CN201159151Y - hermetic compressor - Google Patents

Abstract

The utility model provides a hermetical compressor, which comprises an electric unit and a compression unit, wherein the electric unit is provided with a stator and a rotor, and the compression unit is driven by the electric unit, the compression unit comprises a shaft, an operating cylinder body, a main bearing, a piston, a connecting mechanism and a thrust ball bearing, wherein the shaft is provided with a main shaft portion and an eccentric shaft portion, the main bearing is formed on the operating cylinder body and is in pivot bearing the main shaft portion of the shaft, the piston reciprocates, the connecting mechanism connects the piston with the eccentric shaft portion, the thrust ball bearing is provided with a plurality of balls and a seat portion to retain the balls, and the seat portion is made of polymerized substances of diaminobutane and adipic acid.

Description

hermetic compressor

technical field

The utility model relates to a hermetic compressor used for freezing and refrigerating devices and the like.

Background technique

In recent years, for hermetic compressors used in refrigerating apparatuses and the like, higher efficiency, lower noise, and higher reliability have been demanded in order to reduce power consumption.

Such a conventional hermetic compressor has a structure in which a thrust ball bearing is used for efficiency improvement, and the shaft is rotatable with respect to the main bearing (for example, refer to Patent Documents 1 and 2).

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

FIG. 9 is a longitudinal sectional view of a conventional hermetic compressor described in Patent Document 1, and FIG. 10 is an enlarged view of an essential part of FIG. 9 .

9 and 10, in the airtight container 1, the electric unit 2 composed of the stator 52 and the rotor 54 and the compression unit 4 driven by the electric unit 2 are accommodated respectively, and the lubricating oil 6 is stored at the bottom. The electric unit 2 and the compression unit 4 are integrated to form a compression mechanism 8, and the compression mechanism 8 is elastically supported in the airtight container 1 by a plurality of coil springs (not shown).

A cylinder-shaped compression chamber 22 is formed in a cylinder block 20 constituting the compression unit 4 , and a piston 24 is fitted into the compression chamber 22 so as to be able to reciprocate. A main bearing 26 is fixed to an upper portion of the cylinder block 20 , and a thrust surface 28 is formed above the main bearing 26 .

The shaft 30 includes a main shaft portion 34 axially supported by the main bearing 26 in the vertical direction and having a spiral groove 32 on the outer periphery, and an eccentric shaft portion 36 formed therebelow. In addition, a tubular oil supply pipe 42 is press-fitted into an oil supply hole (not shown) formed in the lower end 38 of the eccentric shaft portion 36 , and the eccentric shaft portion 36 and the piston 24 are coupled via a coupling mechanism 44 .

One end of the oil supply pipe 42 communicates with the spiral groove 32 through the oil supply hole, and the lower end opening 46 opens into the lubricating oil 6 .

The electric unit 2 is fixed above the cylinder block 20 and is composed of a stator 52 wound with a winding 50 and a rotor 54 fixed to the main shaft portion 34 of the shaft 30 by shrink fitting or the like.

A hole plane 58 is formed in a counterbore 56 that is a recess in the lower portion 55 of the rotor 54 , and a thrust surface 28 is formed at the upper end of the main bearing 26 . A thrust ball bearing 60 for supporting the shaft 30 is disposed between the hole plane 58 in the countersink 56 and the thrust surface 28 .

The thrust ball bearing 60 includes a plurality of balls 62 , a seat portion 64 holding the balls 62 , and an upper race 66 and a lower race 68 arranged above and below the balls 62 . Furthermore, the upper race 66 is in contact with the hole plane 58 , and the lower race 68 is in contact with the thrust surface 28 .

The seat portion 64 of the thrust ball bearing 60 is formed of a polymer obtained by polycondensing hexamethylenediamine and adipic acid (hereinafter referred to as “polymer A”).

Hereinafter, the operation of the hermetic compressor configured as above will be described.

When the electric unit 2 is energized by an external power source, the rotor 54 rotates, and the shaft 30 rotates accordingly. Then, the rotational movement of the eccentric shaft portion 36 is transmitted to the piston 24 via the coupling mechanism 44 . Then, the piston 24 reciprocates in the compression chamber 22, and the compression unit 4 performs a predetermined compression operation.

Accordingly, the refrigerant gas is sucked into the compression chamber 22 from the cooling system (not shown), compressed, and then discharged to the cooling system.

At this time, the oil supply pipe 42 draws up the lubricating oil 6 by centrifugal force to lubricate the sliding parts (not shown). In addition, a part of lubricating oil 6 is supplied from the spiral groove 32 to the thrust surface 28 to lubricate the thrust ball bearing 60 .

Therefore, the weight of the shaft 30 and the rotor 54 is supported by the thrust ball bearing 60 , and when the shaft 30 rotates, the balls 62 roll between the upper race 66 and the lower race 68 . Therefore, the torque for rotating the shaft 30 supported by the thrust ball bearing 60 is smaller than that of the thrust sliding bearing. Therefore, the loss in the thrust bearing can be reduced, and the input can be reduced, so that the compression operation can be performed efficiently.

In addition, among the conventional hermetic compressors described above, other hermetic compressors that are different from the hermetic compressors described above will be described with reference to the drawings.

FIG. 11 is a longitudinal sectional view of a conventional hermetic compressor described in Patent Document 2, and FIG. 12 is an enlarged view of an essential part of FIG. 11 .

In FIGS. 11 and 12 , an electric unit 108 including a stator 104 and a rotor 106 and a compression unit 110 rotatably driven by the electric unit 108 are housed in an airtight container 102 . Also, lubricating oil 112 is stored at the bottom inside the airtight container 102 . In addition, the electric unit 108 and the compression unit 110 are integrated to form a compression mechanism 114 . In addition, the compression mechanism 114 is elastically supported in the airtight container 102 by a plurality of coil springs 116 .

The compression unit 110 includes a shaft 126 including an eccentric shaft portion 124 formed via a main shaft portion 120 and a flange portion 122 , a cylinder block 132 forming a compression chamber 130 , and a main bearing 134 provided on the cylinder block 132 and supporting the shaft 126 . In addition, the compression unit 110 further includes a piston 136 reciprocating in the compression chamber 130 and a coupling mechanism 138 coupling the piston 136 and the eccentric shaft portion 124 . Furthermore, it also includes an upper race seating surface 142 provided on the lower portion 139 of the flange portion 122 of the shaft 126 and arranged at a substantially right angle to the axis 140 of the main shaft 120, and an upper race seating surface 142 arranged on the upper portion of the main bearing 134 and aligned with the shaft of the main bearing. The core 140 is provided with an upper end surface 144 at a substantially right angle, and a thrust ball bearing 146 provided between the upper race seat surface 142 and the upper end surface 144 forms a reciprocating compressor.

In addition, the shaft 126 has an oil supply mechanism 150 whose one end communicates with the lubricating oil 112 stored in the airtight container 102 , and an oil supply groove 152 on the main shaft portion 120 that supplies a part of the lubricating oil 112 picked up by the oil supply mechanism 150 to the upper end surface 144 . .

Here, the electric unit 108 is composed of a stator 104 fixed below the cylinder block 132 and a rotor 106 fixed to the main shaft portion 120 by shrink fitting or the like.

Further, the thrust ball bearing 146 includes, as shown in FIG. 12 , a plurality of balls 160 , a seat portion 162 holding the balls 160 , and an upper race 164 and a lower race 166 arranged above and below the balls 160 . Furthermore, the upper race 164 is in contact with the upper race seating surface 142 of the flange portion 122 , and the lower race 166 is in contact with the upper end surface 144 .

The seat portion 162 of the thrust ball bearing 146 is also formed of a polymer A obtained by polycondensing hexamethylenediamine and adipic acid described in Patent Document 1. As shown in FIG.

Hereinafter, the operation of the hermetic compressor configured as above will be described.

When the electric unit 108 is energized by an external power source (not shown), the rotor 106 rotates, and the shaft 126 rotates accordingly. Furthermore, the motion of the eccentric shaft portion 124 is transmitted to the piston 136 via the coupling mechanism 138 . Accordingly, the piston 136 reciprocates in the compression chamber 130, and the compression unit 110 performs a predetermined compression operation.

Accordingly, the refrigerant gas is sucked into the compression chamber 130 from the cooling system (not shown), compressed, and then discharged to the cooling system.

At this time, the lubricating oil 112 is sucked up by the oil supply mechanism 150 of the shaft 126 to lubricate each sliding part (not shown). Further, a part of lubricating oil 112 is supplied from oil supply groove 152 to upper end surface 144 to lubricate thrust ball bearing 146 .

Therefore, the weight of the shaft 126 and the rotor 106 is supported by the thrust ball bearing 146 , and the balls 160 roll between the upper race 164 and the lower race 166 when the shaft 126 rotates. Therefore, the torque for rotating the shaft 126 supported by the thrust ball bearing 146 becomes smaller than that of the thrust sliding bearing. Therefore, the loss in the thrust bearing can be reduced, and the input can be reduced, so that the compression operation can be performed efficiently.

However, with the above-mentioned conventional configurations shown in Patent Document 1 and Patent Document 2, the input may increase during severe operation in which the temperature in the airtight container 1, 102 rises, such as a long continuous operation time. Then, when the hermetic compressor with large input was disassembled and the cause was investigated, it was found that there were deposits on the side of the raceway surface where the balls 62, 160 of the upper race 66, 164 and the lower race 68, 166 rolled, and the lubricating oil 6 , 112 also produce floats.

As a result of analyzing the components of the attached matter and floating matter, these components were consistent with the components of the seats 64 , 162 of the thrust ball bearings 60 , 146 . Accordingly, it was found that the adhered matter and floating matter were low polymers (hereinafter referred to as “oligomers”) eluted from the seat portions 64 and 162 .

In addition, the seat portions 64 and 162 were placed in a hermetically sealed airtight container together with the refrigerant and lubricating oil, and a sealed tube test in which it was heated to a high temperature was performed. Also in this sealed tube test, it was confirmed that oligomers were eluted in the lubricating oil in the same manner as the component analysis results of the above-mentioned deposits and floating substances.

On the other hand, it can be seen that, for example, in a hermetic compressor operated under the operating condition that the continuous operating time is short, that is, the temperature in the airtight container 1, 102 is not high, the input does not increase, and the above-mentioned oligomers do not occur. . It was thus found that the input of the hermetic compressor increases due to the generation of oligomers.

That is, it is considered that the oligomers adhering to the raceway surfaces of the upper races 66, 164 and the lower races 68, 166 act as resistance during operation of the hermetic compressor, making it difficult for the balls 62, 160 to roll. In addition, the input of the hermetic compressor increases, and oligomers eluted in the lubricating oil 6 , 112 are sucked up together with the lubricating oil 6 , 112 via the oil supply pipe 42 and the oil supply mechanism 150 . When such a situation occurs, oligomers adhere to the respective sliding parts of the shafts 30 and 126 and the main bearings 26 and 134, thereby increasing the sliding resistance. As a result, it was found that the calorific value increases, the temperature inside the airtight container 1, 102 rises, and furthermore, the reliability of the hermetic compressor may decrease.

Patent Document 1: JP-A-61-53474

Patent Document 2: JP-A-2005-127305

Utility model content

The utility model solves the above-mentioned problems, and provides a high-efficiency and high-reliability hermetic compressor that suppresses the generation of oligomers from the seat portion and suppresses the increase in input even during operation where the temperature inside the hermetic compressor rises.

The hermetic compressor of the present invention is characterized in that lubricating oil is stored in a hermetic container, and an electric unit having a stator and a rotor and a compression unit driven by the electric unit are accommodated, and the compression unit includes a main shaft. and the shaft of the eccentric shaft portion, the cylinder block forming the compression chamber, the main bearing of the main shaft portion formed on the cylinder block and pivotally supporting the shaft, the piston reciprocating in the compression chamber, and the coupling A coupling mechanism between the piston and the eccentric shaft portion, and a thrust ball bearing, the thrust ball bearing includes a plurality of balls and a seat portion holding the balls, and the seat portion is formed of a polymer.

That is, in the hermetic compressor of the present invention, the seat portion of the thrust ball bearing is formed of a polymer (hereinafter referred to as "polymer" B) produced by polycondensation of diaminobutane and adipic acid. The polymer B forming the seat here is excellent in heat resistance, oil resistance, and refrigerant resistance, and thus can prevent oligomers from eluting from the seat even when the temperature of the seat rises due to operating conditions and the like. Therefore, oligomers eluted from lubricating oil do not adhere to the raceway surfaces of the upper race and the lower race, and it is possible to prevent the balls from becoming difficult to roll.

As a result, in the hermetic compressor of the present invention, even under severe conditions where the temperature of the hermetic compressor rises, oligomers eluted from lubricating oil will not accumulate on the upper race and the upper race as attachments. In the case of the raceway side of the lower race, there is no heat generation due to the adhesion of oligomers, so an increase in input can be suppressed, and a highly efficient and highly reliable hermetic compressor can be realized.

Description of drawings

Fig. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention.

Fig. 2 is an enlarged view of a main part of the hermetic compressor according to Embodiment 1 of the present invention.

Fig. 3 is a longitudinal sectional view of the rotor according to Embodiment 1 of the present invention.

Fig. 4 is a top sectional view of the rotor according to Embodiment 1 of the present invention.

Fig. 5 is a longitudinal sectional view of a hermetic compressor according to Embodiment 2 of the present invention.

Fig. 6 is an enlarged view of main parts of a hermetic compressor according to Embodiment 2 of the present invention.

7 is a longitudinal sectional view of a rotor according to Embodiment 2 of the present invention.

Fig. 8 is a top sectional view of a rotor according to Embodiment 2 of the present invention.

Fig. 9 is a longitudinal sectional view of a conventional hermetic compressor.

Fig. 10 is an enlarged view of essential parts of a conventional hermetic compressor.

Fig. 11 is a longitudinal sectional view of another conventional hermetic compressor.

Fig. 12 is an enlarged view of essential parts of another conventional hermetic compressor.

In the figure: 201, 302- airtight container, 202, 308- electric unit, 204, 310- compression unit, 206, 312- lubricating oil, 208, 314- compression mechanism, 220, 320- working cylinder, 222, 322- Compression chamber, 224, 324-piston, 226, 326-main bearing, 228-thrust surface, 230, 340-shaft, 232-spiral groove, 234, 342-main shaft part, 236, 346-eccentric shaft part, 238-lower end , 242-oil supply pipe, 244, 354-connecting mechanism, 246-lower end opening, 248-central axis, 250, 360-winding, 251, 304-stator, 252, 306-rotor, 254, 362-rotor core, 256, 364-seam, 258, 366-aluminum rod, 260, 368-short-circuit ring A, 261, 370-short-circuit ring B, 262, 380-bottom, 264-countersink, 266-hole plane, 268, 334-inner Wall surface, 270, 384-thrust ball bearing, 272, 386-ball, 274, 388-seat, 276, 390-upper race (レ一ス), 278, 392-lower race, 316-coil spring, 328- Thrust groove, 330-axis center, 332-upper end surface, 344-flange, 350-oil supply mechanism, 352-oil supply groove, 382-upper seat ring seating surface, 385-outer surface.

Detailed ways

Hereinafter, one Embodiment of this invention is demonstrated using drawing. In the following drawings, each dimension is enlarged for easy understanding of the structure. In addition, since the same code|symbol is attached|subjected to the same unit, description may be abbreviate|omitted.

(Embodiment 1)

Fig. 1 is a longitudinal sectional view of a hermetic compressor according to Embodiment 1 of the present invention. FIG. 2 is an enlarged view of an essential part of FIG. 1 .

In FIGS. 1 and 2 , an electric unit 202 composed of a stator 251 and a rotor 252 and a compression unit 204 rotationally driven by the electric unit 202 are accommodated in a sealed container 201 , and lubricating oil 206 is stored at the bottom.

In addition, the electric unit 202 and the compression unit 204 are integrated to form a compression mechanism 208 . The compression mechanism 208 is elastically supported in the airtight container 201 by a plurality of coil springs (not shown).

A cylindrical compression chamber 222 is formed in the cylinder block 220 constituting the compression unit 204 , and a piston 224 is reciprocally fitted in the compression chamber 222 . A main bearing 226 is fixed to an upper portion of the cylinder block 220 , and a thrust surface 228 is formed above the main bearing 226 .

The shaft 230 includes a main shaft portion 234 that is vertically supported by the main bearing 226 and has a spiral groove 232 on its outer periphery, and an eccentric shaft portion 236 formed therebelow. In addition, an oil supply pipe 242 formed of a steel pipe is press-fitted into an oil supply hole (not shown) formed in the lower end 238 of the eccentric shaft portion 236 , and the eccentric shaft portion 236 and the piston 224 are connected via a connecting mechanism 244 .

One end of the oil supply pipe 242 communicates with the spiral groove 232 from the lower end 238 of the eccentric shaft portion 236 .

The electric unit 202 is formed of an easy-to-operate induction motor that can rotate when connected to a commercial power source, and is fixed above the cylinder block 220 with bolts (not shown). Furthermore, the electric unit 202 is constituted by a stator 251 having a winding 250 and a rotor 252 fixed to the main shaft portion 234 of the shaft 230 by shrink fitting or the like.

FIG. 3 is a vertical cross-sectional view of the rotor 252 according to the first embodiment, and FIG. 4 is a top cross-sectional view of the rotor 252 according to the first embodiment.

As shown in FIGS. 3 and 4 , the rotor 252 is constructed by placing an aluminum rod 258 in the slot 256 equally arranged on the outer peripheral side of the rotor core 254 of laminated iron plates, and using aluminum short-circuit rings A260 and short-circuit rings B261 to connect the aluminum rods. 258 short-circuited at both ends of the basket.

As shown in FIGS. 1 to 3 , a part of the main bearing 226 is put into the rotor 252 so that they overlap, and a countersunk hole 264 as a recess is provided in the lower part 262 of the rotor 252, thereby shortening the length of the shaft 230 and sealing the container 201. The height is kept low.

A ring-shaped hole plane 266 is formed in a countersink 264 serving as a recess in the lower portion 262 of the rotor 252 , and is formed substantially at right angles to the central axis 248 . Furthermore, an annular thrust surface 228 is formed at an upper end of the main bearing 226 and is substantially perpendicular to the central axis 248 . A thrust ball bearing 270 for supporting the shaft 230 is arranged between the hole plane 266 in the counterbore 264 and the thrust surface 228 . At least a part of the thrust ball bearing 270 enters the counterbore 264 so that its periphery is surrounded by the inner wall surface 268 of the counterbore 264 , and the upper part becomes a dead end.

The thrust ball bearing 270 includes a plurality of balls 272 , a seat portion 274 holding the balls 272 , and an upper race 276 and a lower race 278 arranged above and below the balls 272 . Also, upper race 276 adjoins bore plane 266 and lower race 278 adjoins thrust face 228 .

The balls 272 are made of high wear-resistant carburized and quenched bearing steel, and the upper race 276 and the lower race 278 are also made of heat-treated carbon steel with high wear resistance. In addition, the seat portion 274 of the thrust ball bearing 270 is formed of a polymer B obtained by polycondensing diaminobutane and adipic acid.

This polymer B has a structure in which four methylene groups are regularly arranged between amide bonds, and has a high crystallization rate and high crystallinity. Specifically, the crystallinity is about 40 to 45%, and it is excellent in heat resistance, oil resistance, and refrigerant resistance.

In addition, the manufacturing method of the hermetic compressor described in Embodiment 1 includes a finished product step of assembling components to form a finished product, and an assembly step of drying the inside of the hermetic compressor as a finished product. In this assembly process, the hermetic compressor is heated for a certain period of time in a constant temperature furnace heated to a temperature of 150° C. or higher. Accordingly, the mechanical properties of the seat portion 274 of the thrust ball bearing 270 formed of the polymer B can be brought into a thermally stable state.

Hereinafter, the operation of the hermetic compressor configured as above will be described.

When the electric unit 202 shown in FIGS. 1 to 4 is energized by an external power source (not shown), the rotor 252 rotates, and the shaft 230 rotates accordingly. Then, the rotational motion of the eccentric shaft portion 236 is transmitted to the piston 224 via the connection mechanism 244, and the piston 224 reciprocates in the compression chamber 222, whereby the compression unit 204 performs a predetermined compression operation.

Accordingly, the refrigerant gas is sucked into the compression chamber 222 from the cooling system (not shown), compressed, and then discharged to the cooling system.

At this time, one end of the oil supply pipe 242 is pressed into the lower end 238 of the eccentric shaft portion 236, and the lower end opening 246 is bent on the extension line of the central axis 248 of the main shaft portion 234, so that the lubricating oil is picked up by centrifugal force as the shaft 230 rotates. 206. Lubricating oil 206 lubricates each sliding portion, and a part thereof is supplied from spiral groove 232 to thrust surface 228 to lubricate thrust ball bearing 270 .

The weight of the shaft 230 and the rotor 252 is supported by the thrust ball bearing 270, and when the shaft 230 rotates, the ball 272 rolls between the upper race 276 and the lower race 278, so that the rotational torque of the shaft 230 is lower than that of the thrust sliding bearing. Small. Therefore, the loss in the thrust bearing can be reduced, and the input can be reduced, so that high efficiency can be realized.

Next, heat on thrust ball bearing 270 will be described.

When the hermetic compressor is running, for example, if the continuous running time is too long, since the electric unit 202 is formed by an induction motor, the winding 250 of the stator 251, the aluminum rod 258 of the rotor 252 and the short-circuit ring A260 and short-circuit ring B261 at both ends continuous current flow. Therefore, the temperature of the stator 251 and the rotor 252 rises to a higher temperature than that of a rotor provided with permanent magnets.

In addition, as the operating load increases, the value of the current flowing through the electric unit 202 also increases, and similarly, the temperatures of the stator 251 and the rotor 252 increase.

The heat of the stator 251 is directly transferred to the compression unit 204 and the lubricating oil 206 , or transferred to the hermetic container 201 via refrigerant gas, thereby increasing the temperature of each part of the hermetic compressor.

The temperature of the thrust ball bearing 270 rises as the temperature of the compression unit 204, the stator 251, the rotor 252, and the like rises. In addition, the thrust ball bearing 270 is also exposed to the high-temperature and low-viscosity lubricating oil 206 supplied from the spiral groove 232 for lubrication.

Furthermore, a part of the thrust ball bearing 270 is disposed in the countersink 264 of the rotor 252 and its periphery is surrounded by the inner wall surface 268 . Therefore, the upper part of the thrust ball bearing 270 is in a dead end state, and the lower part forms a small space that is approximately a closed space surrounded by the stator 251, the main bearing 226, and the working cylinder block 220. Therefore, the thrust ball bearing 270 and the refrigerant gas around it are very It becomes difficult to dissipate heat to other components, and the temperature rises further.

The temperature of the seat portion 274 constituting the thrust ball bearing 270 also rises due to the above reasons, and since it is sandwiched between the upper race 276 and the lower race 278, it is difficult to dissipate heat, so the temperature rises.

The seat portion 274 is formed of polymer B excellent in heat resistance, oil resistance, and refrigerant resistance. Therefore, as described above, even if a part of seat portion 274 is arranged in counterbore 264 where heat dissipation is difficult and the temperature rises, oligomers can be prevented from being eluted from seat portion 274 . Furthermore, it was also confirmed by experiments that oligomers eluted from the lubricating oil 206 can be prevented from adhering to the raceway surfaces of the upper race 276 and the lower race 278 .

In addition, since the oligomers are not eluted in the lubricating oil 206 , they are not sucked up together with the lubricating oil 206 via the oil supply pipe 242 , and the oligomers do not adhere to sliding parts such as the shaft 230 and the main bearing 226 . As a result, it was confirmed that the thrust ball bearing 270 does not increase the sliding resistance, and the reliability is improved.

From the above results, it is considered that when the seat portion 274 is formed of the polymer B, even when the temperature becomes high, the movement of the polymer B molecules excellent in heat resistance, oil resistance, and refrigerant resistance can be suppressed, so that the heat from the seat portion 274 is prevented. Oligomers are eluted. As a result, it is considered that oligomers do not accumulate on the raceway surfaces of the upper race 276 and the lower race 278 as deposits, nor do they float in the lubricating oil 206 as floating matters.

As described above, it is possible to prevent oligomers from being eluted from the thrust ball bearing 270 , thereby preventing the balls 272 from being difficult to roll, and also preventing the balls 272 from adhering to sliding parts such as the shaft 230 and the main bearing 226 to increase the sliding resistance. As a result, a high-efficiency and highly-reliable hermetic compressor suppressing an increase in input is provided.

In addition, when at least a part of the thrust ball bearing 270 is arranged in the countersunk hole 264 which is a concave portion of the rotor 252, or the motor unit 202 adopts an induction motor, even if the operating conditions such as long continuous operation time or large operating load, the thrust force The temperature of the ball bearing 270 rises to a high temperature, and since the seat portion 274 is formed of the polymer B, elution of the oligomer can be prevented. Therefore, employing such a thrust ball bearing 270 can provide a high-efficiency and highly-reliable hermetic compressor that suppresses an increase in input.

In addition, in the hermetic compressor, if water is mixed in the airtight container 201 , rust will be formed on the compression unit 204 and the inner side of the airtight container 201 , and the durability will be deteriorated. In addition, when a hermetic compressor is installed in a cooling system and operated, moisture discharged together with the refrigerant gas may freeze in the cooling system to close the cooling system, resulting in poor cooling. In order to prevent such problems, for the purpose of removing moisture in the airtight container of the hermetic compressor, in the assembly process, it is necessary to heat the airtight compressor after the finished product process of assembling the components to form a finished product. Dry drying process.

However, since the seat portion 274 is formed of the polymer B excellent in heat resistance, oil resistance, and refrigerant resistance, even if the seat portion 274 is heated at a temperature of 150° C. Even if the ambient temperature rises to a high temperature of 150° C. or higher, deformation of the seat portion 274 due to thermal deterioration can also be prevented. Therefore, the seat portion 274 may be heated at a temperature of 150° C. or higher for a certain period of time, or the seat portion 274 incorporated in a hermetic compressor may be heated at a heating temperature of 150° C. or higher.

By adopting such a method, it is possible to prevent problems such as a decrease in efficiency due to input loss, an increase in noise, and a decrease in reliability due to deformation of the seat portion 274 .

In addition, since the airtight compressor can be heated and dried for a short time in a drying furnace in which the atmosphere temperature of the seat portion 274 is at least 150° C. or higher, productivity in the assembly process can be improved.

Similarly, even if the air temperature of the thrust ball bearing 270 of the hermetic compressor is operated for a certain period of time at a temperature of 150° C. or higher, the seat portion 274 rises to a temperature of 150° C. or higher. However, due to the heat resistance of the seat portion 274 , oil resistance, and excellent refrigerant resistance are formed to prevent oligomers from eluting from the seat portion 274 . That is, the thrust ball bearing 270 may be used for a certain period of time at an ambient temperature of 150° C. or higher, or a hermetic compressor equipped with the thrust ball bearing 270 may be operated at an ambient temperature of 150° C. or higher for a certain period of time.

By adopting such a method, it is possible to prevent problems such as a decrease in efficiency due to input loss, an increase in noise, and a decrease in reliability due to deformation of the seat portion 274 .

In addition, in the first embodiment, a case where the continuous operation time is long or the operation load is large is described as an example in which the temperature of the thrust ball bearing 270 rises to a high temperature. However, other situations can be implemented similarly as long as the temperature of the thrust ball bearing 270 rises to a high temperature other than this situation, and oligomers can be prevented from being eluted from the seat portion 274 .

In addition, when the electric unit 202 is constituted by a motor using a permanent magnet, it goes without saying that the same function and effect can be obtained although the heat generation is smaller than that of an induction motor.

(Embodiment 2)

Fig. 5 is a longitudinal sectional view of a hermetic compressor according to Embodiment 2 of the present invention, and Fig. 6 is an enlarged view of an essential part of Fig. 5 .

In FIGS. 5 and 6 , an electric unit 308 composed of a stator 304 and a rotor 306 and a compression unit 310 rotationally driven by the electric unit 308 are accommodated in a sealed container 302 , and lubricating oil 312 is stored at the bottom.

In addition, the electric unit 308 and the compression unit 310 are integrated to form a compression mechanism 314 . In addition, the compression mechanism 314 is elastically supported in the airtight container 302 by a plurality of coil springs 316 .

Next, the main configuration of compression section 310 will be described.

A cylindrical compression chamber 322 is formed in the cylinder block 320 constituting the compression unit 310 , and a piston 324 is reciprocally fitted in the compression chamber 322 . A main bearing 326 is formed at a lower portion of the cylinder block 320 , and a thrust groove 328 is formed at an upper portion of the main bearing 326 .

At the bottom of the thrust groove 328 , an upper end surface 332 is formed substantially at right angles to the axis 330 of the main bearing 326 , and its periphery is surrounded by an inner wall surface 334 .

An eccentric shaft portion 346 formed via the main shaft portion 342 and the flange portion 344 is formed on the shaft 340 . The main shaft part 342 is axially supported on the main bearing 326 in the vertical direction and has an oil supply mechanism 350 whose one end communicates with the lubricating oil 312 stored in the airtight container 302 and a part of the main shaft part 342 that will be sucked up by the oil supply mechanism 350 The lubricating oil 312 is supplied to the oil supply groove 352 on the upper end surface 332 . Furthermore, the eccentric shaft portion 346 and the piston 324 are connected by a connection mechanism 354 .

The electric unit 308 is formed of an easy-to-operate induction motor that can rotate as long as it is connected to a commercial power supply. Furthermore, the motor unit 308 is fixed below the cylinder block 320 with bolts (not shown), and is composed of a stator 304 having a winding 360 and a rotor 306 fixed to the main shaft portion 342 of the shaft 340 by shrink fitting or the like.

FIG. 7 is a vertical cross-sectional view of the rotor 306 according to the second embodiment, and FIG. 8 is a top cross-sectional view of the rotor 306 according to the second embodiment.

As shown in FIG. 7 and FIG. 8, the rotor 306 is constructed by placing an aluminum rod 366 in the slit 364 equally arranged on the outer peripheral side of the rotor core 362 of laminated iron plates, and short-circuiting both ends with an aluminum short-circuit ring A368 and a short-circuit ring B370. basket shape.

On the lower portion 380 of the flange portion 344 of the shaft 340 is formed an upper race seating surface 382 that is substantially perpendicular to the axis 330 of the main shaft portion 342 . Further, a thrust ball bearing 384 is disposed between the upper race seating surface 382 and the upper end surface 332 of the main bearing 362 to support the shaft 340 . The thrust ball bearing 384 enters the thrust groove 328 of the main shaft portion 342, at least a part of the outer surface 385 of the outer periphery of the thrust ball bearing 384 is surrounded by at least a part of the inner wall surface 334 of the thrust groove 328, and the bottom becomes a dead end state.

By putting at least a part of the thrust ball bearing 384 in the thrust groove 328, the position of the eccentric shaft portion 346 can be kept low. Thereby, the height of the airtight container 301 can be suppressed low.

In addition, in the thrust groove 328, since a part of the outer side of the thrust ball bearing 384 is surrounded by the thrust groove 328 and a part of the main bearing 326, the transmission of noise from the thrust ball bearing 384 to the outside of the thrust groove 328 can be reduced. At the same time, the thrust groove 328 also serves to store lubricating oil, so that the thrust groove 328 becomes a structure capable of smoothly supplying oil to the thrust ball bearing 384 .

The thrust ball bearing 384 includes a plurality of balls 386 , a seat portion 388 holding the balls 386 , and an upper race 390 and a lower race 392 arranged above and below the balls 386 . In addition, the upper race 390 is in contact with the seating surface 382 of the upper race, and the lower race 392 is in contact with the upper end surface 332 .

The ball 386 is made of high wear-resistant carburized and quenched bearing steel, and the upper race 390 and the lower race 392 are also made of heat-treated carbon steel with high wear resistance. In addition, the seat portion 388 of the thrust ball bearing 384 is formed of a polymer B obtained by polycondensing diaminobutane and adipic acid.

This polymer B, as described in Embodiment 1, has a structure in which four methylene groups are regularly arranged between amide bonds, and has a high crystallization rate and high crystallinity. Specifically, the crystallinity is about 40 to 45%, and it is excellent in heat resistance, oil resistance, and refrigerant resistance.

In addition, the manufacturing method of the hermetic compressor described in Embodiment 2 includes a finished product step of assembling components to form a finished product, and an assembly step of drying the inside of the hermetic compressor as a finished product. In this assembly process, the hermetic compressor is heated for a certain period of time in a constant temperature furnace heated to a temperature of 150° C. or higher. Accordingly, the seat portion 388 of the thrust ball bearing 384 formed of the polymer B can be thermally stable in terms of its mechanical properties and the like.

Hereinafter, the operation of the hermetic compressor configured as above will be described.

When the electric unit 308 shown in FIGS. 5 to 8 is energized by an external power source (not shown), the rotor 306 rotates, and the shaft 340 rotates accordingly. Then, the rotational motion of the eccentric shaft portion 346 is transmitted to the piston 324 via the coupling mechanism 354, and the piston 324 reciprocates in the compression chamber 322, whereby the compression unit 310 performs a predetermined compression operation.

Accordingly, the refrigerant gas is sucked into the compression chamber 322 from the cooling system (not shown), compressed, and then discharged to the cooling system.

At this time, the shaft 340 sucks up the lubricating oil 312 by the oil supply mechanism 350 of the main shaft. Lubricating oil 312 lubricates each sliding portion, and a part thereof is supplied from oil supply groove 352 to upper end surface 332 to lubricate thrust ball bearing 384 .

The weight of the shaft 340 is supported by the thrust ball bearing 384, and when the shaft 340 rotates, the ball 386 rolls between the upper race 390 and the lower race 392, so that the torque for rotating the shaft 340 becomes smaller than that of the thrust sliding bearing. Therefore, the loss in the thrust bearing can be reduced, and the input can be reduced, so that high efficiency can be realized.

Next, heat on the thrust ball bearing 384 will be described.

When the hermetic compressor is running, for example, if the continuous running time is too long, since the electric unit 308 is formed by an induction motor, the winding 360 of the stator 304, the aluminum rod 366 of the rotor 306 and the short-circuit ring A368 and short-circuit ring B370 at both ends continuous current flow. Therefore, the temperature of the stator 304 and the rotor 306 rises to a higher temperature than that of a rotor equipped with permanent magnets.

In addition, as the operating load increases, the value of the current flowing through the electric unit 308 also increases, and similarly, the temperatures of the stator 304 and the rotor 306 increase.

The heat of the stator 304 is directly transferred to the compression unit 310 and the lubricating oil 312 or transferred to the hermetic container 302 via refrigerant gas, thereby increasing the temperature of each part of the hermetic compressor.

The temperature of the thrust ball bearing 384 rises as the temperature of the compression unit 310, the stator 304, the rotor 306, and the like rises. In addition, the thrust ball bearing 384 is also exposed to the high-temperature and low-viscosity lubricating oil 312 supplied from the oil supply tank 352 for lubrication.

Furthermore, a part of the thrust ball bearing 384 is arranged in the thrust groove 328 of the main bearing 326 . And, the periphery of the outer surface 385 of the thrust ball bearing 384 is surrounded by the inner wall surface 334 of the thrust groove 328, and the lower part is in a dead end state, and the upper part becomes a small area of an approximately closed space surrounded by the flange part 344 and the working cylinder block 320, etc. space. With such a configuration, it is difficult for the thrust ball bearing 384 and the refrigerant gas around it to dissipate heat, and the temperature rises further.

The temperature of the seat portion 388 constituting the thrust ball bearing 384 also rises due to the above reasons, and since it is sandwiched between the upper race 390 and the lower race 392, it is difficult to dissipate heat, so the temperature rises.

The seat portion 388 is formed of polymer B excellent in heat resistance, oil resistance, and refrigerant resistance. Therefore, as described above, even if a part of seat portion 388 is arranged in thrust groove 328 which is difficult to dissipate heat and the temperature rises, it is possible to prevent oligomers from being eluted from seat portion 388 . Furthermore, it was also confirmed by experiments that oligomers eluted from the lubricating oil 312 can be prevented from adhering to the raceway surfaces of the upper race 390 and the lower race 392 .

In addition, since the oligomers are not eluted in the lubricating oil 312, they are not sucked up together with the lubricating oil 312 via the oil supply mechanism 350, and the oligomers are not attached to the sliding parts such as the shaft 340 and the main bearing 326. . As a result, it was confirmed that the thrust ball bearing 384 does not increase the sliding resistance and improves reliability.

From the above results, it is considered that when the seat portion 388 is formed of the polymer B, even at a high temperature, the movement of the polymer B molecules excellent in heat resistance, oil resistance, and refrigerant resistance can be suppressed, so that the Oligomers are eluted. As a result, it is considered that oligomers do not accumulate as deposits on the raceway surfaces of upper race 390 and lower race 392 , and do not float in lubricating oil 312 as floats.

As described above, it is possible to prevent oligomers from being eluted from the thrust ball bearing 384 , thereby preventing the balls 386 from being difficult to roll, and also preventing the balls 386 from adhering to sliding parts such as the shaft 340 and the main bearing 326 to increase the sliding resistance. As a result, it is possible to provide a high-efficiency and highly-reliable hermetic compressor that suppresses an increase in input.

In addition, in the configuration where at least a part of the thrust ball bearing 384 is arranged in the thrust groove 328 of the main bearing 326, or the electric unit 308 adopts an induction motor, even due to operating conditions such as a long continuous operation time or a large operating load, the thrust ball bearing The temperature of 384 rises to a high temperature, also because the seat 388 is formed of polymer B, so that the elution of the oligomer can be prevented. Therefore, if such a thrust ball bearing 384 is adopted, it is possible to provide a high-efficiency and highly-reliable hermetic compressor that suppresses an increase in input.

In addition, in the hermetic compressor, if water is mixed in the airtight container 302 , rust will be generated inside the compression unit 310 and the airtight container 302 , and the durability will be deteriorated. In addition, when a hermetic compressor is installed in a cooling system and operated, moisture discharged together with the refrigerant gas may freeze in the cooling system to close the cooling system, resulting in poor cooling. In order to prevent such problems, for the purpose of removing moisture in the airtight container of the hermetic compressor, in the assembly process, it is necessary to heat the airtight compressor after the finished product process of assembling the components to form a finished product. Dry drying process.

However, since the seat portion 388 is formed of polymer B excellent in heat resistance, oil resistance, and refrigerant resistance, even if the seat portion 388 is heated at a temperature of 150° C. Even if the ambient temperature rises to a high temperature of 150° C. or higher, deformation of the seat portion 388 due to thermal deterioration can also be prevented. Therefore, the seat portion 388 may be heated at a heating temperature of 150° C. or higher for a certain period of time, or the seat portion 388 incorporated in a hermetic compressor may be heated at a heating temperature of 150° C. or higher.

By adopting such a method, it is possible to prevent problems such as a decrease in efficiency due to input loss, an increase in noise, and a decrease in reliability that are caused by deformation of the seat portion 388 .

In addition, since the airtight compressor can be heated and dried for a short time in a drying furnace in which the atmosphere temperature of the seat portion 388 is at least 150° C., productivity in the assembly process can be improved.

Similarly, even if the air temperature of the thrust ball bearing 384 of the hermetic compressor is operated at a temperature of 150° C. or higher for a certain period of time, the seat portion 388 rises to a temperature of 150° C. or higher. However, due to the heat resistance of the seat portion 388 , oil resistance, and excellent refrigerant resistance are formed to prevent oligomers from eluting from the seat portion 388 . That is, the thrust ball bearing 384 may be used for a certain period of time at an ambient temperature of 150° C. or higher, or a hermetic compressor equipped with the thrust ball bearing 384 may be operated at an ambient temperature of 150° C. or higher for a certain period of time.

By adopting such a method, it is possible to prevent problems such as a decrease in efficiency due to input loss, an increase in noise, and a decrease in reliability that are caused by deformation of the seat portion 388 .

In addition, in the second embodiment, the case where the continuous operation time is long or the operation load is large is described as an example in which the temperature of the thrust ball bearing 384 rises to a high temperature. However, other situations can be implemented similarly as long as the temperature of the thrust ball bearing 384 rises to a high temperature other than this situation, and oligomers can be prevented from being eluted from the seat portion 388 .

It goes without saying that even if a part of the outer side of the thrust ball bearing 384 is surrounded by a part of the cylinder 320, the same action and effect can be obtained.

It goes without saying that when the motor unit 308 is constituted by a motor using permanent magnets, it generates less heat than an induction motor, but the same operations and effects can be obtained.

Industrial availability

As described above, the hermetic compressor of the present invention utilizes a polymer formed by polycondensation of diaminobutane and adipic acid to form a seat portion, thereby providing a high-efficiency and highly reliable hermetic compressor that suppresses an increase in input. machine. Therefore, it can be applied to applications such as automatic vending machines, refrigerated showcases, and dehumidifiers including refrigerated appliances such as refrigerated refrigerators, and functions.

Claims (8)

1. hermetic type compressor, it is characterized in that, in seal container, store lubricant oil, and contain electrodynamic element that possesses stator and rotor and the compression unit that drives by described electrodynamic element, described compression unit comprises the axle with main shaft part and eccentric axial portion, form the working cylinder of pressing chamber, be formed on the described working cylinder and the main bearing of the described main shaft part of a described axle of supporting, pistons reciprocating in described pressing chamber, the connect mechanism and the thrust ball bearing that link described piston and described eccentric axial portion, described thrust ball bearing possesses a plurality of balls and keeps the seat portion of described ball, and described seat portion is formed by polymer.

2. hermetic type compressor according to claim 1 is characterized in that, described axle is at the fixing described rotor of described main shaft part hot charging, and described thrust ball bearing is arranged between described rotor and the described main shaft part.

3. hermetic type compressor according to claim 2 is characterized in that, at least a portion of described thrust ball bearing is configured in the countersink as recess of described rotor.

4. hermetic type compressor according to claim 1 is characterized in that, described beam warp forms described eccentric axial portion by described main shaft part and lip part, and described thrust ball bearing is configured between the upper-end surface of described lip part and described main bearing.

5. hermetic type compressor according to claim 4 is characterized in that at least a portion in the outside of described thrust ball bearing is surrounded by at least a portion of described working cylinder or described main bearing.

6. according to any described hermetic type compressor in the claim 1～5, it is characterized in that described electrodynamic element is an induction motor.

7. according to any described hermetic type compressor in the claim 1～5, it is characterized in that described seat portion is made of the member that has heated certain hour with the heating-up temperature more than 150 ℃.

8. according to any described hermetic type compressor in the claim 1～5, it is characterized in that described thrust ball bearing is a temperature running certain hour more than 150 ℃ with atmosphere temperature.

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