it can.

This is because the lubricating oil 104 is inserted into the helical groove 176 of the insertion portion 166 constituting the viscous pump 150.
This is because the viscous friction force is received by the speed difference caused by the rotation of the cylindrical cavity 160 in the whole, and the configuration of the viscous pump 150 can convey the lubricating oil 104 upward even at a low rotational speed.

  In the centrifugal pump 152, the centrifugal force is surely exerted on the lubricating oil 104 by the rotation synchronizing means 178, and when used together with the viscous pump 150, the stroke required by the centrifugal pump 152 can be reduced.

  Therefore, even when the rotational speed is very low, such as less than half of the commercial frequency, or when the diameter of the main shaft 120 is small, it is possible to reliably supply oil, and it is possible to improve efficiency and reduce reliability by reducing sliding loss. Become.

  In the centrifugal pump 152, since a strong centrifugal force acts on the lubricating oil 104, the lubricating oil 104 gathers outside the rotation above the centrifugal pump 152, and a refrigerant gas with a low specific gravity gathers at the center of the rotation. It is done. Therefore, the refrigerant gas is discharged into the space inside the sealed container 102 from the gas vent hole 172 that opens at the center above the centrifugal pump 152. Therefore, even when the refrigerant gas flows into the oil supply mechanism 158 or when the refrigerant gas dissolved in the lubricating oil 104 is generated as bubbles in the oil supply mechanism 158, such as at the time of startup, the refrigerant gas is centrifuged. They are separated by a pump 152 and discharged from a gas vent hole 172. As a result, the oil does not flow into the oil supply mechanism after the second viscous pump 154. For this reason, the lubrication at each sliding portion such as the main shaft portion 120 and the main bearing 126 is improved, the occurrence of wear can be prevented, and the reliability is improved.

  Further, at the time of low speed rotation, the centrifugal pump 152 has a small stroke, and oil cannot be supplied to a very high position. However, by providing the second viscous pump 154 connected to the upper portion through the communication hole 170, Lubricating oil can be reliably supplied to the sliding portion. As a result, the occurrence of wear at each sliding portion can be suppressed, and the reliability can be improved.

  Further, the second viscous pump 154 is formed on the lead groove 184 engraved on the outer periphery of the main shaft portion 120 of the shaft 118 and the inner peripheral surface of the main bearing 126 that supports the main shaft portion 120. The two viscous pumps 154 can be formed integrally with the machining of the shaft 118, and productivity can be improved.

  Further, the second viscous pump 154 is formed by the lead groove 184 so that the sliding portion between the main shaft portion 120 and the main bearing 126 is lubricated, and the eccentric shaft portion 122 and the connecting means 136 or the piston is lubricated. Since the lubricating oil 104 can be supplied to the upper sliding portions such as 130 and the cylinder 134, each sliding portion can be reliably lubricated and the reliability can be improved.

  In the first embodiment, since the cylindrical cavity 160 is formed integrally with the shaft 118, it is not necessary to attach another member to form the cylindrical cavity 160, and the structure becomes simple. As a result, the width of the fitting portion between the main shaft 120 and the rotor 116 can be reduced, the overall height of the hermetic compressor can be reduced, and the space is effective when mounted on a product such as a refrigerator. Can be used for

  The cylindrical cavity 160 forming the viscous pump 150 may be a cylindrical part that is a separate member from the shaft 118 and may be attached below the shaft 118 or the rotor 116. In this case, the partition plate 180 or the honeycomb plate 180 constituting the rotation synchronization means 178 may be incorporated in the cylindrical part in advance and attached to the lower side of the shaft 118 or the rotor 116.

  In the first embodiment, the spiral groove 176 is provided on the outer surface of the insertion portion 166, but the same effect can be obtained even if it is provided on the inner surface of the cylindrical cavity portion 160.

  Furthermore, in Embodiment 1, the partition plate 180 and the honey plate 182 are used as the rotation synchronization means 178. However, the centrifugal pump 152 can also be configured as a configuration using only one of them.

  Further, the rotation synchronization means 178 may have a configuration other than the partition plate 180 and the splash plate 182 shown in the first embodiment as long as the lubricating oil 104 functions to rotate at the same rotational angular velocity as that of the main shaft portion 120. Well, for example, as shown in FIG. 5, the partition member 200 provided with a plurality of holes 201 in the vertical direction is fixed to the inner wall of the cylindrical cavity 160 shown in FIG. 1 (upper part of the partition plate 180), It is also possible to function as the rotation synchronization means 178, and the same effect can be expected.

  Furthermore, in the first embodiment, the elastic wire rod bracket 164 is used as a means for restraining the rotation of the insertion portion 166. However, the insertion portion 166 is prevented from rotating, and the shaft 118 is prevented from falling off. Then, the same effect can be expected.

  As described above, since the hermetic compressor according to the present invention can improve efficiency and reliability by using a combination of a viscous pump and a centrifugal pump, not only an electric refrigerator-freezer for home use, but also an air conditioner, automatic Widely applicable to vending machines and other commercial refrigeration equipment.

102 Sealed container 104 Lubricating oil 110 Electric element 112 Compression element 114 Stator 116 Rotor 118 Shaft 120 Main shaft part 122 Eccentric shaft part 124 Cylinder block 126 Main bearing 130 Piston 134 Cylinder 136 Connecting means 150 Viscosity pump 152 Centrifugal pump 154 Second Viscous pump 160 Cylindrical cavity portion 166 Insertion portion 176 Spiral groove 178 Rotation synchronization means 180 Partition plate 181 Hole portion 182 Heating plate 184 Lead groove 200 Partition member (rotation synchronization means)

Claims (6)

Lubricating oil is stored in a sealed container, and an electric element having a stator and a rotor and a compression element disposed above the electric element are accommodated, and the compression element is fixed to the rotor. A shaft having a main shaft portion and an eccentric shaft portion, a cylinder block having a cylinder, a piston inserted in the cylinder so as to be capable of reciprocating, and a connecting means for connecting the piston and the eccentric shaft portion; A cylindrical bearing formed in the shaft, the main bearing formed on the cylinder block and supporting the main shaft portion of the shaft, and a viscous pump and a centrifugal pump provided at a lower portion of the shaft. An insertion portion inserted into the cylindrical cavity, a spiral groove formed between the inner periphery of the cylindrical cavity and the outer periphery of the insertion portion in a direction in which the lubricating oil rises, and the insertion The centrifugal pump is disposed at the upper part of the viscous pump and includes a rotation synchronization means for bringing the flow rate of the lubricating oil in the cylindrical cavity close to the rotational speed of the shaft. A hermetic compressor with a configuration. 2. The hermetic compressor according to claim 1, wherein the rotation synchronization unit includes a partition plate that divides a space in the cylindrical cavity portion into upper and lower portions and has a hole portion that communicates the upper and lower spaces in a central portion. . 3. The hermetic compressor according to claim 1, wherein the rotation synchronization unit includes a honeycomb plate that is provided in the cylindrical cavity and rotates integrally with a shaft. The hermetic compressor according to any one of claims 1 to 3, wherein a second viscous pump communicating with the centrifugal pump is provided at an upper portion of the centrifugal pump. 5. The hermetic compressor according to claim 4, wherein the second viscous pump is formed by a lead groove carved on an outer periphery of a main shaft portion of a shaft and an inner peripheral surface of a main bearing that pivotally supports the main shaft portion. . The hermetic compressor according to any one of claims 1 to 5, wherein the electric element is driven and controlled at a plurality of frequencies including a frequency lower than a commercial frequency.