JP2013241874A - Hermetic compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hermetic compressor in which a spiral passage forming member can be arranged in an oil supply piece or an oil supply passage in a crank shaft without considering the positional relationship between the oil supply piece or the oil supply passage in the crank shaft and the spiral passage forming member to form a spiral passage for executing the pumping action.SOLUTION: A spiral passage forming member is provided between an inlet of a spiral passage formed in a crank shaft and an oil supply piece mounted on an oil supply passage of the crank shaft. Thus, the assembly can be executed without considering the correct positional relationship between the oil supply piece or the oil supply passage in the crank shaft and the spiral passage forming member for executing the pumping action. As a result, any abnormal noise or wear caused by uneven touch is not generated between the oil supply passage in the crank shaft or the oil supply piece and a spring member.

Description

  The present invention relates to a compressor for compressing a refrigerant used in a refrigeration apparatus such as a refrigerator or a refrigeration cycle mounted in a refrigeration apparatus, and in particular, supplies refrigeration oil to a sliding portion of a reciprocating compressor. The present invention relates to a hermetic compressor including an oil supply mechanism.

  Usually, a hermetic reciprocating compressor is used as a compressor for compressing a refrigerant used in the refrigeration cycle. In this type of reciprocating compressor, it is necessary to supply the refrigerating machine oil to the sliding portion of the piston and cylinder, the connecting rod (hereinafter referred to as the connecting rod) connected to the piston, and the sliding portion of the crankshaft. .

  This oil supply mechanism for supplying refrigeration oil fluidly connects an oil supply piece that is press-fitted into a crankshaft and performs a pumping action, and an oil supply passage and a spiral passage formed in the crankshaft, and is supplied via the spiral passage. The refrigeration oil is supplied to the sliding part of the piston and the cylinder and the connecting part connected to the piston and the sliding part of the crankshaft. Here, a tip hole for sucking the refrigerating machine oil stored in the bottom of the hermetic container of the reciprocating compressor is provided at the tip of the oil supply piece.

  In such an oil supply mechanism, the refrigerating machine oil that has flowed from the tip hole of the oil supply piece by the rotation of the crankshaft is pushed upward from the vicinity of the center of the oil supply passage toward the outer wall surface by centrifugal force. Thereafter, when it reaches the entrance of the spiral passage formed on the outer periphery of the crankshaft, it is carried upward along the spiral passage due to viscosity or the like.

  Thereafter, the sliding portion between the crankshaft and the connecting rod is lubricated along the outer peripheral surface of the crankshaft, or the refrigeration oil is scattered by centrifugal force to lubricate the sliding portion between the cylinder and the piston. .

  However, in such an oil supply mechanism, when the compressor is operated at a low speed, the number of revolutions of the crankshaft also decreases, so that the centrifugal force based on the rotational movement of the oil supply piece is weakened and the ratio of the refrigeration oil being pushed upward is reduced. As a result, the refrigerating machine oil does not reach the inlet of the spiral passage, so that the oil supply capacity is lowered and the oil supply amount becomes insufficient.

  Therefore, poor lubrication due to insufficient lubrication during low-speed operation cannot ensure the reliability of the compressor, the cooling of the cylinder and piston by the refrigeration oil is insufficient, and the sucked refrigerant is overheated. There has been a phenomenon that the volumetric efficiency of the compressor is lowered due to a decrease in sealing performance.

  In order to avoid such a phenomenon, in Japanese Patent Laid-Open No. 2000-314380 (Patent Document 1), a spring member is fixed to the inner bottom surface portion of the hermetic container, and the spring member is spiraled through the oil supply piece and the oil supply passage. A technique is disclosed in which a sufficient amount of refrigeration oil reaches the inlet of the spiral passage by extending to the entrance of the spiral passage even during low-speed operation. The spring member forms a spiral pump passage between the oil supply piece and the oil supply passage, and functions to perform a pump action by the spring member.

JP 2000-314380 A

  By the way, the spring member described in Patent Document 1 is configured to be fixed to the inner bottom surface of the sealed container that houses the compressor, and has the following problems.

  In other words, if the positional relationship between the fixed position of the spring member, the oil supply piece, and the oil supply passage in the crankshaft is not set correctly, contact between the oil supply passage or oil supply piece in the crankshaft and the spring member will occur, causing abnormal noise and wear. Is not preferable.

  In addition, the frictional heat between the spring member and the oil supply passage or oil supply piece in the crankshaft increases the temperature of the refrigeration oil in the sealed container, and the refrigerant and the refrigerant sucked are overheated due to insufficient cooling of the compressor cylinder and piston. A problem occurs.

  An object of the present invention is to provide an oil supply piece, a crankshaft without considering the positional relationship between the oil supply piece, the oil supply passage in the crankshaft, and the spiral passage forming member that forms a spiral passage that performs a pumping action. An object of the present invention is to provide a hermetic compressor that can be disposed in an oil supply passage.

  The present invention is characterized in that a spiral passage forming member is provided between an inlet of a spiral passage formed in the crankshaft and an oil supply piece attached to the oil supply passage of the crankshaft.

  According to the present invention, the spiral passage forming member is provided between the inlet of the spiral passage and the oil supply piece attached to the oil supply passage of the crankshaft, so that the oil supply piece, the oil supply passage in the crankshaft, and the spiral that performs a pump action Assembling can be performed without taking into account the exact positional relationship between the passage forming members. As a result, there is no contact between the oil supply passage or oil supply piece in the crankshaft and the spring member, and no noise or wear occurs.

1 is a longitudinal sectional view of a hermetic compressor provided with an oil supply mechanism according to an embodiment of the present invention. It is explanatory drawing which shows the behavior of the refrigerating machine oil in the case of performing oil supply by the oil supply piece. It is an external appearance perspective view of the spring member used as the other Example (2nd Embodiment) of this invention. It is a perspective view of the oil supply piece used for the oil supply mechanism which becomes the other Example (3rd Embodiment) of this invention. It is a principal part expanded sectional view of the oil supply mechanism which becomes the other Example (4th Embodiment) of this invention. It is an expanded sectional view of the oil supply piece part for demonstrating the oil supply state by the conventional oil supply piece.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings, but a plurality of embodiments are proposed in the present invention. Therefore, although the detailed description is given for each embodiment, the present invention is not limited to these embodiments and includes various modifications and applications within the basic concept of the present invention.

  Next, a first embodiment of the present invention will be described with reference to FIG. In FIG. 1, reference numeral 10 is a sealed container that houses a compressor 11 and an electric motor 12, and refrigerating machine oil 30 for supplying oil to a mechanical sliding portion of the compressor 11 is stored in the sealed container 10. It has a configuration.

  The compressor 11 includes a cylinder block 13, a piston 14 disposed in the cylinder block 13, a compression chamber 15 formed between the piston 14 and the cylinder block 13, and a cond that connects the piston 14 and the crankshaft 16. 17, an intake valve for sucking and discharging refrigerant, an exhaust valve (each not shown), and the like.

  A crankshaft 9 is rotatably supported on a bearing portion 18 constituting a part of the cylinder block 13, and a connecting rod 17 is rotatably supported on one end of the crankshaft 16.

  A rotor 19 of the electric motor 12 is fixed to the other end of the crankshaft 16, and the rotation of the rotor 19 is transmitted to the crankshaft 16.

  The electric motor 12 is arranged below the cylinder block 13 when viewed in the vertical direction, and a rotor 19 is accommodated in an annular stator 20 constituting the electric motor 12. The stator 20 is integrated with the cylinder block 13 using a fixing bolt or the like, and the rotor 19 is held in the stator 20 by a crankshaft 16.

  The compressor 11 and the electric motor 12 are supported in the sealed container 10 by four support springs 21.

  In the hermetic compressor having such a configuration, when the rotor 19 is rotated by a three-phase alternating current from an inverter device (not shown), this rotation is transmitted to the crankshaft 16, and the rotational movement of the crankshaft 16 is transferred to the piston by the connecting rod 17. The refrigerating cycle is operated by reciprocating 14 to suck and compress the refrigerant. Since the operation of such a compressor is already well known, further explanation is omitted.

  Next, an oil supply mechanism that is a feature of the present invention will be described below. The other of the crankshaft (the side where the connecting rod 17 is not connected) is provided with an oil supply passage 22 having a hollow interior, and this oil supply passage 22 is formed in a spiral groove 23 formed on the outer periphery of the crankshaft 16. Fluidly connected to the

  The spiral groove 23 has a function of forming a spiral passage with the bearing portion 18 of the cylinder block 13 and flowing the refrigerating machine oil 30.

  The spiral groove 23 is connected to the oil supply passage 22 via a connection opening 23A. The connection opening 23A is formed on the outer periphery of the crankshaft 16 and the inner periphery of the crankshaft 16. It is a communication hole formed in the crankshaft 16 that connects the oil supply passage 22.

  The spiral groove 23 on the opposite side of the connection opening 23A is connected to an outflow opening 23B that is open at a portion of the crankshaft 16 that supports the connecting rod 17 so that the refrigerating machine oil is supplied to the bearing portion of the connecting rod 17 and the piston 14 and the cylinder block 13. It is designed to be supplied to the sliding part.

  A hollow oil supply piece 24 is fixed to the oil supply passage 22 formed on the other side of the crankshaft 16 by a method such as press fitting, and the oil supply piece 24 hangs downward and is stored in the sealed container 10. It extends so as to be immersed in the machine oil 30. An opening 24 </ b> A is formed at the tip of the oil supply piece 24, and this opening 24 </ b> A has a role of introducing the refrigerating machine oil 30 into the oil supply piece 24.

  Further, a rotary blade 24C is fixed in the oil supply piece 24 so as to extend in the axial direction. The rotation of the rotary blade 24C rotates the refrigerating machine oil 30 in the oil supply piece 24, and the refrigerating machine oil 30 is supplied by centrifugal force. It functions to push up along the wall surface in the oil supply passage 22.

  In such an oil supply mechanism, when electric power is supplied to the electric motor 12 from an inverter circuit (not shown), the rotor 19 rotates accordingly. When the rotor 19 rotates, the crankshaft 16 fixed to the rotor 19 also rotates. When the crankshaft 16 rotates, the oil supply piece 24 also rotates in synchronization therewith.

  At this time, the refrigerating machine oil 30 in the sealed container 10 is introduced into the oil supply piece 24 attached to the lower end of the crankshaft 16 and rises along the wall surface of the oil supply passage 22 by centrifugal force. FIG. 6 shows the behavior of the refrigerating machine oil 30. The refrigerating machine oil 30 is pushed upward along the wall surface in the oil supply passage 22 according to the centrifugal force generated by the rotation of the crankshaft 16 and the oil supply piece 24.

  The pushed-up refrigeration oil 30 enters the spiral groove 23 from the connection opening 23A of the spiral groove 23 by centrifugal force and viscous action, and enters the refrigerator oil 30 from the outlet opening 23B. 14 and the cylinder block 13 are supplied to the sliding portion.

  The refrigerating machine oil 30 is supplied with oil by being scattered from the outflow opening 23 </ b> B to the outer peripheral surface of the piston 14 which is the sliding surface of the cylinder block 13. In addition, oil films are formed on the sliding surfaces between the cylinder block 13 and the piston 14, between the piston 14 and the connecting rod 17, between the connecting rod 17 and the crankshaft 16, and between the crankshaft 16 and the bearing portion 18. The metal contact on the sliding surface is prevented to ensure reliability.

  However, since this oil supply mechanism is structured to use the centrifugal force generated by the rotation of the crankshaft 16, the centrifugal force tends to be small in the operation region where the rotational speed is low.

  For this reason, when the rising height of the refrigerating machine oil 30 rising along the wall surface of the oil supply passage 22 decreases, the refueling amount of the refrigerating machine oil 30 entering the spiral groove 23 decreases, and the compressor 11 is configured. Therefore, sufficient refrigeration oil 30 cannot be supplied to the sliding portion of the machine element.

  If sufficient refrigerating machine oil 30 cannot be supplied to these sliding parts, for example, the amount of refrigerating machine oil 30 supplied to the sliding surfaces of the cylinder block 13 and the piston 14 decreases, and an oil film is formed in this part. Because it becomes difficult. As a result, metal contact is generated on the sliding surface of the cylinder block 13 and the piston 14 to reduce the reliability of the compressor itself, or the refrigerant gas leaks out from the compression chamber 15 to reduce the cooling power of the compressor 11. This causes problems such as lowering.

  As a method for solving such a problem, a technique of newly providing an auxiliary oil supply mechanism for refrigerating machine oil by a spring member as described in Patent Document 1 has been proposed.

  However, in the technique disclosed in Patent Document 1, unless the positional relationship between the fixed position of the spring member, the oil supply piece, and the oil supply passage in the crankshaft is set accurately, the oil supply passage in the crankshaft, the oil supply piece, and the spring member This is not preferable because the contact with one piece causes abnormal noise and wear. In addition, the frictional heat between the spring member and the oil supply passage or oil supply piece in the crankshaft increases the temperature of the refrigeration oil in the sealed container, and the refrigerant and the refrigerant sucked are overheated due to insufficient cooling of the compressor cylinder and piston. A problem occurs.

  The present invention adopts the following configuration in order to solve such problems.

  1 and 2, a spring member 31 formed of a helically wound compression coil spring is provided in the oil supply passage 22, and the spring member 31 includes an upper end portion 22 </ b> A and a lower end portion 22 </ b> B of the oil supply passage 22. Alternatively, it is interposed in a compressed state between the upper end portion 24B of the oil supply piece 24 extending beyond the lower end portion 22B. In this embodiment, the spring member 31 is interposed between the upper end portion 22A of the oil supply passage 22 and the upper end portion 24B of the oil supply piece 24 in a compressed state.

  Further, the spring member 31 has an outer diameter that is substantially the same as the inner diameter of the oil supply passage 22, and as a result, a spiral pump passage 32 between the lines of the spring member 31 and the inner peripheral surface of the oil supply passage 22. Is supposed to form.

  The spring member 31 is a compression coil spring as described above, and the compression coil spring can be slightly displaced not only in the compression direction but also in the radial direction, so that it can be installed in the oil supply passage 22 without requiring much dimensional accuracy.

  This pump passage 32 connects at least the upper end portion 24B of the oil supply piece and the connection opening 23A of the spiral groove 23. For this reason, between the wires of the wire forming the spring member 31 is in close contact with each other in a compressed state.

  The connection opening 23 </ b> A only needs to be supplied with at least the refrigerating machine oil 30 from the pump passage 32. For this reason, the connection opening 23 only needs to be opened so as to face the pump passage 32. In the present embodiment, the gap C between the spring members 31 in the vicinity of the connection opening 23A is increased so that the connection opening 23A faces the pump passage 23 more.

  That is, as can be seen from FIG. 2, the line between the spring members 31 is determined to be in close contact from the upper end portion 24B of the oil supply piece 24 to the lower end side of the connection opening 23A, and the spring member 31 extends from the lower end side of the connection opening 23A. The line is determined to be in close contact with each other, and as a result, the ratio of the connection opening 23 facing the pump passage 32 is increased.

  Furthermore, by comprising in this way, when the refrigerating machine oil 30 is pushed up by centrifugal force in the normal rotation area | region, the refrigerating machine oil 30 can be smoothly entered into the connection opening 23A.

  The wire diameter of the spring member 31 may be appropriately selected. However, if the wire diameter is too thin, a sufficient pump passage area cannot be obtained. If the wire diameter is too large, the pump passage area becomes large. It becomes too much and it becomes difficult for the refrigerating machine oil 30 to enter. For this reason, in the present embodiment, the refrigerating machine oil 30 is connected to the connection opening 23A according to the rotation speed of the compressor to be applied, the axial length of the oil supply passage 22, the inclination (pitch angle) of the pump passage 32 by the spring member 31, and the like. What is necessary is just to employ the shape of lifting.

  In the above, since the rotational speed is high when the normal compressor 11 is driven, the refrigerating machine oil 30 is pushed up to the wall surface side of the oil supply passage 22 by centrifugal force as shown in FIG. For this reason, since the refrigerating machine oil 30 is pushed up to the connection opening 23 </ b> A opened in the wall surface of the oil supply passage 22, sufficient refrigerating machine oil 30 can be supplied to the spiral groove 23. In this case, the refrigerating machine oil 30 is sent to the connection opening 23 </ b> A through the portion where the gap C between the spring members 31 is large.

  On the other hand, when the rotation of the compressor 11 is low, the refrigerating machine oil 30 does not have enough centrifugal force to be pushed up to the wall surface side of the oil supply passage 22 as shown in FIG. For this reason, the refrigerating machine oil 30 cannot be pushed up to the spiral groove 23 because the refrigerating machine oil 30 cannot be pushed up to the connection opening 23 </ b> A opened in the wall surface of the oil supply passage 22.

  On the other hand, according to the present embodiment, the refrigerating machine oil 30 can be caused to enter the connection opening 23A by the action of the spiral pump passage 32 formed between the spring member 31 wound spirally and the oil supply passage 22. become able to.

  That is, the refrigerating machine oil 30 supplied from the oil supply piece 24 to the lower side of the helical spring member 31 enters the helical pump passage 32, but the centrifugal force that acts on the refrigerating machine oil 30 and the viscosity of the refrigerating machine oil 30. For example, the refrigerating machine oil 30 enters the spiral pump passage 32 upward and reaches the connection opening 23A.

  Thereafter, the refrigerating machine oil 30 that has reached the connection opening 23 </ b> A is supplied to the bearing part of the connecting rod 17 and the sliding part of the piston 14 and the cylinder block 13 from the outlet opening 23 </ b> B via the spiral passage 23. It has become.

  As described above, even when the compressor 11 is driven at a low speed, the refrigerating machine oil 30 remains between the cylinder block 13 and the piston 14, between the piston 14 and the connecting rod 17, between the connecting rod 17 and the crankshaft 16, and between the crankshaft 16. By forming an oil film on each sliding surface between the bearing portion 18 and the bearing portion 18, metal contact on the sliding surface can be prevented and reliability can be ensured.

Further, in this embodiment, the spring member 31 that performs the pump action is disposed in the oil supply passage 22, and therefore, the precise dimension control is not so accurate because it is simply inserted in the oil supply passage 22 in a compressed state. Furthermore, in the present embodiment, since the spring member 31 is only disposed in the oil supply passage 22, the oil supply passage 22 and the spring member come into contact with each other and cause noise and wear as disclosed in Patent Document 1. The temperature of the refrigerating machine oil in the sealed container rises due to frictional heat between the spring member and the oil supply passage or oil supply piece, and the refrigerant and the refrigerant sucked are overheated due to insufficient cooling of the compressor cylinder and piston. There is no such thing.

  FIG. 3 is an external perspective view of the spring member 31 according to the second embodiment of the present invention. The spring member 31 shown in FIG. 1 is a compression coil spring, whereas the spring member 31 shown in FIG. This is different from the first embodiment in that it is a wound torsion coil spring.

  The spring member 31 shown in FIG. 3 is a torsion coil spring wound in a spiral shape, and is similar to the spring member 31 shown in FIG. 1 between the upper end portion 24B of the fueling piece and the connection opening 23A of the spiral groove 23. Are formed, and the spring members 31 are in close contact with each other in a compressed state.

  Further, the gap between the wires of the spring member 31 in the vicinity of the connection opening 23A is increased so that the connection opening 23A faces the pump passage 32 more.

  When the torsion coil spring is used, the spring member 31 can be installed in the oil supply passage 22 without requiring dimensional accuracy as compared with the compression coil spring because it can be displaced in the compression direction and the radial direction.

  Although common to the first embodiment, the gap C between the wires of the spring member 31 near the connection opening 23A is increased so that the connection opening 23A faces the pump passage 32 more. For this reason, even when the refrigerating machine oil 30 rises to the vicinity of the connection opening 23A of the spiral groove 23 by the rotary blade 24C in the normal rotation speed region, the refrigerating machine oil 30 is smoothly supplied through the gap between the lines formed in the torsion coil spring. be able to.

  FIG. 4 is an external perspective view of an oil supply piece 24 according to the third embodiment of the present invention, and the upper end portion 24B of the oil supply piece 24 shown in FIG. This is different from the first embodiment in that a non-rotating portion 24D such as a step portion is formed instead of an annular shape.

  In this embodiment, the anti-rotation portion 24D is formed on an annular end surface that spirally extends from the lower portion of the step portion toward the upper portion of the step portion. If the height of the step portion is approximately the same as the wire diameter of the spring member 31, the annular end surface that spirally extends from the lower portion of the step portion toward the upper portion of the step portion is the wire rod on the lowermost surface of the spring member 31. Therefore, the sitting of the spring member 31 is good.

  The anti-rotation portion 24D functions as follows. When the spring member 31 is placed in a compressed state on the upper end portion 24B of the oil supply piece 24, the end portion of the spring member 31 is caught by the anti-rotation portion 24D, and the spring member 31 rotates. It is to prevent it. Specifically, the end portion of the spring member 31 is hooked on the rotation preventing portion 24D while sliding on the annular end surface extending in a spiral manner during several rotations after the crankshaft 16 of the compressor 11 starts rotating. For this reason, when assembling the oil supply mechanism, it is not necessary to position the end portion of the stepped rotation-preventing portion 24D formed on the upper end portion 24B of the oil supply piece 24 and the spring member 31, so that the assembly is easily performed. Can do.

  FIG. 5 is a cross-sectional view of an essential part of an oil supply mechanism according to the fourth embodiment of the present invention. The spring member 31 shown in FIGS. 1 and 2 is formed with a gap C between lines leading the refrigerator oil 30 to the connection opening 23A. The present embodiment is different from the first embodiment in that a locking portion 22E that locks the spring member in the middle when the gap C between the lines is not provided.

  In FIG. 5, locking portions 22 </ b> E formed at equal intervals, for example, 90 ° intervals, are provided on the wall surface of the oil supply passage 22 near the lower end surface of the connection opening 23 </ b> A so as to protrude inside the wall surface of the oil supply passage 22. For example, the locking portion 22E can be formed so as to protrude inward over the inner periphery of the oil supply passage 22 avoiding the connection opening 23A. Of course, it is also possible to insert a pin-like locking portion from the outer peripheral side of the oil supply passage 22.

  The spring member 31 is housed in a compressed state between the locking portion 22E in the oil supply passage 22 and the upper end portion 24B of the oil supply piece 24, and the wire member is in close contact with the spring member 31.

  In the above, since the rotational speed is high when the normal compressor 11 is driven, the refrigerating machine oil 30 is pushed up to the wall surface side of the oil supply passage 22 by centrifugal force. For this reason, the refrigerating machine oil 30 is pushed up to the vicinity of the connection opening 23 </ b> A opened in the wall surface of the oil supply passage 22. In this embodiment, since the spring member 31 is locked by the locking portion 22E in the vicinity of the connection opening 23A, the refrigerating machine oil 30 exceeds the close contact portion (near the locking portion 24E) of the spring member 31. Are sent to the connection opening 23A.

  On the other hand, when the rotation of the compressor 11 is low, the refrigerating machine oil 30 supplied from the oil supply piece 24 to the lower side of the spring member 31 enters the spiral pump passage 32 as in the first and second embodiments. However, due to the centrifugal force acting on the refrigerating machine oil 30 and the viscosity of the refrigerating machine oil 30, the refrigerating machine oil 30 enters the spiral pump passage 32 to the upper side and reaches the connection opening 23A.

  As described above, according to the present invention, the helical passage forming member is provided between the inlet of the spiral passage and the oil supply piece attached to the oil supply passage of the crankshaft, so that the oil supply piece and the oil supply passage in the crankshaft are provided. Assembling can be performed without taking into account the exact positional relationship between the hose and the spiral passage forming member that performs the pumping action. As a result, there is no contact between the oil supply passage or the oil supply piece in the crankshaft and the spring member as in Patent Document 1, and no noise or wear occurs.

DESCRIPTION OF SYMBOLS 10 ... Airtight container, 11 ... Compressor, 12 ... Electric motor, 13 ... Cylinder block, 14 ... Piston, 15 ... Compression chamber, 16 ... Crankshaft, 17 ... Connecting rod, 18 ... Bearing part, 19 ... Rotor, 20 ... Fixed Child, 21 ... support spring, 22 ... oil supply passage, 23 ... spiral groove,
23A ... Connection opening, 23B ... Outlet opening, 24 ... Refueling piece, 24A ... Opening, 24B ... Upper end surface, 31 ... Spring member, 32 ... Spiral pump passage.

Claims (7)

A compressor for compressing refrigerant in the refrigeration cycle; an electric motor for driving the compressor; and a sealed container for storing the compressor and the electric motor and storing refrigerating machine oil for lubricating the sliding portion of the compressor. In a hermetic compressor,
An oil supply passage that is connected to a crankshaft of the compressor through a passage through which the refrigeration oil flows to the sliding portion of the compressor and a connection opening is formed, and the refrigeration oil stored in the sealed container is guided to the oil supply passage In addition to providing a piece, a helical pump passage is provided in the oil supply passage between the oil supply piece and the connection opening to flow the refrigerating machine oil introduced through the oil supply piece to the connection opening. Hermetic compressor. The hermetic compressor according to claim 1, wherein
The hermetic compressor, wherein the pump passage is formed by a spirally wound spring member disposed in the oil supply passage and a wall surface of the oil supply passage. The hermetic compressor according to claim 2, wherein
The helically wound spring member is a compression coil spring that is compressed and in close contact with a wire, and the compression coil spring is in close contact with the wall surface of the oil supply passage to form a helical pump passage. A hermetic compressor. The hermetic compressor according to claim 2, wherein
The helically wound spring member is a torsion coil spring that is compressed and in close contact with the wire, and the torsion coil spring is in close contact with the wall surface of the oil supply passage to form a helical pump passage. A hermetic compressor characterized by that. The hermetic compressor according to any one of claims 3 to 4,
A hermetic compressor, wherein a gap (a gap between lines) is provided between the wire rods of the compression coil spring or the torsion coil spring near the connection opening. The hermetic compressor according to any one of claims 3 to 4,
A hermetic compression, wherein an end face of an oil supply piece in contact with the compression coil spring or torsion coil spring is provided with a detent portion in contact with the end face of the compression coil spring or torsion coil spring. Machine. The hermetic compressor according to any one of claims 3 to 4,
A locking portion protruding inward is provided on the wall surface of the oil supply passage in the vicinity of the connection opening, and the wire rod of the compression coil spring or torsion coil spring is in close contact between the front locking portion and the oil supply piece. A hermetic compressor, wherein the compressor is provided to be compressed.

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