JP2010265830A - Hermetic compressor and refrigeration cycle equipment - Google Patents

Abstract

[PROBLEMS] To reduce the run-out of a rotating shaft with a long shaft length on the assumption that a plurality of compression mechanisms are provided, to improve compression efficiency, and to minimize lubricating oil leakage. Provided are a hermetic compressor that can be suppressed to the limit and improve the oil supply efficiency for the compression mechanism, and a refrigeration cycle apparatus that includes this hermetic compressor and can improve the refrigeration cycle efficiency.
A hermetic compressor A according to the present invention includes a hermetic container 1 provided with an oil reservoir T for lubricating oil at an inner bottom, a motor part 3 accommodated in the hermetic container, and the motor part and the rotation. 1st-3rd compression mechanism part 2A-2C connected via the axis | shaft 4, and the oil supply channel | path K which supplies lubricating oil of an oil reservoir part to each compression mechanism part with rotation of a rotating shaft are comprised. The rotary shaft is divided into a first divided rotary shaft 4A and a second divided rotary shaft 4B along the axial direction, and these divided rotary shafts are connected to each other by a rotary shaft connector 21. A partition cylinder 24 that partitions the muffler chamber M that guides the discharged refrigerant is provided around the tool.
[Selection] Figure 1

Description

  The present invention relates to a multi-cylinder type hermetic compressor having a plurality of compression mechanisms and a refrigeration cycle apparatus that constitutes a refrigeration cycle using the hermetic compressor.

  In recent years, a two-cylinder type hermetic compressor provided with two sets of the compression mechanism portions above and below is being standardized, which is advantageous in that the compression capacity can be increased as compared with a single-cylinder type compressor. In order to further increase the compression capacity, for example, [Patent Document 1] discloses a multi-cylinder type hermetic compressor in which three sets of compression mechanisms are connected in the axial direction.

  Naturally, the shaft length of the rotating shaft used in this type of compressor is longer than that of the rotating shaft used in the single-cylinder and two-cylinder type compressors. The lower end portion and the substantially intermediate portion of the rotating shaft are pivotally supported by bearings. One or more eccentric portions are integrally provided on the rotating shaft between the bearings, and an eccentric roller is fitted to each. There is no bearing.

  When the rotary shaft described above is driven to rotate, the rotary shaft portion between the bearings, which is not subject to the restriction of the bearing, is greatly curved and deformed. In particular, the eccentric roller fitted in the eccentric part in the middle part between the bearings has a larger runout compared to the eccentric roller in contact with the bearings on both side parts, and galling due to metal contact at the sliding part is likely to occur. The wear increases and the compression efficiency is substantially lowered or the reliability is lowered.

  Therefore, in the multi-cylinder type hermetic compressor, for example, the idea of setting the clearance of the compression mechanism portion not in contact with the bearing to be larger than the clearance of the compression mechanism portion in contact with the bearing has arisen. In this case, it is possible to prevent galling at the rotating shaft portion that is not in contact with the bearing, reduce wear, and minimize the decrease in compression efficiency.

JP-A-5-1686

  On the other hand, as a result of increasing the clearance, the average compression efficiency is reduced with respect to the single cylinder type compressor. In addition, since the dimensions of each part are determined with emphasis on assemblability, in which a plurality of eccentric rollers, partition plates, and the like are incorporated in the same order with respect to one rotating shaft, it is not always a perfect optimum design.

  By the way, in a general hermetic compressor, an oil reservoir for collecting lubricating oil is formed at the inner bottom of the hermetic container, and the lubricating oil is sucked up as the rotary shaft rotates. Lubricating oil is supplied to, for example, a sliding portion in each compression mechanism portion where the rotating shaft and the bearing are in contact via an oil supply passage provided in the rotating shaft.

On the other hand, the refrigerant gas compressed by each compression mechanism is once discharged into the sealed container, and after being filled inside, is led to a discharge refrigerant pipe connected to the sealed container. Therefore, the lubricating oil flowing out between the rotating shaft and the bearing is exposed to the compressed refrigerant gas filling the sealed container.
In other words, if the lubricating oil is mixed with the flow of the refrigerant gas and the lubricating oil leaks, the same phenomenon occurs. In combination with the long shaft length of the rotating shaft, insufficient lubrication due to leakage of lubricating oil cannot be ignored.

  The present invention has been made based on the above circumstances, and the object of the present invention is to reduce the whirling of the rotating shaft with a long shaft length on the assumption that a plurality of compression mechanism sections are provided, and to improve the compression efficiency. A hermetic compressor that can improve the lubrication efficiency of the compression mechanism by minimizing the leakage of the lubricating oil, and a refrigeration cycle comprising this hermetic compressor. An object of the present invention is to provide a refrigeration cycle apparatus capable of improving cycle efficiency.

In order to satisfy the above object, a hermetic compressor according to the present invention includes a hermetic container having an oil reservoir for collecting lubricating oil at an inner bottom, a motor part accommodated in the hermetic container, and the motor part. And a plurality of compression mechanism parts that are connected to each other via a rotation shaft and each compresses and discharges the refrigerant, and lubrication oil in an oil reservoir is supplied to the plurality of compression mechanism parts as the rotation shaft rotates. The rotary shaft is divided into a plurality of portions along the axial direction, and the divided rotary shafts are connected to each other by a connecting means, and compressed around the connecting means by a compression mechanism and discharged. Partitioning means for partitioning from the discharge refrigerant passage for guiding the refrigerant is provided.
In order to satisfy the above object, the refrigeration cycle apparatus of the present invention comprises the above-described hermetic compressor, a condenser, an expansion device, and an evaporator connected via a refrigerant pipe to constitute a refrigeration cycle.

According to the hermetic compressor of the present invention, it is possible to reduce the whirling of the rotary shaft with a long shaft length, to improve the compression efficiency, and to suppress the leakage of the lubricating oil to the minimum, so that the compression mechanism section The oil supply efficiency can be improved.
Moreover, according to the refrigeration cycle apparatus of the present invention, the above-described hermetic compressor is provided, and an improvement in refrigeration cycle efficiency can be obtained.

The partial longitudinal cross-sectional view and refrigeration cycle block diagram of a hermetic type compressor concerning a 1st embodiment in the present invention. The longitudinal cross-sectional view of the compression mechanism part based on the same embodiment, and the figure explaining the flow of lubricating oil and the compressed refrigerant gas. The cross-sectional top view of the compression mechanism part based on the embodiment. The longitudinal cross-sectional view of the compression mechanism part based on 2nd Embodiment in this invention, and the figure explaining the flow of lubricating oil and the compressed refrigerant gas. The figure explaining the assembly of the compression mechanism part based on the embodiment.

Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a refrigeration cycle configuration diagram of a refrigeration apparatus and a partial longitudinal sectional view showing an internal structure of a hermetic compressor A constituting the refrigeration cycle. In addition, the components which do not attach | subject the code | symbol in description are not shown in figure. Some parts are not illustrated even though they are shown. (Hereinafter the same)
First, the refrigeration cycle configuration of the refrigeration apparatus will be described.
A discharge refrigerant pipe P is connected to an upper end portion of the hermetic compressor A, and a condenser B, an expansion valve C as an expansion mechanism, an evaporator D, and an accumulator E are sequentially provided in the discharge refrigerant pipe P. . Three suction refrigerant tubes Pa, Pb, Pc are connected from the bottom of the accumulator E, and these suction refrigerant tubes Pa, Pb, Pc are connected to the side surface of the hermetic compressor A, and the refrigeration cycle is completed as described above. Composed.

Next, the hermetic compressor A will be described.
Reference numeral 1 denotes an airtight container, and a plurality of compression mechanism portions, here, a first compression mechanism portion 2A, a second compression mechanism portion 2B, and a third compression mechanism portion 2C are provided in a lower portion of the airtight container 1. Is provided. An electric motor unit 3 is provided on the upper portion of the first compression mechanism unit, and all of the electric motor unit 3 and the first to third compression mechanism units 2A to 2C are connected via a rotating shaft 4 described later.

  An oil reservoir T for collecting lubricating oil is provided at the inner bottom of the sealed container 1, and the second and third compression mechanisms 2B and 2C are immersed in the lubricating oil in the oil reservoir T, Almost most of the compression mechanism portion 2A of 1 is also immersed in the lubricating oil.

  The electric motor unit 3 includes a stator 5 that is fixed to the inner surface of the hermetic container 1 and a rotor 6 that is disposed inside the stator 5 with a predetermined gap and into which the rotating shaft 4 is inserted. Is done. The electric motor unit 3 is electrically connected to an inverter that varies the operation frequency and a control unit that controls the electric motor unit 3 via the power supply unit 3 a.

The first compression mechanism portion 2A and the second compression mechanism portion 2B are connected and integrated by mounting bolts, and can be used for a so-called two-cylinder (twin) type hermetic compressor. . The third compression mechanism portion 2C is configured by itself, and can be used for a so-called single-cylinder (single) type hermetic compressor.
Here, an assembly in which the first and second compression mechanism portions 2A and 2B are integrated and a single third compression mechanism portion 3C are connected by an intermediate connection body F to be described later to provide one compression mechanism. An assembly G is formed.

FIG. 2 is a longitudinal sectional view of the compression mechanism assembly G. As shown in FIG.
As shown in FIGS. 1 and 2, the rotating shaft 4 inserted into the rotor 6 of the electric motor unit 3 is inserted into the compression mechanism assembly G, and downward from the lower end of the third compression mechanism unit 2C. Protruding. Actually, the rotating shaft 4 is divided into a part that is inserted into the electric motor unit 3 and a part of the compression mechanism assembly G, and a part that is inserted into the remaining part of the compression mechanism assembly G.

  In other words, the rotating shaft 4 is inserted into the first divided rotating shaft 4A and the third compression mechanism 2C, which are inserted from the motor unit 3 into the first compression mechanism 2A and the second compression mechanism 2B. It consists of the 2nd division | segmentation rotating shaft 4B to fit. The end surfaces of the first divided rotating shaft 4A and the second divided rotating shaft 4B face each other with a narrow gap S inside the intermediate coupling body F.

  The first compression mechanism portion 2A and the second compression mechanism portion 2B are provided via an intermediate partition plate 7, and each includes a first cylinder 8A and a second cylinder 8B. That is, the first and second cylinders 8A and 8B are overlapped with each other via the intermediate partition plate 7, and are attached and fixed to each other by a plurality of mounting bolts.

  A main bearing 9 is mounted on the upper surface of the first cylinder 8A, and is fixed to the first cylinder 8A together with the valve cover a. The main bearing 9 is superposed on the first cylinder 8A and is provided with a flange portion 9a provided with a discharge valve mechanism 10a, and provided at the center of the flange portion 9a so as to pivotally support the first divided rotary shaft 4A. And the pivot portion 9b.

  The third compression mechanism portion 2C includes a third cylinder 8C, and a sub bearing 11 is provided on the lower surface. The auxiliary bearing 11 includes a flange portion 11a superimposed on the third cylinder 8C, and a pivotal support portion 11b that pivotally supports the second divided rotating shaft 4B at the center of the flange portion 11a.

The upper and lower surfaces of the first cylinder 8A are partitioned by the main bearing 9 and the intermediate partition plate 7, and a first cylinder chamber 12a is formed in the inner diameter portion. The upper and lower surfaces of the second cylinder 8B are partitioned by the intermediate partition plate 7 and the intermediate coupling body F, and a second cylinder chamber 12b is formed in the inner diameter portion.
The upper and lower surfaces of the third cylinder 8C are partitioned by the intermediate coupling body F and the auxiliary bearing 11, and a third cylinder chamber 12c is formed in the inner diameter portion. These first to third cylinder chambers 12a to 12c are formed to have the same diameter.

  4A of 1st division | segmentation rotating shafts and the 2nd division | segmentation rotating shaft 4B penetrate the 1st-3rd cylinder 8A-8C internal diameter part. Then, three eccentric portions 4a, 4b, 4c formed with a phase difference of approximately 120 ° in order from the top are integrally provided, and eccentric rollers 13a, 13b, 13c are fitted to the peripheral surfaces of these eccentric portions 4a-4c. Is done.

  In other words, two eccentric portions 4a and 4b are provided at a predetermined interval on the first divided rotating shaft 4A, and one eccentric portion 4c is provided on the second divided rotating shaft 4B. The eccentric roller 13a fitted to the eccentric part 4a is the first cylinder chamber 12a, the eccentric roller 13b fitted to the eccentric part 4b is the second cylinder chamber 12b, and the eccentric roller 13c fitted to the eccentric part 4c is the third cylinder. The cylinder chambers 12c are assembled so as to be positioned respectively.

FIG. 3 is a schematic cross-sectional view of the first compression mechanism portion 2A constituting the compression mechanism assembly G. Since the first compression mechanism 2A to the third compression mechanism 2C all have the same configuration, only the first compression mechanism 2A will be described here, and the second and third compression mechanisms 2B will be described. , 2C are numbered corresponding to the corresponding component parts, and description thereof is omitted.
The first cylinder 8A is provided with a blade chamber 15a communicating with the first cylinder chamber 12a. In the blade chamber 15a, the blade 16a is accommodated so as to protrude and retract with respect to the first cylinder chamber 12a.

  The blade chamber 15a includes a blade housing groove 17a in which both side surfaces of the blade 16a can move slidably, and a vertical hole portion that is integrally connected to an end portion of the blade housing groove 17a and accommodates a rear end portion of the blade 16a. 18a. A spring member 19 that is a compression spring is accommodated in the blade chamber 15a, and an elastic force (back pressure) is applied to the blade 16a.

  The tip edge of the blade 16a is formed in a semicircular shape in plan view, and receives the back pressure from the spring member 19, and the tip edge makes line contact with the peripheral wall of the eccentric roller 13a regardless of the rotation angle. When the eccentric roller 13a rotates eccentrically along the inner peripheral wall of the cylinder chamber 12a, the blade 16a reciprocates along the blade housing groove 17a, and its rear end can project and retract into the vertical hole 18a.

A semicircular discharge notch 20 is provided in the vicinity of the blade housing groove 17a in the first cylinder 8A, and this discharge notch 20 communicates with a discharge valve mechanism 10a provided in the flange portion 9a of the main bearing 9.
The semicircular discharge notch 20 provided in the vicinity of the blade storage groove 17b in the second cylinder 8B and the semicircular discharge notch 20 provided in the vicinity of the blade storage groove 17c in the third cylinder 8C are respectively intermediate. It communicates with the discharge valve mechanisms 10b, 10c provided on the connecting body F.

  A suction hole b is provided in a portion opposite to the discharge notch 20 through the blade housing groove 17a so as to penetrate from the outer peripheral surface of the first cylinder 8A to the cylinder chamber 12a which is the inner diameter portion. A suction refrigerant pipe Pa extending from the bottom of the accumulator E and penetrating the sealed container 1 is connected to the suction hole b.

As shown in FIG. 2 again, the first split rotary shaft 4A and the second split rotary shaft 4B constituting the rotary shaft 4 are rotated by a rotary shaft coupler (connecting means) 21 constituting the intermediate coupling body F. It is connected.
Therefore, if the first split rotation shaft 4A is driven to rotate by the motor unit 3, the first compression mechanism unit 2A and the second compression mechanism unit 2B are operated, and the second compression mechanism unit 2B is operated via the rotation shaft connector 21. The divided rotation shafts 4B are simultaneously driven to rotate, and the third compression mechanism 2C is simultaneously operated.

The intermediate coupling body F includes the rotary shaft coupling tool 21, the first intermediate bearing 22 </ b> A and the second intermediate bearing 22 </ b> B, a frame 23, and a partition cylinder (partitioning unit) 24.
First, the frame 23 will be described. The frame 23 is interposed between the respective peripheral ends of the second cylinder 8B and the third cylinder 8C, and a body portion provided with a hole through which the mounting bolt 25 is inserted. 23a, and a flange portion 23b that protrudes integrally in the circumferential direction at the upper end of the body portion 23a.

As shown in FIG. 1 again, the peripheral surface of the flange 23b of the frame 23 is closely fitted into the inner peripheral surface of the sealed container 1, and the frame 23 is sealed by means such as spot welding from the outer peripheral surface side of the sealed container 1. It is attached and fixed to the container 1.
The upper end of the frame 23 is in contact with the lower surface of the second cylinder 8B, the upper surface of the third cylinder 8C is in contact with the lower end of the frame 23, and after being aligned with each other, a mounting bolt 25 is inserted into the hole of the frame 23 and fastened. To do. Thus, the second cylinder 8B and the third cylinder 8C are integrally attached and fixed via the frame 23.

  As shown in FIGS. 1 and 2 again, the first intermediate bearing 22A is provided on the inner diameter side of the flange portion of the frame 23, and is attached and fixed to the intermediate partition plate 7 assembled in a twin type. The second intermediate bearing 22B is provided on the inner diameter side of the lower end portion of the frame 23, and is attached and fixed to the auxiliary bearing 11 with the third cylinder 8C interposed.

  The first and second intermediate bearings 22A and 22B are provided with the discharge valve mechanisms 10b and 10c, respectively. The discharge valve mechanism 10b of the first intermediate bearing 22A communicates with the discharge notch 20 provided in the second cylinder 8B, and the discharge valve mechanism 10c of the second intermediate bearing 22B discharges provided in the third cylinder 8C. It communicates with the notch 20.

  The first split rotary shaft 4A is pivotally supported by the first intermediate bearing 22A, and the second split rotary shaft 4B is pivotally supported by the second intermediate bearing 22B. The lower end portion of the split rotary shaft 4B pivotally supported by the second intermediate bearing 22B protrudes from the intermediate bearing 22B. A narrow gap S between the first divided rotating shaft 4A and the second divided rotating shaft 4B is formed at a substantially intermediate portion between the first intermediate bearing 22A and the second intermediate bearing 22B.

  The rotating shaft coupler 21 is a ball joint in which a rolling member 21c such as a ball is interposed between the inner ring portion 21a, the outer ring portion 21b, and the inner ring portion 21a and the outer ring portion 21b. Actually, the inner ring portion 21a of the rotating shaft coupling tool 21 is fitted to the first and second divided rotating shafts 4A and 4B, and there is no mating partner in the outer ring portion 21b.

  The partition cylinder 24 is provided over the respective peripheral surfaces of the first intermediate bearing 22A and the second intermediate bearing 22B. As a result, the partition cylinder 24 covers the rotary shaft connector 21 with a gap. A seal member h made of, for example, an O-ring is interposed between the partition cylinder 24 and the peripheral surface of the first intermediate bearing 22A and between the peripheral surface of the second intermediate bearing 22B. Thus, the inside of the partition cylinder 24 is sealed.

  Thus, the rotary shaft 4 divided along the central axis of the intermediate coupling body F is inserted, and the rotary shaft coupling tool 21 couples the divided rotary shafts 4A and 4B. A partition cylinder 24 is provided along with a seal member h on the periphery of the rotary shaft connector 21 with a gap therebetween, and seals the rotary shaft connector 21 inside and the divided rotary shaft 4.

On the other hand, gas extends over the first intermediate bearing 22A, the second cylinder 8B, the intermediate partition plate 7, the first cylinder 8A, and the flange portion 9a of the main bearing 9 constituting the intermediate coupling F. A guide hole 27 is provided in communication.
Accordingly, the space surrounded by the partition cylinder 24 of the intermediate coupling body F, the frame 23, and the flange portions of the first intermediate bearing 22A and the second intermediate bearing 22B, and the valve cover attached to the main bearing 9 a communicates with the inside through the gas guide hole 27. Hereinafter, the space surrounded by the partition cylinder 24, the frame 23, and the first and second intermediate bearings 22A and 22B is referred to as a “muffler chamber” M.

  An oil supply passage K is provided in the first and second divided rotary shafts 4A and 4B. That is, one end portion of the oil supply hole 28 is opened at the lower end surface of the second divided rotation shaft 4B on the lower side. The oil supply hole 28 is provided along the axial direction of the second split rotary shaft 4B, and is provided along the axial direction of the first split rotary shaft 4A.

  The upper end position of the oil supply hole 28 in the first divided rotating shaft 4A is set at a portion beyond the upper end of the pivot 9b of the main bearing 9. An oil supply pump is provided at the lower end of the oil supply hole 28 at the lower end of the second divided rotary shaft 4B, and the lubricating oil in the oil reservoir T is pumped into the oil supply hole 28 as the second divided rotary shaft 4B rotates. ing.

  A plurality of lateral oil holes 29 are provided across the middle portion of the oil supply hole 28 and the outer peripheral surfaces of the first and second divided rotary shafts 4A and 4B. In other words, the portion where the lateral oil hole 29 is provided includes the portion communicating with the sub-bearing 11, the portion communicating with the second intermediate bearing 22B, the portion communicating with the first intermediate bearing 22A, and the main bearing 9. This is the part that communicates.

  The lubricating oil pumped up from the oil reservoir T by the oil pump is guided along the oil supply holes 28, and from the respective lateral oil holes 29, the auxiliary bearing 11, the second intermediate bearing 22B, the first intermediate bearing 22A, the main oil Oil is supplied to the bearings 9, and oil is supplied to the sliding portions where the peripheral surface of the pivot hole of these bearings and the peripheral surfaces of the divided rotary shafts 4A and 4B are in contact.

  Lubricating oil supplied to the sliding portion between the first split rotary shaft 4A and the first intermediate bearing 22A is formed in the space between the rotary shaft coupler 21 and the partition cylinder 24 that constitute the intermediate coupler F. And the lubricating oil supplied to the sliding portion between the second split rotary shaft 4B and the second intermediate bearing 22B collects. The space between the rotary shaft connector 21 and the partition cylinder 24 is referred to as a “lubricating oil chamber” N.

Next, the operation of the multi-cylinder type hermetic compressor A configured as described above will be described.
When an operation start signal is input to the control unit from a remote controller (remote control panel) (not shown), the control unit sends an operation signal to the electric motor unit 3 through the inverter, and the rotary shaft 4 is rotationally driven. Specifically, the first divided rotating shaft 4A provided in the electric motor unit 3 is rotationally driven, and the second divided rotating shaft 4B connected to the first divided rotating shaft 4A via the rotating shaft connector 21 is integrated. Is driven to rotate.

  The eccentric portions 4a to 4c are rotationally driven together with the first and second divided rotating shafts 4A and 4B, and the eccentric rollers 13a to 13c rotate eccentrically in the cylinder chambers 12a to 12c. The blades 16a to 16c to which the back pressure is applied by the spring member 19 slidably contact the peripheral walls of the eccentric rollers 13a to 13c and divide the first to third cylinder chambers 12a to 12c into suction chambers and compression chambers. .

  The cylinder chambers 12a to 12c have the largest space capacity in a state in which the inner circumferential surface rolling contact positions of the eccentric rollers 13a to 13c coincide with the blade housing grooves 17a to 17c and the blades 16a to 16c are retracted most. Become. The refrigerant gas is sucked into the cylinder chambers 12a to 12c from the accumulator E through the refrigerant suction pipes Pa to Pc and is filled.

  As the eccentric rollers 13a to 13c rotate eccentrically, the rolling contact position with respect to the inner peripheral surfaces of the cylinder chambers 12a to 12c moves, and the volume of the compression chamber partitioned by the cylinder chambers decreases, so that the gas introduced earlier gradually Compressed. The rotating shaft 4 is continuously rotated, the compression chamber capacity of each of the cylinder chambers 12a to 12c is further reduced, and the pressure of the compressed refrigerant gas is increased.

  When the gas pressure rises to a predetermined pressure and increases, the discharge valve mechanisms 10a to 10c provided in the bearings 9, 22A and 22B are opened. As indicated by broken line arrows in FIG. 2, the refrigerant gas compressed in the first cylinder chamber 12a and discharged from the discharge valve mechanism 10a directly fills the valve cover a.

  The refrigerant gas compressed in the second cylinder chamber 12b and discharged from the discharge valve mechanism 10b of the first intermediate bearing 22A fills the muffler chamber M between the frame 23 and the partition cylinder 24 of the intermediate coupling body F. . At the same time, the muffler chamber M is also filled with the refrigerant gas compressed in the third cylinder chamber 12c and discharged from the discharge valve mechanism 10c of the second intermediate bearing 22B.

  The refrigerant gas filled in the muffler chamber M is guided into the valve cover a through the gas guide hole 27 and merges with the refrigerant gas compressed in the first cylinder chamber 12a. After that, since it comes out from the discharge hole a1 of the valve cover a and fills the sealed container 1, the refrigerant gas is completely silenced when discharged from the respective cylinder chambers 12a to 12c.

  The high-pressure refrigerant gas is led out to the discharge refrigerant pipe P connected to the hermetic container 1, led to the condenser B, condensed, led to the expansion valve C, adiabatically expanded, and led to the evaporator D. Evaporate. At this time, heat is exchanged with the air led to the evaporator D to take away latent heat of vaporization, and after the refrigeration action, it is led to the accumulator E to be gas-liquid separated.

The low-pressure evaporative refrigerant separated from the gas and liquid by the accumulator E is led out and is compressed by being led to the first to third cylinder chambers 12a to 12c via the suction refrigerant pipes Pa to Pc. Then, the above route is circulated again.
Eventually, in the multi-cylinder type hermetic compressor A, the three cylinder chambers 12a to 12c, which are the first cylinder chamber 12a, the second cylinder chamber 12b, and the third cylinder chamber 12c, are all together. At the same time, since the compression action is performed, the compression capacity can be increased.

  In addition, as the first and second split rotary shafts 4A and 4B rotate, the oil pump provided in the oil feed hole 28 of the second split rotary shaft 4B causes lubricating oil from the oil reservoir T at the inner bottom portion of the hermetic container 1. Suck up. The sucked lubricating oil is guided along the oil supply passage K as indicated by solid line arrows in FIG.

  Lubricating oil is led from the oil supply passage K to the sliding portions of the respective divided rotary shafts 4A, 4B and the bearings 9, 22A, 22B, 11, etc., and ensures their lubricity. Then, they are also guided to sliding portions with eccentric rollers 13a to 3c rotating eccentrically in the cylinder chambers 12a to 12c and sliding portions with blades 16a to 16c reciprocatingly moving in the blade chambers 15a to 15c. Guarantee sex.

  In particular, the lubricating oil introduced to the sliding portion between the first intermediate bearing 22A and the first split rotating shaft 4A and the sliding portion between the second intermediate bearing 22B and the second split rotating shaft 4B are guided. The lubricating oil thus collected accumulates in the lubricating oil chamber N between the rotary shaft connector 21 and the partition cylinder 22, and returns to the oil reservoir T as time passes.

  The lubricating oil chamber N is partitioned from the muffler chamber M by the partition cylinder 22 so that the lubricating oil in the lubricating oil chamber N is not exposed to the high-pressure refrigerant gas that fills the muffler chamber M. Since the lubricating oil and the refrigerant gas are completely separated inside the intermediate coupling body F, it is possible to prevent the lubricating oil from being mixed in the flow of the refrigerant gas.

  Therefore, most of the lubricating oil sucked up from the oil reservoir T and supplied to each sliding portion via the oil supply passage K surely and smoothly returns to the oil reservoir T, and again passes through the oil supply passage K. Oil is supplied to each sliding part. A sufficient amount of lubricating oil is always supplied to each sliding portion, so that these lubricating properties are guaranteed.

Since the rotary shaft 4 is divided into the first split rotary shaft 4A and the second split rotary shaft 4B, the shaft length of the rotary shaft 4 is longer than that of a single cylinder or two cylinder type compressor. Long formed. If the lubricating oil supplied to each sliding part leaks in the middle of returning to the oil reservoir T, a sufficient amount of lubricating oil may be supplied to the sliding part of the first divided rotating shaft 4A, which is the upper part in particular. Can not.
In that respect, by adopting the structure of the present embodiment, it is possible to guarantee lubricity and improve reliability.

  Further, the rotating shaft 4 provided across the electric motor unit 3 and the first to third compression mechanism units 2A to 2C is divided into a first divided rotating shaft 4A and a second divided rotating shaft 4B. However, these divided rotary shafts 4A and 4B are connected to the electric motor unit 3 so as to be able to rotate synchronously by the rotary shaft connector 21, and there is no disadvantageous structure.

  The compression mechanism portions 2A to 2C are integrally attached and fixed by an attachment fixture 25 such as a bolt via the frame 23 constituting the intermediate coupling body F. Therefore, an assembly in which the first compression mechanism portion 2A and the second compression mechanism portion 2B are integrated and a compression mechanism assembly G in which the third compression mechanism portion 2C is fixed can be configured. It is possible to provide a hermetic compressor A that can sufficiently withstand a torsional moment and a drop impact caused by the above.

  Since the frame 23 constituting the intermediate coupling body F is attached and fixed to the sealed container 1 and the first to third compression mechanism portions 2A to 2C and the sealed container 1 are fixed via the frame 23, the first to first It is not necessary to attach the three compression mechanism portions 2A to 2C to the sealed container 1. The deformation | transformation accompanying the welding with respect to the airtight container 1 of the 1st-3rd compression mechanism parts 2A-2C can be prevented.

  Since the space part surrounded by the inner peripheral part of the frame 23 constituting the intermediate coupling body F and the second compression mechanism part 2B and the third compression mechanism part 2C is the muffler chamber M, the volume of the muffler chamber M is reduced. In addition to being able to be increased, the sound insulation is improved and the noise can be reduced.

  In the present embodiment, the first split rotary shaft 4A and the second split rotary shaft 4B are attached and fixed to the rotary shaft coupler 21 by press fitting. In addition, depending on productivity conditions, press-fitting and other methods, for example, shrink fitting, screwing, keying, adhesive, etc. can be used together, or shrink fitting can be fixed alone.

  In any case, in order to insert and fix the split rotary shafts 4A and 4B to the rotary shaft coupler 21, it is necessary to push the first split rotary shaft 4A and the second split rotary shaft 4B in the thrust load direction. Become. Further, during the compression operation, it is necessary to provide a thrust bearing function for supporting the thrust load of each of the divided rotary shafts 4A and 4B.

In the present embodiment, the first and second compression mechanism portions 2A and 2B are integrated via the intermediate partition plate 7 and the assembly of the compression mechanism portion and the third compression mechanism portion 2C are connected. The first intermediate bearing 22A and the auxiliary bearing 11 support the thrust load.
According to such a configuration, since the thrust load can be evenly distributed to both compression mechanism components without having a thrust load at one place, a highly reliable thrust bearing can be provided without using expensive materials. .

  In other words, the thrust load is supported by a bearing located at the lowermost end of the first and second compression mechanism portions 2A and 2B and a bearing located at the lowermost end of the third compression mechanism portion 2C. That is, the first intermediate bearing 22A and the sub-bearing 11 are applicable, and therefore, at least the lower end surface of the second eccentric portion 4b and the lower end surface of the third eccentric portion 4c are polished.

  Moreover, in the operation | work which connects 4 A of 1st division | segmentation rotating shafts and the 2nd division | segmentation rotating shaft 4B via the rotating shaft coupling tool 21, the lower end surface of the 2nd eccentric part 4b, and the bottom of the 3rd eccentric part 4c The gap S is provided in order to make the end faces evenly contact the first intermediate bearing 22A and the auxiliary bearing 11 and to avoid collision between the shafts.

  Further, in the present embodiment, a so-called twin type compression mechanism portion is used in which the first compression mechanism portion 2A and the second compression mechanism portion 2B are assembled together via the intermediate partition plate 7. Therefore, the inner diameter hole of the intermediate partition plate 7 has a large diameter in order to smoothly incorporate the eccentric portion 4a and the eccentric roller 13a of the first split rotation shaft 4A.

  For this reason, if it is made the structure which receives a thrust load with the intermediate partition board 7, a sliding area will be small and wear will advance easily. Therefore, in the present embodiment, the intermediate partition plate 7 is not subjected to a thrust load, and the thrust receiving structure is provided in the first intermediate bearing 22A, which is the lowermost bearing, so that the thrust receiving area is sufficiently secured and reliable. We are trying to improve.

  FIG. 4 is a longitudinal sectional view of the compression mechanism assembly Ga in the second embodiment, and FIG. 5 is a view for explaining the assembly of the compression mechanism assembly Ga. Note that the same parts as those in the first embodiment are denoted by the same reference numerals, and a new description is omitted.

  The compression mechanism assembly Ga fixes the first compression mechanism portion 2A and the second compression mechanism portion 2B via the intermediate partition plate 7, and includes a first bearing 9 and a first intermediate bearing 22Aa. The assembly Q1, and the second assembly Q2 provided with the second intermediate bearing 22Ba and the auxiliary bearing 11 in the third compression mechanism portion 2C are connected via a frame 23A.

  Here, the intermediate coupling body Fa includes a frame 23A, a first intermediate bearing 22Aa, a second intermediate bearing 22Ba, and a rotary shaft coupling tool 21. In particular, the partition means (partition cylinder 22) is not provided as a single component, and the second intermediate bearing 22Ba is also used.

  The frame 23A is provided with a body portion 23a1 provided with a hole through which the mounting bolt 25 is inserted, and an upper end of the body portion 23a1 projecting integrally in the circumferential direction, and the peripheral surface is fitted and fixed to the inner peripheral surface of the sealed container 1. The flange portion 23b is provided. Although the basic structure is not changed, the axial length of the body portion 23a1 is shortened from that used in the first embodiment for the reason described later.

  The first intermediate bearing 22Aa includes a flange portion where the second discharge valve mechanism 10b is provided, and a pivotal support portion that pivotally supports a part of the first split rotation shaft 4A. Here, as described in the first embodiment, since it is not necessary to attach the partition cylinder 24 to the pivotal support portion, the pivotal support portion is the minimum axial direction necessary to pivotally support the first divided rotating shaft 4A. It only has to be long.

  The second intermediate bearing 22Ba includes a flange portion where the discharge valve mechanism 10c is provided and a pivot portion that pivotally supports the second divided rotation shaft 4B via the rotation shaft connector 21. Therefore, the axial length of the pivotal support portion in the second intermediate bearing 22Ba needs to be at least long enough to accommodate the rotary shaft connector 21.

  The rotary shaft connector 21 is composed of, for example, a ball joint in which an inner ring portion 21a, an outer ring portion 21b, and a rolling member 21c such as a ball are interposed between the inner ring portion 21a and the outer ring portion 21b. Substantially, the inner ring portion 21a constituting the rotary shaft coupling tool 21 fits and fixes the first split rotary shaft 4A and the second split rotary shaft 4B.

  The outer ring portion 21b of the rotary shaft connector 21 is fitted into an inner diameter hole provided in the pivotal support portion of the second intermediate bearing 22Ba. Therefore, the outer ring portion 21b is fixed, and the first divided rotation shaft 4A and the second divided rotation shaft 4B, which are inner ring portions, are freely rotatable via a rolling member 21c such as a ball.

  A seal member h such as an O-ring is attached to the upper end surface of the second intermediate bearing 22Ba, and the first seal member Q1 and the second assembly Q2 are assembled, and the seal member h is the first, The space between the second intermediate bearings 22Aa and 22Ba is sealed. The gas guide hole 27 described above is provided, and the oil supply passage K is provided in the first and second divided rotary shafts 4A and 4B.

  Accordingly, a space portion surrounded by the flange portion and the pivot portion of the second intermediate bearing 22Ba, the flange portion of the first intermediate bearing 22Aa, and the inner peripheral surface of the frame 23A is the muffler chamber Ma. A seal member h provided on the second intermediate bearing 22Ba seals between the first intermediate bearing Aa and seals between the muffler chamber Ma and the oil supply passage K.

  The second intermediate bearing 22Ba provided with the seal member h also serves as a partitioning means, and a gap portion where the rolling member 21c is provided between the inner ring portion 21a and the outer ring portion 21b of the rotary shaft connector 21 is provided. It becomes lubricating oil chamber Na.

  The compression mechanism assembly Ga configured as described above is functionally the same as that described in the first embodiment, and a new description is omitted here. Since the three compression mechanism portions 2A to 2C are provided along the rotation shaft 4, the axial length of the rotation shaft 4 is inevitably increased.

  However, in this embodiment, the axial length of the first intermediate bearing 22Aa is set to the minimum necessary length, and the first intermediate bearing 22Aa is attached in close contact with the second intermediate bearing 22Ba, and the gap between them is eliminated. The rotary shaft connector 21 is provided at the pivotal support portion of the second intermediate bearing 22Ba, so that the axial length of the rotary shaft connector 21 alone is unnecessary.

  Therefore, the axial length of the intermediate coupling body Fa can be shortened, which leads to the shortening of the axial length of the compression mechanism assembly Ga and the shortening of the axial length of the hermetic compressor A. be able to.

  The discharge valve mechanism 10b of the first intermediate bearing 22Aa and the discharge valve mechanism 10c of the second intermediate bearing 22Ba are provided to face each other, the muffler chamber Ma formed between them, and the inner ring of the rotary shaft connector 21 Since the lubricating oil chamber Na formed between the portion 21a and the outer ring portion 21b is partitioned by the seal member h provided in the pivotal support portion of the second intermediate bearing 22Ba, the effect of restricting the leakage of the lubricating oil Is also definitely obtained.

  Note that, for example, a ball is used as the rolling member 21c between the inner ring portion 21a and the outer ring portion 21b constituting the rotary shaft connector 21, but the present invention is not limited to this, and other rolling elements such as rollers are used. A moving member can be applied. In short, a rolling bearing may be used as the rotary shaft connector 21.

  Further, the present invention is not limited to the above-described embodiments as they are, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. Various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the above-described embodiments.

  T ... Oil reservoir, 1 ... Sealed container, 3 ... Electric motor, 4 ... Rotating shaft, 2A ... First compression mechanism, 2B ... Second compression mechanism, 2C ... Third compression mechanism, K ... Oil supply passage, A ... Sealed compressor, 21 ... Rotating shaft connector (connecting means), 24 ... Partition cylinder (partitioning means), 23 ... Frame, M ... Muffler chamber, 21a ... Inner ring portion, 21b ... Outer ring portion, 21c ... rolling member, B ... condenser, C ... expansion valve (expansion mechanism), D ... evaporator.

Claims (6)

A sealed container having an oil reservoir for collecting lubricating oil at the inner bottom;
An electric motor unit housed in the hermetic container, and a plurality of compression mechanism units that are connected to the electric motor unit via a rotating shaft, and each compresses and discharges the refrigerant;
An oil supply passage provided in the rotating shaft, for supplying lubricating oil in the oil reservoir to the plurality of compression mechanisms as the rotating shaft rotates;
In a hermetic compressor provided with
The rotating shaft is divided into a plurality along the axial direction, and these divided rotating shafts are connected to each other by connecting means,
A hermetic compressor characterized in that a partition means for partitioning from a discharge refrigerant passage for guiding a refrigerant compressed by the compression mechanism section and discharged from the compression mechanism section is provided around the connecting means. The connecting means connects the rotating shaft divided into a plurality of parts so as to be able to rotate synchronously with the electric motor part,
The frame is sandwiched between the plurality of compression mechanism portions, and the plurality of compression mechanism portions and the frame are integrally attached and fixed by a mounting fixture such as a bolt. Hermetic compressor. 3. The hermetic compressor according to claim 2, wherein the frame is attached and fixed to the sealed container, and the plurality of compression mechanisms and the sealed container are fixed via the frame. The hermetic compressor according to claim 2, wherein a muffler chamber is provided between the frame and the compression mechanism. The connecting means includes a rolling bearing having a rolling member interposed between the inner ring portion and the outer ring portion, and a bearing tool in which the outer ring portion of the rolling bearing is inserted and accommodates the rolling bearing,
The end of the split rotary shaft is fitted to the inner ring portion of the rolling bearing,
The hermetic compressor according to any one of claims 1 to 4, wherein the bearing tool also serves as the partition means.   A hermetic compressor according to any one of claims 1 to 5, a condenser, an expansion device, and an evaporator are connected via a refrigerant pipe to constitute a refrigeration cycle. Refrigeration cycle equipment.

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