JP2015094224A - Hermetic type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hermetic type compressor enabled to separate refrigerant gas, even with a stationary piece, so that it can contribute to an improvement in the cooling performance in a refrigeration system.SOLUTION: A hermetic type compressor sucks up a lubricating oil 2 by the viscous pump action of a viscous pump 16a, which is composed of a hollow sleeve 19 accompanying the rotation of a crankshaft 12 and a stationary piece 21, to separate a liquid and a gas (a coolant gas), containing a mist state. When the liquid is fed via a communication hole 17 to a sliding part whereas the gas is fed via a gas hole 29 to the upper portion of a compression element, an interference part 18a formed between the upper end part of the sleeve 19 and the lower end part of the communication hole 17 reduces the pressure of the lubricating oil 2 thereby to serve for a gas-liquid separation, and increases the capacity so that the liquid of the lubricant to be reserved in the chamber as it is sump may not flow out to the side of the gas hole 29, and so that it suppresses the flow of the liquid to the side of the permeable hole 29 by the individual walls of the weir 33 of the indoor upper part.

Description

  The present invention relates to a hermetic compressor mounted on a refrigeration system for home appliances such as a refrigerator and an air conditioner (air conditioner).

  In recent years, the demand for higher efficiency is increasing in refrigeration systems for home appliances, and for the hermetic compressors mounted on the refrigeration systems, commercial power supplies can be used from low operating frequency bands below the commercial power supply frequency in order to realize high efficiency. A type capable of operating in a wide frequency band up to a high operating frequency band higher than the frequency is applied.

However, in such a hermetic compressor, in a frequency region of a low operating frequency band that affects high efficiency, it is difficult to secure oil supply for satisfying reliability and efficiency in operation. As a well-known technology proposed for the purpose of securing oil supply by taking measures against these trends, oil flow can be effectively ensured even at a low operating speed of about 800 min ^-1 through the use of simple, reliable and low-cost means. "Oil pump of hermetic compressor" (see Patent Document 1), or intermittent noise between the pump body and the support or fixed rod can cause unwanted noise due to operation of the compressor at high rotational speed. The pump body can be mounted concentrically inside the tubular sleeve of the oil pump with the freedom to move in a radial direction perpendicular to the crankshaft by rotationally locking the pump body with respect to the pump rotor. Examples of the mounting device for the oil pump of the refrigeration compressor (Patent Document 2).

  Incidentally, a general hermetic compressor for a refrigerator has a compression element and an electric element, and oil is supplied to the sliding portion by a viscous pump formed at the lower part of the crankshaft. Specifically, it is fixed to the sleeve. Lubricating oil (oil) is pumped up by a first viscous pump such as a spiral groove formed between the two pieces and sent to the sliding portion of the crankshaft through the second viscous pump to lubricate the bearing portion. It has a structure. At that time, the sucked lubricating oil is separated from the gas refrigerant contained in the lubricating oil in the hollow portion at the center of the crankshaft, the lubricating oil flows to the oil supply hole, and the gas refrigerant flows from the center of the crankshaft to the piston side. A gas-liquid separation chamber is formed in the hollow portion at the center of the so-called crankshaft.

  On the other hand, in the above-described hermetic compressor of Patent Document 1, a sleeve is provided at the lower end portion of the crankshaft, and a grooved member (fixed piece) supported by the bracket is fixed in the sleeve. A viscous oil supply mechanism is adopted in which the oil between the outer surface of the sleeve and the inner surface of the sleeve is raised by a viscous pump action as the sleeve rotates.

Special Table 2002-519589 Special table 2012-505331

  In both Patent Document 1 and Patent Document 2 described above, the lubricating oil is sucked up along the spiral groove of the fixed piece by rotating the viscous lubricating oil together with the wall surface of the sleeve rotating by the rotation of the crankshaft. After the lubricating oil is sent to the main bearing side through the oil supply hole leading from the center of the crankshaft to the outer peripheral side wall, the main bearing portion is lubricated through the spiral groove on the outer periphery of the crankshaft. Then, since a fixed piece (an oil suction member in Patent Document 1 and a tubular pump body in Patent Document 2 corresponds) is attached to the cavity at the center of the crankshaft, the separation of the refrigerant gas becomes insufficient. The cooling effect may be reduced.

Particularly in refrigerators equipped with recent refrigeration systems, power saving is screamed, and the rotational speed of the hermetic compressor is controlled in the range of 800 to 4300 min ⁻¹ using an inverter drive circuit. When a large amount of food is stored or when the temperature is high in the summer, the compressor is rotated at a high speed to rapidly cool the interior. If the internal temperature is stabilized by the high speed rotation at this time, the power consumption of the hermetic compressor can be greatly reduced by setting the rotation speed of the hermetic compressor to a low speed rotation of 800 min- ¹ .

However, when high-speed rotation 4300 min ⁻¹ is performed with a hermetic compressor, the amount of lubricating oil sucked up by the crankshaft increases extremely, and a situation occurs in which the lubricating oil flows into a passage through which only the refrigerant gas originally passes, In such a case, if the supply amount of the refrigerant gas is reduced, the original refrigerant supply amount of the compressor is lowered, and the cooling effect as the refrigerator is lowered.

  The present invention has been made to solve such problems, and its technical problem is to enable high-efficiency separation of refrigerant gas even if a fixed piece is provided, and to improve cooling performance in a refrigeration system. It is in providing the hermetic compressor which can contribute to.

  In order to solve the above technical problem, a crankshaft rotatably supported by a main bearing in a sealed container storing lubricating oil and having a rotor attached to the outer periphery thereof, and the inside of the sealed container and the inner diameter hollow portion of the crankshaft communicate with each other. Thus, the gas passage hole provided in the crankshaft, the communication hole provided in the crankshaft so that the inner diameter portion and the inner diameter hollow portion of the main bearing communicate with each other, and the lower portion of the inner diameter hollow portion of the crankshaft are press-fitted. A hollow sleeve and a fixed piece with a concave and convex shape having a spiral surface and mounted with a clearance in the sleeve, and lubricated by a viscous pump action by the sleeve and the fixed piece as the crankshaft rotates The oil is pumped up and separated into a liquid and a gas containing a mist state in a gas-liquid separation chamber which becomes an oil separation space in the hollow portion of the inner diameter. In the hermetic compressor that supplies the gas to the sliding element through the through hole and supplies the gas to the compression element through the through hole, the upper end of the fixed piece is disposed between the upper edge of the sleeve and the lower end of the communication hole. The gas-liquid separation chamber has a dimension between the diameter of the inner peripheral surface of the cylindrical hollow portion and the diameter of the outer surface of the boss portion of the fixed piece, and the outer diameter of the inner peripheral surface of the sleeve and the boss portion of the fixed piece. It is characterized by having a structure having an interference part for decompression formed by making it larger than the dimension between the surface diameter.

  According to the hermetic compressor of the present invention, with the above configuration, the gas-liquid separation chamber has a sufficient volume, and the lubricating oil supplied abundantly regardless of the compressor rotational speed is supplied to the gas-liquid separation chamber. Since it is subjected to gas-liquid separation after being depressurized at the interference part, the liquid with respect to the lubricating oil and the gas containing the mist state are efficiently separated, and the pumped-up lubricating oil does not turn to the bearing side and moves the sliding part. The compression operation is smoothly performed without being damaged.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a view showing a basic structure of a hermetic compressor according to a first embodiment of the present invention, with a partial cross section in the vertical direction and the inside exposed. It is the figure which expanded and showed a partially broken main part of FIG. FIG. 2 is a diagram comparing a detailed structure of a crankshaft provided in the hermetic compressor of FIG. 1 with a conventional product, in which (a) is a diagram related to the conventional structure, and (b) is a diagram related to the structure of the first embodiment. It is the figure which showed the characteristic in the relationship of the amount of oil supply with respect to the rotation speed according to the length of the fixed piece with which the hermetic compressor of FIG. 1 is equipped. 2 is a main part for explaining the relationship between the projecting position of the lower end of the viscous pump relative to the lower end of the sleeve and the relationship between the gas-liquid separation chamber and the size of the sleeve when the viscous pump and the sleeve in FIG. FIG. It is the perspective view shown in order to demonstrate the assembly structure with respect to the electric element and compression element of the viscous pump shown in FIG. 2, and its supporting member. It is the perspective view shown from the other direction in the state which removed the spring and connected the electrical connector, supporting the arrangement | positioning relationship of the support member and insulator of a viscous pump in the assembly | attachment structure shown in FIG. It is the perspective view which showed the 1st modification of the viscous pump with which the hermetic compressor which concerns on Example 2 is equipped. FIG. 12 is a perspective view showing a second modification of the viscous pump provided in the hermetic compressor according to the third embodiment. FIG. 10 is a perspective view showing a third modification of the viscous pump provided in the hermetic electric compressor according to the fourth embodiment.

  In the following, the hermetic compressor of the present invention will be described in detail with reference to the drawings with some examples.

  FIG. 1 is a view showing a basic structure of a hermetic compressor according to a first embodiment of the present invention, with a partial cross section in the vertical direction and the inside exposed. FIG. 2 is an enlarged view of a main part of FIG. The hermetic compressor stores lubricating oil (oil) 2 in a hermetic container 1 and is filled with a refrigerant 3, and is reciprocally fitted in a frame 7 forming a cylinder 5 and in the cylinder 5. The piston 6, the main shaft portion 9 that is pivotally supported by the main bearing 8 of the frame 7, and the compression element 4 composed of the crankshaft 12 including the eccentric portion 10, the stator 14 connected to the inverter drive circuit (not shown), and the illustration And an electric element 13 for driving the inverter, which is composed of a rotor 15 fixed to the main shaft portion 9 and fixed below the frame 7.

Among these, the eccentric part 10 has a connecting rod 11 for connecting the piston 6, and the compression element 4 is elastically supported in the hermetic container 1 by a support spring 20 via a stator 14, and is reciprocating compression. The mechanism is configured. The electric element 13 is driven at a plurality of operating frequencies including at least a rotation speed of 700 min ⁻¹ by an inverter drive circuit. The main shaft portion 9 of the crankshaft 12 is formed with a second viscous pump 16b that is connected via a first viscous pump 16a and a communication hole 17, and the lubricating oil 2 serves as the main bearing 8, piston 6, cylinder 5, etc. Oil is supplied to each part.

  Next, referring to FIG. 2, the crankshaft 12 is provided with a gas passage hole 29 so that the inside of the sealed container 1 and the inner diameter hollow portion of the crankshaft 12 communicate with each other, and the inner diameter portion and the inner diameter of the main bearing 8. A communication hole 17 is provided so as to communicate with the hollow portion, a hollow sleeve 19 is press-fitted into the lower portion of the inner diameter hollow portion of the crankshaft 12, and a spiral is formed in the sleeve 19 with a clearance. A fixed piece 21 having an uneven surface with a spiral surface is attached by a boss portion 23 and a spiral groove 25 (may be referred to as a first oil supply groove 26) around the boss portion 23. Here, the gas-liquid which pumps up the lubricating oil 2 by the viscous pump action of the first viscous pump 16 a by the sleeve 19 and the fixed piece 21 accompanying the rotation of the crankshaft 12 and becomes an oil separation space in the inner diameter hollow portion of the crankshaft 12. In the separation chamber 18, the liquid and the gas including the mist state (gas of the refrigerant 3) are separated, the liquid is supplied to the sliding portion through the communication hole 17, and the gas is supplied to the compression element 4 through the gas passage hole 29.

  The gas-liquid separation chamber 18 is a liquid separated from the lubricating oil 2 stored in the chamber as the lubricating oil 2 is pumped up by the viscous pump action of the first viscous pump 16a when the compressor speed is higher than normal. The capacity is increased so that the liquid does not overflow to the gas passage hole 29 side, and the liquid is moved to the gas passage hole 29 side by the weir 33 (specifically, the lower large weir 33a and the upper small weir 33b) provided in the room. It has a structure that blocks and suppresses the flow. The gas passage hole 29 supplies the gas separated and flowed through the weir 33 formed in the upper part of the gas-liquid separation chamber 18 to the compression element 4 side in the sealed container 1. The communication hole 17 is provided in the lower part of the gas-liquid separation chamber 18 in the hollow portion of the inner diameter of the crankshaft 12 and supplies liquid to the second viscous pump 16b by the second oil supply groove 30 provided on the outer peripheral side of the crankshaft 12. To supply. The oil supply hole 28 is a passage through which the liquid pumped up by the second viscous pump 16 b flows, and the liquid passing through the oil supply hole 28 is blown out from the hole of the eccentric portion 10 to the upper portion of the compression element 4. Incidentally, the dust collecting groove 27 provided in the middle of the spiral groove 25 provided in the fixed piece 21 is for collecting the dust in the lubricating oil 2 supplied through the spiral groove 25. An interference portion 18 a formed between the upper edge portion of the sleeve 19 and the lower end portion of the communication hole 17 in the gas-liquid separation chamber 18 lowers the pressure between the first viscous pump 16 a and the gas-liquid separation chamber 18. Has a role for decompression.

  The relationship between the first viscous pump 16a and the second viscous pump 16b will be described below. The first viscous pump 16 a includes a gas-liquid separation chamber 18 and a sleeve 19 formed in the lower part of the crankshaft 12, a fixed piece 21 inserted coaxially with the axis of the crankshaft 12, The support member 22 (details will be described later) that restrains free movement in the rotational direction and the vertical direction is used. Here, the support member 22 is inserted into an insulator support portion (insulator 32, support portion 32a in FIG. 6 described later) attached to the stator 14 at both ends, and the substantially central portion is the end portion of the fixed piece 21. It penetrates the through hole 24 provided in the protrusion 34 and is locked by its inner wall surface.

  The mounting position of the fixed piece 21 does not overlap with the communication hole 17 provided in the side wall of the crankshaft 12 in order to connect the gas-liquid separation chamber 18 formed by the hollow inner diameter of the crankshaft 12 and the main bearing 8. Is in position. If the position overlaps, the communication hole 17 is closed by the boss portion 23 for forming the spiral groove 25 of the fixed piece 21. That is, each time the crankshaft 12 rotates, the communication hole 17 becomes the boss of the fixed piece 21. It will be obstruct | occluded by the part 23. FIG.

  The sleeve 19 has a substantially cylindrical shape and has a cap-like shape with open upper and lower surfaces, and is made of a metal material that is likely to have relatively high accuracy. On the other hand, the fixing piece 21 can be exemplified by a case where it is made of a plastic material having low heat conductivity, such as refrigerant resistance and lubricating oil resistance, such as PPS, PBT, PEEK and the like. The spiral groove 25 provided on the outer periphery of the fixed piece 21 forms a first viscous pump 16 a through which the lubricating oil 2 flows between the sleeve 19 and the spiral groove 25. The main bearing 8 is fixed to the frame 7 or formed integrally with the frame 7 and fixed. The second oil supply groove 30 having a trapezoidal cross section formed on the outer surface of the main shaft portion 9 forms the second viscous pump 16b.

  Hereinafter, the refueling operation of the hermetic compressor having such a configuration will be described. When the electric element 13 is energized, the rotor 15 rotates, and accordingly, the crankshaft 12 rotates and the compression element 4 performs a predetermined compression operation. The sleeve 19 is also rotated by the rotation of the crankshaft 12, whereby the lubricating oil 2 is agitated and pumped up by the first viscous pump 16a. The pumped lubricating oil 2 flows through the second oil supply groove 30 serving as the second viscous pump 16b with the communication hole 17 of the crankshaft 12 as a switching point, passes through the main bearing 8 and the oil supply hole 28, and is eccentric. The upper part of the compression element 4 is lubricated from the 10 holes. At this time, the dust in the lubricating oil 2 supplied through the spiral groove 25 is collected by the dust collecting groove 27 located in the middle of the spiral groove 25 provided in the fixed piece 21.

  With respect to the configuration of the first viscous pump 16 a, a gas-liquid separation chamber 18 is formed in the hollow portion of the inner diameter of the crankshaft 12, and a sleeve 19 is press-fitted into the crankshaft 12 below the gas-liquid separation chamber 18. Although it is attached, the press-fitting allowance is usually about 5 mm. Here, the lubricating oil 2 rising in the spiral groove 25 encounters the dust collecting groove 27 in the middle of the rotation, but the weight of the dust contained in the lubricating oil 2 is usually compared with that of the lubricating oil 2. Therefore, the centrifugal force acts strongly on the dust and rises while being inscribed in the sleeve 19, and enters the dust collection groove 27 and stays in the middle of the rise. In this way, the lubricating oil 2 is purified.

  The communication hole 17 provided in the crankshaft 12 feeds the lubricating oil 2 ascending the first viscous pump 16a by the first oil supply groove 26 formed by the spiral groove 25 provided on the outer periphery of the fixed piece 21 to the crankshaft 12. The second oil supply groove 30 provided on the outer surface side of the second oil pump 30 serves to move to the second viscous pump 16b side. Further, the gas of the mist refrigerant 3 including the lubricating oil 2 brought into the gas-liquid separation chamber 18 by the spiral groove 25 of the fixed piece 21 passes through the gas passage hole 29 provided in the crankshaft 12 and is connected to the piston 6 and the cylinder 5. These parts are lubricated and cooled. Further, the lubricating oil 2 that has moved up the second viscous pump 16b by the second oil supply groove 30 is lubricated to the main bearing 8, and then blown out to the upper portion of the compression element 4 through the oil supply hole 28, and the piston 6, cylinder 5 is used for lubrication and cooling of each part.

  FIG. 3 is a diagram in which the detailed structure of the crankshaft 12 provided in the hermetic compressor is compared with a conventional product. FIG. 3A is a diagram related to the conventional structure, and FIG. 3B is a diagram related to the structure of the first embodiment. FIG. Referring to FIG. 3 (a), the crankshaft 12 'having a conventional structure has a structure including an oil supply hole 28 and a gas passage hole 29 communicating with the eccentric portion 10, but a gas-liquid separation chamber 18 for centrifugal separation. ′ Is positioned on the lower end side and has a small capacity, and the gas-liquid separation chamber 18 ′ and the gas passage hole 29 are connected by an air passage 29 ′. With such a structure, when the compressor is rotated at a high speed, even if the air passage 29 'functions somewhat as a weir, the volume of the gas-liquid separation chamber 18' is small, so that the liquid of the lubricating oil 2 flows into the gas passage hole. There is a risk of leakage to the 29 side.

  On the other hand, referring to FIG. 3B, in the structure of the crankshaft 12 of the first embodiment, the gas-liquid separation chamber 18 having a large capacity is provided above the first viscous pump 16a by the fixed piece 21. The upper portion of the chamber is provided with a weir 33 for suppressing the liquid of the lubricating oil 2 from flowing to the gas passage hole 29 side. With such a structure, when the compressor is rotated at a high speed, the liquid of the lubricating oil 2 is prevented from flowing to the gas passage hole 29 side by the weir 33, and the capacity of the gas-liquid separation chamber 18 is large, so that the lubricating oil There is no possibility that the second liquid leaks to the gas passage hole 29 side.

FIG. 4 is a diagram showing characteristics in relation to the amount of oil supply (mL / min) with respect to the number of rotations (min ⁻¹ ) for each length of the fixed piece 21 provided in the hermetic compressor of the first embodiment. Referring to FIG. 4, when the axial length of the crankshaft 12 of the fixed piece 21 is, for example, 26 mm, the amount of oil supply increases with an increase in the number of rotations compared to the case of 33 mm longer than that. I understand. This is because, in the case of 33 mm, since the fixed piece 21 is long, the capacity of the gas separation / liquid separation chamber 18 is reduced. Therefore, when the compressor is rotated at a high speed, the volume of the gas separation / liquid separation chamber 18 is reduced. This is because the gas separation effect is reduced and the liquid of the lubricating oil 2 flows toward the gas passage hole 29 side.

  That is, if the communication hole 17 of the crankshaft 21 is closed by the boss portion 23 of the fixed piece 21 as described above, the supply amount of the lubricating oil 2 to the sliding portion of the main bearing 8 may be reduced. Or if the dimension of the axial direction of the crankshaft 12 of the fixed piece 21 is long, the dimension in the same direction of the gas-liquid separation chamber 18 will become short, the volume will become small, and the gas separation effect of the refrigerant | coolant 3 will fall. The problem arises.

  Accordingly, in the present invention, as a result of various studies on the supply amount of the lubricating oil 2 and the supply amount of the gas of the refrigerant 3 related to the first viscous pump 16a, if the structure of the fixed piece 21 and the crankshaft 12 is devised, It has been found that the volume of the liquid separation chamber 18 can be increased to improve the gas-liquid separation function and to solve such problems.

  Hereinafter, the improvement measures will be described in detail with reference to FIGS. FIG. 5 shows the relationship between the protruding position (protruding dimension H) of the lower end of the first viscous pump 16a with respect to the lower end 19a of the sleeve when the first viscous pump 16a and the sleeve 19 in FIG. FIG. 5 is a partial cross-sectional view illustrating the relationship between the gas-liquid separation chamber 18 and the dimensions of a sleeve 19. FIG. 6 is a perspective view showing the electric element 13 in an inverted state in order to explain the assembly structure of the first viscous pump 16a and its support member 22 shown in FIG. . FIG. 7 is a perspective view showing the arrangement relationship between the support member 22 and the insulator 32 of the first viscous pump 16a and the insulator 32 in the assembly structure shown in FIG. 6 from another direction with the spring 20 removed and the electrical connector 32b connected. It is.

First, referring to FIG. 5, as described in FIG. 2, a spiral groove 25 is formed around the spiral boss portion 23 on the outer periphery of the fixed piece 21, and this spiral groove 25 is formed by the first oil supply groove 26. A first viscous pump 16a is configured. In addition, the protrusion 34 at the tip of the fixed piece 21 is provided with a through hole 24 through which the substantially central portion of the support member 22 is penetrated and locked. Here, the fixed piece 21 is integrally formed of resin including the projecting portion 34, the boss portion 23, and the spiral groove 25. Incidentally, the sleeve 19 is press-fitted and fixed to the crankshaft 12, and the fixed piece 21 is positioned by the support member 22 and the like so as not to hit the rotating sleeve 19 in the vertical direction and the rotational direction. For example, referring to FIG. 5, the protrusion position (protrusion dimension H) of the lower end of the first viscous pump 16a (fixed piece 21) with respect to the sleeve lower end 19a is secured in the range of 0.3 to 1.6 mm, and fixed. Even if the piece 21 moves before and after the range in the axial direction of the sleeve 19, the fixed piece 21 is set so as not to hit the sleeve 19 or the crankshaft 12. Thereby, the fixed piece 21 shown in FIG. 5 is in a state of moving slightly downward from the position of the fixed piece 21 shown in FIG. By the way, the range of 0.3 to 1.6 mm of the above-described protrusion dimension H is a result of investigating and investigating the oiling effect when the compressor speed is driven at the lowest speed operation frequency of 800 min ⁻¹ . It is found as a value that gives the highest oiling effect. In this case, the oil level of the lubricating oil 2 stored in the sealed container 1 is located at a position about 5 mm from the sleeve lower end 19a. The lubricating oil 2 at such a position can be pumped up by the sleeve 19 and the spiral groove 25 of the fixed piece 21 in the first viscous pump 16a.

  Further, as shown in FIG. 5, the upper end portion of the fixed piece 21 is positioned between the upper edge portion of the sleeve 19 and the lower end portion of the communication hole 17. Is in a positional relationship that does not wrap in the height direction. This is a positional relationship in which the communication hole 17 and the fixed piece 21 are wrapped in the height direction, and when the crankshaft 12 rotates, the boss portion 23 and the communication hole, which are the outer diameters of the spiral grooves 25 of the fixed piece 21. This is because the dimension between the inlet 17 and the inlet 17 becomes small, the lubricating oil 2 hardly flows and the flow rate may decrease, and the communication hole 17 may be blocked by the boss portion 23 when the fixed piece 21 is tilted. . Therefore, the upper end portion of the fixed piece 21 is positioned below the lower end portion of the communication hole 17 so that the communication hole 17 and the fixed piece 21 do not wrap in the height direction.

  That is, in the first viscous pump 16 a, the upper end portion of the fixed piece 21 protrudes above the upper edge portion of the sleeve 19 and is positioned below the lower end portion of the communication hole 17. In addition, the inner diameter of the gas-liquid separation chamber 18 is larger than the inner diameter of the sleeve 19. As the crankshaft 12 and the sleeve 19 rotate, the lubricating oil 2 rises between the inner peripheral surface of the sleeve 19 and the outer surface of the fixed piece 21 in the first viscous pump 16a. Thereby, even when the centrifugal force is reduced due to the low speed rotation, the lubricating oil 2 can be viscously pulled up and can be stably conveyed even during the low speed rotation.

  Further, the lubricating oil 2 rising from the upper end of the sleeve 19 is released to an interference portion 18 a formed between the upper end portion of the sleeve 19 and the lower end portion of the communication hole 17. The interference portion 18a has a diameter B of the inner peripheral surface of the gas-liquid separation chamber 18 (equal to the diameter A of the inner peripheral surface of the cylindrical hollow portion of the crankshaft 12 in the structure of FIG. 6) and the boss of the fixed piece 21. It is formed by making the dimension between the diameter of the outer surface of the part 23 larger than the dimension between the diameter C of the inner peripheral surface of the sleeve 19 and the outer surface of the boss part of the fixed piece 21. In the interference portion 18a, the diameter B of the inner peripheral surface of the gas-liquid separation chamber 18 is larger than the diameter A of the inner peripheral surface of the cylindrical hollow portion of the crankshaft 12, and the diameter C of the inner peripheral surface of the sleeve 19 is gas-liquid. Another structure when the diameter is smaller than the diameter B of the inner peripheral surface of the separation chamber 18 (in this case, the relationship between the diameter A of the inner peripheral surface of the cylindrical hollow portion of the crankshaft 12 and the diameter C of the inner peripheral surface of the sleeve 19 is specified). Can be formed in the same manner.

  Therefore, when the lubricating oil 2 that has risen in the first viscous pump 16a is released from the high-pressure first viscous pump 16a and discharged to the low-pressure gas-liquid separation chamber 18, the pressure rapidly decreases and lubrication occurs. The oil 2 may flow to the gas passage hole 29 side without being separated into liquid and gas in the gas-liquid separation chamber 18, but the interference unit 18 a here includes the first viscous pump 16 a and the gas-liquid separation chamber 18. Acts to lower the pressure between. Incidentally, the magnitude of the pressure applied to the lubricating oil 2 has a relationship of the first viscosity pump 16a> interference part 18a> gas-liquid separation chamber 18. Thereby, even when the lubricating oil 2 is pulled up vigorously at high speed rotation, the pressure can be gradually reduced by the interference portion 18a, and the gas-liquid separation chamber 18 can stably separate into liquid and gas. can do. Incidentally, since the interference portion 18a in another structure described above is located immediately before the lubricating oil 2 flows into the communication hole 17, the flow of the lubricating oil 2 into the communication hole 17 becomes smooth, and the communication hole 17 Since the gas-liquid separation chamber 18 located at the upper portion becomes a stepped portion, a pressure reducing action is also applied, and there is an effect of suppressing the flow of the lubricating oil 2 to the gas passage hole 29.

  In addition, referring to FIG. 1, the positions of the lower end of the sleeve 19a and the lower end of the fixed piece 21 are set so as not to come into contact with the bottom of the hermetic container 1, assuming impact, vibration or overturning. . The center position of the through hole 24 provided in the support member 22 that supports the fixed piece 21 is also set to a position 3 to 4 mm from the sleeve lower end 19a. In addition, if it is such a dimension, about the support member 22, it is preferable to use the wire material whose outer diameter dimension is the range of 1.0-2.0 mm. Furthermore, the amount of immersion of the sleeve 19 with respect to the oil surface of the lubricating oil 2 shown in FIG. 1 is set so that the initial immersion amount is set so that the sleeve 19 is immersed in the oil surface even when the oil level is maximum lowered.

  Next, referring to FIG. 6, the electric element 13 includes the stator 14 connected to the inverter drive circuit as described above, and the rotor 15 including a permanent magnet and fixed to the crankshaft 12. A winding 31 is attached between the child 14 and the rotor 15. This winding 31 is fixed to the stator 14 via an insulator 32. A crankshaft 12 is press-fitted into the rotor 15, and a sleeve 19 and a fixed piece 21 attached to the tip of the crankshaft 12 protrude from the rotor 15. A support member 22 is inserted into the through hole 24 of the protrusion 34 at the tip of the fixed piece 21. Both end portions of the support member 22 are substantially U-shaped portions 22a bent into a substantially U-shape, and the substantially U-shaped portions 22a are inserted into the holes of the support portions 32a provided in the insulator 32. The support portion 32 a is formed integrally with a resin insulator 32. Support springs 20 attached to the four corners of the stator 14 elastically support the compression element 4 in the hermetic container 1 via the stator 14.

  The insulator 32 here has a substantially cylindrical shape, and the winding 31 is formed so as to make a round of the cylindrical portion. As shown in FIG. 7, an electrical connector 32 b extends from a part of the winding 31. A crossover support portion 32c that connects the windings 31 is formed integrally with a part of the insulator 32 around the electrical connector 32b. A rising wall 32 d that shields the winding 31 is formed integrally with the insulator 32. Incidentally, the support part 32a provided in the insulator 32 is provided at a position that avoids the electrical connector 32b and the crossover support part 32c and connects the rising wall 32d diagonally.

  In such a structure, the mounting position of the support member 22 is set so as not to obstruct the electrical connector 32b and the crossover support portion 32c, so that the support member 22 that vibrates due to the rotation of the compressor may come into contact with the winding 31. Thus, even if the compressor is used for a long time, the coil forming the winding 31 is prevented from being damaged or disconnected.

  In any case, according to the hermetic compressor according to the first embodiment, the lubricating oil 2 is pumped up by the viscous pump action of the first viscous pump 16a by the sleeve 19 and the fixed piece 21 as the crankshaft 12 rotates. In the gas-liquid separation chamber 18 in the inner diameter hollow portion 12, the liquid and the gas including the mist state (gas of the refrigerant 3) are separated and supplied to the sliding portion through the communication hole 17, and the gas is supplied to the gas passage hole 29. In the gas-liquid separation chamber 18, when the interference portion 18 a formed between the upper end portion of the sleeve 19 and the lower end portion of the communication hole 17 decompresses the lubricating oil 2, In addition to being used for gas-liquid separation, the volume of the lubricating oil 2 stored in the room as it is pumped is increased so that the liquid does not overflow to the gas passage hole 29 side. Weir 33 (Osegi 33a, small weir 33b) was with liquid lubricant 2 suppressing structure dammed to flow into the gas passage holes 29 side by the.

  That is, in the hermetic compressor according to the first embodiment, a sufficient volume of the gas-liquid separation chamber 18 is ensured, and the lubricating oil that is supplied abundantly regardless of the rotational speed of the compressor is stored in the gas-liquid separation chamber 18. Since it is used for gas-liquid separation after being depressurized by the interference section 18a, the liquid and the gas including the mist state are efficiently separated from the lubricating oil 2, and the pumped lubricating oil 2 is on the bearing (main bearing 8) side. The sliding part is not damaged without turning around. Moreover, since the attachment structure by the support member 22 with respect to the fixed piece 21 of the 1st viscous pump 16a is devised, even if the crankshaft 12 rotates at low speed, the fixed piece 21 is always immersed in the lubricating oil 2 and lubricated. Oil 2 is abundantly supplied to the sliding part. As a result, even if the fixed piece 21 is provided, the gas of the refrigerant 3 can be separated from the lubricating oil 2 with high efficiency, and the lubricating oil 2 and the gas of the refrigerant 3 can be separated in the compressor even during low-speed rotation or high-speed rotation. Since the separation is stabilized and the compression operation is performed smoothly, the cooling performance in the refrigeration system is improved. Therefore, if such a refrigeration system is applied to a refrigerator, it can contribute to improvement of cooling performance and reliability.

  FIG. 8 is a perspective view illustrating a first modification of the viscous pump (first viscous pump 16a) provided in the hermetic compressor according to the second embodiment. Referring to FIG. 8, in the first modification of the first viscous pump 16a, the shape of the through hole 24a in the protrusion 34a at the tip of the fixed piece 21a is a long hole (elliptical shape). Thus, the clearance of the movement of the support member 22 in the axial direction (vertical direction) of the crankshaft 12 is increased. However, as described in the first embodiment, the protrusion dimension H of the lower end of the fixed piece 21a with respect to the sleeve lower end 19a is set in the range of 0.3 to 1.6 mm.

  If the structure of the fixed piece 21a of the second embodiment is applied, the shape of the through hole 24a is a long hole, so that the fixed piece 21a moves up and down at the time of high-speed rotation or low-speed rotation of the crankshaft 12, and always the lubricating oil 2 Therefore, the lubricating oil 2 is supplied to the gas-liquid separation chamber 18 without being interrupted regardless of the rotational speed of the crankshaft 12, and is supplied to the sliding portion after being separated from the gas-liquid. become. As a result, the compression operation is smoothly performed as in the case of the first embodiment, which can contribute to the improvement of the cooling performance in the refrigeration system.

  FIG. 9 is a perspective view illustrating a second modification of the viscous pump (first viscous pump 16a) provided in the hermetic compressor according to the third embodiment. Referring to FIG. 9, in the second modification of the first viscous pump 16a, the protrusion 34b at the tip of the fixed piece 21b has a substantially conical shape with a rounded tip. The shape is a round hole. However, as described in the first embodiment, the protrusion dimension H of the lower end of the fixed piece 21b with respect to the sleeve lower end 19b is set in the range of 0.3 to 1.6 mm.

  If the structure of the fixed piece 21b of the third embodiment is applied, the shape of the protrusion 34b at the tip of the fixed piece 21b is a substantially conical shape that approximates the oil surface of the lubricating oil 2, thereby fixing the crankshaft 12 during rotation. It is suppressed that the oil surface is disturbed by the protrusion 34b at the tip of the piece 21b, and the lubricating oil 2 is smoothly supplied to the gas-liquid separation chamber 18 and separated into gas and liquid, and then supplied to the sliding portion. become. As a result, the compression operation is smoothly performed as in the case of the first embodiment, which can contribute to the improvement of the cooling performance in the refrigeration system.

  FIG. 10 is a perspective view illustrating a third modification of the viscous pump (first viscous pump 16a) provided in the hermetic compressor according to the fourth embodiment. Referring to FIG. 10, in the third modification of the first viscous pump 16a, the protrusion 34c at the tip of the fixed piece 21c has a substantially conical shape with a rounded tip. This is a case where the shape (elliptical shape) is a long hole, thereby increasing the movement clearance of the support member 22 in the axial direction (vertical direction) of the crankshaft 12. However, here, as described in the first embodiment, the protrusion dimension H of the lower end of the fixed piece 21c with respect to the sleeve lower end 19c is in the range of 0.3 to 1.6 mm.

  If the structure of the fixed piece 21c of the fourth embodiment is applied, the shape of the protrusion 34c at the tip of the fixed piece 21c is made to be a substantially conical shape that approximates the oil surface of the lubricating oil 2, and the shape of the through hole 24c is a long hole. As a result, regardless of the rotational speed of the crankshaft 12, the fixed piece 21c moves up and down and is always immersed in the lubricating oil 2, and the oil surface is prevented from being disturbed by the protrusion 34c at the tip of the fixed piece 21c. Then, the lubricating oil 2 is more smoothly supplied to the gas-liquid separation chamber 18 and separated into gas and liquid, and then supplied to the sliding portion. That is, here, the through-hole 24c of the substantially conical protrusion 34c is made into a long hole, so that, for example, depending on the depth of the oil surface of the lubricating oil 2 deformed into a bowl shape even when the crankshaft 12 rotates at a low speed. Since the fixed piece 21c moves up and down, the lubricating oil 2 can be supplied to the sliding portion abundantly without interruption. As a result, the compression operation is smoothly performed as in the case of the first embodiment, which can contribute to the improvement of the cooling performance in the refrigeration system.

  Incidentally, in the hermetic compressors according to the above-described embodiments, the sleeve 19 is formed of a metal or the like with relatively little thermal deformation as described above, but the fixed piece 21 is made of a plastic material such as PPS, PBT, PKEK, etc. are molded. Each embodiment has a great feature of combining a metal sleeve 19 and a resin fixed piece 21, 21a, 21b, 21c. In Patent Document 1 and Patent Document 2, both the sleeve and the fixed piece are resin. Unlike the idea that it is preferable to be made of metal, at least the sleeve 19 needs to be made of metal. The reason is that if the sleeve 19 is made of resin, there is a possibility that the sleeve 19 may be damaged if the sleeve 19 is forcibly pressed into the metal crankshaft 12. Thus, if the sleeve 19 is made of metal, it can be easily press-fitted into the crankshaft 12.

  Further, when the fixed pieces 21, 21 a, 21 b, and 21 c are molded, burrs may occur in the spiral groove 25 depending on how the split molds are aligned. turn into. For this reason, it is necessary to devise the manufacturing method of the fixing pieces 21, 21 a, 21 b, 21 c or the alignment position of the split mold so as not to generate burrs in the spiral groove 25. By not producing burrs, it is possible to manufacture the fixed pieces 21, 21a, 21b, and 21c that are extremely advantageous in terms of productivity and cost.

  Incidentally, when the refrigeration system including the hermetic compressor according to each embodiment described above is mounted on a refrigerator, for example, the configuration described with reference to FIG. 7 in Japanese Patent Laid-Open No. 2013-68112 can be applied as it is. Therefore, it is not detailed here.

  In addition, about the 1st viscous pump 16a of the hermetic compressor which concerns on each Example mentioned above, the shape of the protrusion part 34, 34a-34c of the fixed pieces 21, 21a, 21b, 21c is changed into the thing of another form. However, the shape of the through-holes 24, 24a to 24c provided therein can be appropriately modified and variously selected, so that the hermetic compressor of the present invention is not limited to the form disclosed in each embodiment.

1 Airtight container 2 Lubricating oil
DESCRIPTION OF SYMBOLS 3 Refrigerant 4 Compression element 5 Cylinder 6 Piston 7 Frame 8 Main bearing 9 Main shaft part 10 Eccentric part 11 Connecting rod 12 Crankshaft 12a Lower tip part 13 Electric element 14 Stator 15 Rotor 16 1st viscosity pump 16b 2nd viscosity Pump 17 Communication hole 18 Gas-liquid separation chamber 19 Sleeve 20 Support spring 21, 21a to 21c Fixed piece 22 Support member 22a Substantially U-shaped part 23 Boss part 24, 24a to 24c Through hole 25 Spiral groove 26 First oil supply groove 27 Garbage collection groove 28 Oil supply hole 29 Gas passage hole 30 Second oil supply groove 31 Winding 32 Insulator 32a Support part 32b Electrical connector 32c Crossover support part 32d Rising wall 33 Weir 33a Large weir 33b Small weir 34, 34a-34c Projection

Claims (5)

A crankshaft that is rotatably supported by a main bearing in a sealed container that stores lubricating oil and that has a rotor attached to the outer periphery thereof, and is provided in the crankshaft so that the inside of the sealed container and the inner diameter hollow portion of the crankshaft communicate with each other. A gas passage hole, a communication hole provided in the crankshaft for communication between the inner diameter portion of the main bearing and the inner diameter hollow portion, and a hollow press-fitted into a lower portion of the inner diameter hollow portion of the crankshaft. And a fixed piece having a concave and convex shape with a spiral surface, and a viscous pump action by the sleeve and the fixed piece accompanying the rotation of the crankshaft. A gas containing liquid and mist in a gas-liquid separation chamber that pumps up the lubricating oil and forms an oil separation space in the hollow portion of the inner diameter Separated into supplies the liquid to the sliding portion via the communication hole, the closed-type compressor for supplying the gas to the compression element through the gas through-holes,
An upper end portion of the fixed piece is positioned between an upper edge portion of the sleeve and a lower end portion of the communication hole, and the gas-liquid separation chamber includes a diameter of an inner peripheral surface of the cylindrical hollow portion and a boss of the fixed piece. Interference for pressure reduction formed by making the dimension between the outer surface diameter of the part larger than the dimension between the inner peripheral surface diameter of the sleeve and the outer surface diameter of the boss part of the fixed piece A hermetic compressor characterized by a structure having a part.   2. The hermetic compressor according to claim 1, wherein a distal end portion of the fixed piece protrudes within a range of 0.3 to 1.6 mm from a distal end of the sleeve.   2. The hermetic compressor according to claim 1, further comprising a support member that restrains the movement of the fixed piece in a rotation direction and a vertical direction, and the support member is a part of an insulator that constitutes an electric element that rotates the crankshaft. A hermetic compressor that is locked to   4. The hermetic compressor according to claim 3, wherein the support member is attached at a position that avoids an electrical connector and a crossover support provided on the insulator.   A refrigerator comprising a refrigeration system equipped with the hermetic compressor according to any one of claims 1 to 4.