JP3019770B2 - Scroll gas compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive shaft of a scroll gas compressor and an oil supply passage.

[0002]

2. Description of the Related Art In a scroll compressor having low vibration and low noise characteristics, a suction chamber is provided at the outer periphery of a spiral compression chamber formed by a combination of a fixed scroll and an orbiting scroll.
A discharge port is provided at the center of the spiral, and the flow of the compressed fluid is unidirectional, eliminating the need for a discharge valve to compress the fluid, such as a reciprocating compressor or rotary compressor. If there is no large fluctuation in the operating compression ratio determined by the formula, the discharge pulsation is small and a large discharge space is required by setting the volume ratio determined by the suction volume of the compression chamber and the final compression chamber volume to an appropriate value. Therefore, research on practical application of utilization development in various fields has been conducted.

However, since there are many seal portions in the compression chamber, there is a lot of leakage of the compressed fluid. Particularly, in the case of a scroll gas compressor having a small displacement capacity such as a refrigerant compressor for home air conditioning,
In order to reduce the leakage gap of the compression part, it is necessary to make the dimensional accuracy of the spiral part extremely high.

However, due to the complexity of the component shape, the cost of the scroll gas compressor is high due to variations in the dimensional accuracy of the spiral portion and the like, and the performance of the scroll gas compressor is also large. Has a disadvantage that the gas leakage rate is high and the compression efficiency is lower than that of a reciprocating compressor or a rotary compressor.

Therefore, as measures for solving this type of problem, in order to prevent gas leakage during compression, the accuracy of the combination of the spiral portions of the two scrolls, the setting of the eccentricity of the crank mechanism of the drive shaft, and the optimization of the bearing clearance are set. As described in Japanese Patent Application Laid-Open No. 57-8386, an appropriate amount of lubricating oil is injected into a compression chamber in the course of compression, and the compression is performed by an oil film sealing action using the lubricating oil. Means for improving the compression efficiency by the chamber gap sealing effect have been proposed.

In particular, scroll refrigerant compressors have been put into practical use in the field of refrigeration and air conditioning, and various types of medium to large class compressors, such as packaged air conditioners and chiller units, having a relatively large refrigerant volume per one suction stroke have been developed. Improvements have been made and mass production has already been realized.

FIG. 14 shows a general structure example of a medium to large class scroll refrigerant compressor having a high-pressure space inside a closed case (chamber). In the figure, the compression unit and the discharge chamber 1031 are at the top, the motor (electric element) is at the bottom,
An oil sump is provided at the bottom at the discharge pipe 104 which is the final outlet of the compressor.
2 is disposed in the vicinity of the motor (electric element), and after the discharge refrigerant gas and the lubricating oil are separated in the discharge chamber 1031, the lubricating oil is stored in the motor (electric element) through oil drain holes 1035 and 1036. Returning to the space, the refrigerant gas is collected in the oil reservoir at the bottom, and the discharged refrigerant gas is discharged from the discharge pipe 1042 again after passing through the space accommodating the motor (electric element) from the upper part of the discharge chamber 1031 through another passage. You. In addition, in order to reduce the axial gap of the compression chamber, lubricating oil on which the discharge pressure acts on the bottom of the closed case (chamber) 1013 is provided inside a drive shaft (crankshaft) 1008 with an oil-lifting hole 1019 and a drive shaft ( Crankshaft) 1
After lubricating the bearing sliding surface through the clearance of the bearing of the body frame (frame) 1009 supporting the 008 and fixing the fixed scroll 1003, and the clearance of the crankshaft of the drive shaft (crankshaft) 1008, the orbiting scroll 1
006, the entire amount of the intermediate-pressure lubricating oil reduced in the middle of the path flows into the back-pressure chamber 1025, and the intermediate-pressure lubricating oil and the high-pressure lubricating oil above the crankshaft form the orbiting scroll 1006. Energize the back. As a result, the back pressure biasing force is set so as not to separate the orbiting scroll 1006 from the fixed scroll against the compression chamber gas pressure.

The total amount of the lubricating oil in the back pressure chamber 1025 is stored in the back pressure hole 1 provided in the end plate 1004 of the orbiting scroll 1006.
After flowing into the compression chamber 1015 in the middle of compression via 017,
The gas is compressed and discharged together with the suctioned refrigerant gas while sealing the gap of the compression chamber 1015, and discharged to the discharge chamber 1031. The shape of the drive shaft (crankshaft) 1008 is such that the outer diameter of the tip of the drive shaft as disclosed in JP-A-59-60092 is increased, and the orbiting scroll is formed in an eccentric hole provided in the portion. This is different from the embodiment in which the shaft portions of the drive shaft (crankshaft) 1008 are provided with a crankshaft portion at the tip of the drive shaft (crankshaft) 1008.
008 is designed to reduce the bearing sliding resistance by reducing the diameter of the bearing portion supporting the 008. (JP-A-56-165788).

[0009]

However, the configuration as shown in FIG. 14 has the following two problems.

The first problem is that the lubricating oil supply passage through which all the lubricating oil supplied to the sliding surface of the crankshaft (crank pin portion) on which all of the compressive load acts flows into the compression chamber 1015 causes a problem in the crankshaft. If sufficient lubricating oil is supplied to the sliding surface of the (crank pin portion), an excessive increase in input due to oil compression in the compression chamber 1015 is caused. On the other hand, contradiction arises that if an attempt is made to achieve an appropriate amount of injection into the compression chamber 1015 in order to avoid an excessive increase in input, there is a shortage of lubrication to the sliding surface of the crankshaft (crankpin portion).

The second problem is that the drive shaft (crankshaft) cannot be easily attached or detached after the compression section has been temporarily assembled, and it takes time to select an optimal eccentric amount of the drive shaft (crankshaft).

That is, the outer diameter of the bearing portion of the drive shaft (crankshaft) 1008 supported by the frame 1009 is
Since the diameter of the rotation locus of the outer peripheral surface of the upper crankshaft (crankpin portion) is smaller, the drive shaft (crankshaft) 1008 is
It is a structure that cannot be detached because it is inhibited by 9. As a result, in order to reduce the leakage of the compressed refrigerant gas, the orbiting scroll 1006 and the fixed scroll 1, for which it is difficult to ensure the dimensional accuracy of the spiral part, are difficult.
In order to minimize the radial gap between the compression chamber 1015 and the compression chamber 1015, an appropriate eccentricity of the crankshaft (crankpin portion) of the drive shaft (crankshaft) 1008 in accordance with the combination of the components of the orbiting scroll 1006 and the fixed scroll 1003. You need to set the amount.

For this purpose, it is necessary to confirm the replacement of the drive shaft (crankshaft) 1008 by replacement. As a result, each time the drive shaft (crankshaft) 1008 is replaced, the frame 1009 and the fixed scroll 10 are replaced.
However, there is a problem that the time required for selecting the amount of eccentricity of the drive shaft (crankshaft) becomes long, and the assembly cost becomes extremely high.

The present invention simultaneously solves the above-mentioned conventional problems. A scroll gas compressor provided with a drive shaft which can be easily replaced / removed at the time of assembling, a bearing structure related thereto, and an oil supply passage to the bearing is provided. The purpose is to provide.

[0015]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a crankshaft provided at the tip of a drive shaft so that the drive shaft engages with a swivel bearing of the orbiting scroll. The diameter of the rotation trajectory with respect to the main shaft is set to be equal to or less than the bearing inner diameter of the main bearing that supports the drive shaft, and the drive shaft has a dimension and shape that can be sequentially inserted into the main bearing and the slewing bearing from the motor side, An upper bearing that supports the drive shaft together with the main body frame on the side opposite to the compression chamber of the motor and the main body frame regulate the range in which the drive shaft moves in the axial direction.

According to the dimensions and shape of the crankshaft and the arrangement of the body frame and the upper bearing for supporting the drive shaft,
The drive shaft can be removed and replaced without changing the assembly state of the fixed scroll, orbiting scroll, and main bearing, and the drive shaft suitable for the dimensions of the fixed scroll, orbiting scroll, and main bearing is selected and assembled, and the radial direction of the compression chamber is minute. It is possible to simultaneously improve the compression efficiency by securing the gap, and improve the noise, vibration and durability of the compressor.

[0017]

According to the first aspect of the present invention, the crankshaft provided at the tip of the drive shaft so that the drive shaft engages with the slewing bearing has a diameter of a rotation locus of an outer peripheral surface of the drive shaft with respect to a main shaft of the drive shaft. In a configuration in which the drive shaft is set to be equal to or smaller than the bearing inner diameter of the main bearing, and the drive shaft is dimensioned so that it can be sequentially inserted into the main bearing and the slewing bearing from the motor side, the drive shaft together with the main body frame is located on the non-compression chamber side of the motor. the upper bearing for supporting arranged in a sealed case, and the range in which the drive shaft is moved in the axial direction, which is constituted so as to regulated by the main frame and the upper bearing. According to this configuration, the drive shaft can be detached and replaced without changing the assembly state of the fixed scroll, the orbiting scroll, and the main bearing, and the drive shaft suitable for the dimensions of the fixed scroll, the orbiting scroll, and the main bearing can be selectively assembled. In addition to micro-assembly of the radial gap in the compression chamber to reduce gas leakage during compression and to restrict the free axial movement of the drive shaft, it prevents axial vibration of the drive system and the accompanying noise. , And the durability of the sliding portion of the drive shaft can be improved at the same time.

According to a second aspect of the present invention, the balance weight of the drive shaft system disposed at the end of the rotor of the motor regulates the axial movement range of the drive shaft. According to this configuration, the axial vibration of the drive shaft system during the operation of the compressor can be prevented by simple means.

According to a third aspect of the present invention, at least the main body frame, the drive shaft, the motor, and the upper bearing are arranged in the high-pressure space of the closed case, and the lubrication is separated from the discharge gas discharged from the discharge port to the high-pressure space in the closed case. After collecting the oil in the discharge chamber sump, the total amount of lubricating oil
While most of the lubricating oil is returned to the discharge chamber oil sump,
Oil supply means is provided for reducing the pressure of the remaining lubricating oil and supplying it to one of the compression chamber and the suction chamber. According to this configuration, it is possible to simultaneously achieve oil film sealing of the compression chamber gap by proper lubrication to the compression chamber (suction chamber) and to improve durability by sufficient lubrication to the main bearing and the slewing bearing. In particular, the durability of the slewing bearing smaller in diameter than the main bearing can be easily secured.

According to a fourth aspect of the present invention, the drive shaft is on the compression chamber side.
As a means to restrict movement to the
The balance weights on the side of the
Formed to be supported by thrust bearings located at the side ends
At the same time, after lubricating the main bearing, return it to
A thrust bearing portion is provided as a lubricating passage just before the lubrication passage . According to this configuration, the axial vibration of the drive shaft caused by the change in the lubrication state due to the variable speed operation of the compressor to the bearing portion supporting the drive shaft is prevented by the simple means of the lubricating oil film, and the bearing durability is improved. Can also be improved at the same time. In addition, the thrust bearing is the final lubrication passage.
The lubricating oil that has deteriorated due to temperature rise due to sliding heat
The lubricating oil film is not directly supplied to the next sliding part.
The effect of use can be maintained.

[0021]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A scroll refrigerant compressor according to an embodiment of the present invention will be described below with reference to the drawings.

In FIG. 1, reference numeral 801 denotes a closed case made of iron. The inside of the case 801 is bolted to a fixed scroll 815 forming a compression chamber by meshing with an orbiting scroll 818, and an upper frame 805 is supported by a main body frame 805 supporting a drive shaft 704. Motor room 806 and lower accumulator room 846
And is divided into.

The motor chamber 846 is in a high-pressure atmosphere. A motor 703 is provided at an upper part, and a compression part is provided at a lower part. A main body frame 805 supporting a drive shaft 704 to which a rotor 703a of the motor 703 is connected and fixed has a sliding characteristic and a welding characteristic. Made of eutectic graphite cast iron having excellent heat resistance, and a protrusion 879 provided on the outer peripheral surface thereof.
a is an upper sealed case 801a and a lower sealed case 801b
Abuts on the inner wall surface and the end surface of the protrusion 879a.
, Upper sealed case 801a and lower sealed case 801b are hermetically welded by a single welding bead 879b.

The upper sealed case 801a is composed of a body shell 801a1 for supporting the stator 703b of the motor 703 and an upper shell 801a2 on which a glass terminal 88 for motor power supply is arranged, and supports one end of the drive shaft 704 therebetween. An upper frame 126 is arranged.

Discharge pipe 831 and glass terminal 88
The upper frame 126, which separates the motor side and the motor side, is made of gray cast iron.
9a is in contact with the inner wall and the end surface of the upper shell 801a2 and the trunk shell 801a1, and a single weld bead 77 is provided.
9b hermetically seals the upper shell 801a2 and the torso shell 801a1 together with the protrusions 77 of the upper frame 126.
9a is fixed by sandwiching the outer periphery thereof. In other words,
Although the weld bead 779b has an alloy structure between the upper shell 801a2 and the shell 801a1 made of soft iron, the weld bead 779b does not have an alloy structure with the surface of the upper frame 126 made of gray cast iron. Without effect, weld bead 7
79 b surrounds and fixes the upper frame 126.

The oil separation chamber 128 provided on the upper frame 126 is in communication with the motor chamber 706 through the gas holes 129 provided in the upper frame 126.

Drive shaft 7 supported on upper frame 126
When the drive shaft 704 rotates forward, the surface of the upper end shaft 704d of the upper end shaft 704d has a spiral oil groove 741 in a direction in which the lubricating oil separated from the discharge gas in the oil separation chamber 128 is guided to the motor chamber 806.
d is provided.

An upper balance weight 775 and a lower balance weight 776 are attached to the upper end and the lower end of the rotor 703a of the motor 703, and the axial movement of the rotor 703a causes the end of the upper frame 126 and the body frame 80 to move in the axial direction.
5 is regulated.

The upper frame 126 and the main body frame 805
The diameter D of the main bearing 812 of the drive shaft 704 supported by
Is set to be larger than the sum of the diameter d of the crankshaft 714 and twice the crank eccentricity (e), so that the drive shaft 704 can be pulled upward.

The lower surface of the lower balance weight 776 contacts the thrust bearing 713 at the upper end of the main body frame 805 to support the drive shaft 704 and the rotor 703a.

The oil sump 772 above the main bearing 812 is connected to the back pressure chamber 83 of the orbiting scroll 718 through an oil hole B 738b.
It leads to 9.

The high-pressure oil chamber A778a is
5 through the oil hole A838a provided in the discharge chamber 34.
Leads to.

The discharge chamber 2 communicating with the discharge port 16 of the compression chamber
Communicates with the motor chamber 806 via a discharge passage 880 described later.

The discharge passage 880 (see FIG. 1) is provided in the discharge chamber 2 and the fixed scroll 815 formed by the discharge cover 2a mounted on the end plate 815b so as to cover the check valve device 50 and the end plate 815b. Gas passage B88
0b, gas passage A88 provided in main body frame 805
0a, the discharge guide 881 attached to the main body frame 805 so as to surround the main bearing 812, and the main body frame 805.
The gas passage A 880a and the gas passage B 880b are provided at symmetrical positions, respectively (see FIG. 12).

As shown in FIG. 7, a large number of small holes 81a are provided on the upper surface of the discharge guide 881.

An accumulator chamber 846 communicating with the evaporator side of the refrigeration cycle is formed by a lower sealed case 801b, a fixed scroll 815, and a main body frame 805, and a suction pipe 47 communicating therewith is provided on a side surface of the lower sealed case 801b. The suction holes 43 are provided in the fixed scroll 815 at two positions separated from each other by approximately 90 degrees from the position facing the suction pipe 47 (see FIG. 12).

Oil hole A8 provided in main body frame 805
Oil chamber A778a which communicates with the discharge chamber oil reservoir 34 via 38a
The orbiting scroll 8 is provided by an annular ring 94 attached to the end of the orbiting boss 818e of the orbiting scroll 818.
Excessive leakage of lubricating oil into the back pressure chamber 839 of the lubricating oil supply 18 is prevented.

As shown in FIGS. 1 and 8, the oil chamber A778a
Communicates with the discharge chamber oil reservoir 34 via an oil hole A838a provided in the main body frame 805.

The orbiting boss 818 of the orbiting scroll 818
An annular seal groove 95 which is concentric with the center of the slewing bearing 818b is provided on the end face of the main body frame 805 on the side of the main body 805, and a part of the annular seal groove 95 is cut as shown in FIG. And an annular ring 94 made of resin having flexibility. The outer peripheral surface of the annular ring 94
Thermal expansion of the annular ring 94 and the annular ring 9 during operation of the compressor
Due to the lubricating oil pressure inside 4, cutouts 94 b that are in close contact with the side surfaces of the annular seal groove 95 and that have an inclination angle with respect to the outer peripheral surface of the annular ring 94 are arranged to be in close contact with each other. The annular ring 94 prevents excessive leakage from the oil chamber A 778a on the side of the main bearing 812 supporting the drive shaft 704 to the back pressure chamber 839 of the orbiting scroll 818 formed by the orbiting scroll 818, the main frame 805, and the thrust bearing 220. Sealed to prevent.

The oil chamber A 778a includes a spiral oil groove 741b provided on the outer peripheral surface of the crankshaft 714 and the crankshaft 71.
4, an oil chamber B 778 b provided at an end portion, an axial oil hole 112 d provided in the drive shaft 704, and a spiral oil groove 74.
1a, an oil sump 772, and an oil hole B738b provided in the main body frame 705, and communicates with the back pressure chamber 739.
The open end of the oil hole B738b is intermittently shut off by the turning motion of the annular ring 94.

The fixed scroll 815 is made of a high silicon aluminum alloy whose coefficient of thermal expansion is equivalent to an intermediate value between pure aluminum and eutectic graphite cast iron, and has a spiral fixed scroll wrap 815a as shown in FIG. At the center of the end plate 815b, a discharge port 16 that opens at the beginning of winding of the fixed scroll wrap 515a is provided in communication with a discharge passage 880 that opens to the motor chamber 806, and an outer peripheral portion of the fixed scroll wrap 815a is provided. Is provided with a suction chamber 17.

A check valve device 50 is mounted on the end plate 815b on the side opposite to the orbiting scroll so as to cover the discharge port 16, and the check valve device 50 is, as described in detail in FIGS. A valve body 50b (or a valve body 50e having a discontinuous annular hole 50ea) made of a thin steel plate having a shape in which the outer peripheral portion is cut off at several places, a check valve hole 50a and a central hole 50g.
And a valve case 9 having a plurality of small discharge holes 50h therearound.
9 and a spring device 50c interposed between the valve body 50b and the valve case 99. The spring device 50c contracts when its own temperature exceeds 50 ° C., and its own temperature becomes 50 ° C.
The compressor has a shape memory characteristic that expands at a temperature of 50 ° C. or less, and contracts to the bottom surface of the check valve hole 50a due to the discharged refrigerant gas pressure during operation of the compressor, and the temperature of the compressor itself is 50 ° C. or less. During stop, the valve body 50 is set to be pressed against the end plate 15b so as to close the discharge port 16.

As shown in FIGS. 1 and 12, a spiral orbiting scroll wrap 818a meshing with the fixed scroll wrap 815a to form a compression chamber side wall,
Turning boss 818e engaged with the crankshaft 714 of No. 04
The orbiting scroll 818 made of an aluminum alloy, which is composed of a wrap support disk 818c in which the uprights are upright, is disposed so as to be surrounded by the fixed scroll 815 and the main body frame 805. The surfaces of the wrap support disk 818c and the orbiting scroll wrap 818a are porous. Hardening treatment such as high quality nickel plating is performed. As shown in FIG. 3, a spiral tip seal groove 9 is provided at the tip of the orbiting scroll wrap 818a.
A resin chip seal 98a is mounted in the chip seal groove 98 with a minute gap. When the orbiting scroll 818 is pressed in the axial direction of the fixed scroll 815, the flat portion of the wrap support disk 818 c contacts the tip of the fixed scroll wrap 815 a, but the tip of the orbiting scroll wrap 818 a does not contact the fixed scroll 815. A minute distance of about a micron is maintained.

The low-pressure oil reservoir 846a at the bottom of the accumulator chamber 846 and the suction hole 43 communicate with an oil suction hole A9a provided on the discharge cover 2a and a small-diameter oil suction hole B9b provided on the fixed scroll 815. These oil suction holes (9a, 9b) are set so that refrigerant liquid or lubricating oil accumulated in the low-pressure oil reservoir 846a is sucked up by generation of negative pressure when refrigerant gas passes through the suction holes 43. I have.

A flat thrust bearing 22 which is restricted in movement in the rotational direction by a split pin type parallel pin 19 fixed to the main body frame 805 and is movable only in the axial direction.
Numeral 0 denotes an elastic force of an annular seal ring (made of rubber) 70 (see FIG. 10) disposed between the lap support disk 818c and the main body frame 805 and interposed between the thrust bearing 220 and the main body frame 805. As a result, it comes into contact with the end plate mounting surface 15b1 between the main body frame 805 and the fixed scroll 815.

The wrap support disk 8 of the orbiting scroll 818
The height from the sliding face 15b2 of the end plate slidingly in contact with the end plate 18c to the mounting surface 15b1 of the end plate 18c is determined by the oil film of the lap supporting disk 818c so as to improve the sealing performance of the sliding part.
The thickness is set to be approximately 0.015 to 0.020 mm larger than the thickness of 18c.

The annular thrust bearing 220 is made of a sintered alloy whose hole can be easily formed. As shown in FIGS. 10 and 11, two guide holes 93 into which the split pin 19 is movably inserted, an annular oil groove 92, and oil It has a hole 91 and is attached to the thrust ring groove 890 of the main body frame 805.

Body frame 805 and thrust bearing 220
A release gap 827 of about 0.05 mm is provided between the two, and an annular groove 28 for mounting the seal ring 70 is provided inside and outside the release gap 827. The seal ring 70 seals between the release gap 827 and the back pressure chamber 839.

A plurality of coil springs 131 are arranged at equal intervals on the back side of the thrust bearing 220 on the opposite side of the compression chamber, and the end faces of the coil springs 131 are held down by a discharge guide 881 attached to the main body frame 805, and the thrust bearings The bearing 220 is fixed to the end plate 815 of the fixed scroll 815.
b.

The rear side of the thrust bearing 220 communicates with the discharge chamber oil reservoir 34 by a coil spring mounting hole 132 provided in the main body frame 805 and an oil introduction hole 133 provided in the discharge guide 881.

On the back side of the thrust bearing 220, a seal ring A70a is mounted only on the inside, and on the outer side,
The thrust bearing 220 is sealed by pressing against the end plate 815b.

As shown in FIGS. 1 and 2, the thrust bearing 2
The rotation preventing member (hereinafter referred to as Oldham ring) 24 of the orbiting scroll 818 disposed inside 20 is made of a light alloy or a reinforced fiber composite material suitable for sinter molding, injection molding or the like. A key portion having a parallel key shape orthogonal to each other on both surfaces is provided. The key portion on the upper surface is provided in a key groove 71a provided in the main body frame 805, and the key portion on the lower surface is provided in a lap support disk 818c. It engages with the groove 71 and slides.

When the Oldham ring 24 reciprocates, the thickness of the ring of the Oldham ring 24 is determined by the body frame 80.
5 and the lap support disk 818c are set so as to slide smoothly and no jumping phenomenon occurs.

As shown in FIG. 1, FIG. 10 and FIG. 12, the back pressure chamber 839 is provided with the first compression chambers 61a and 61b intermittently communicating with the suction chamber 17 about 18 degrees before the suction refrigerant gas is completely confined.
Within the turning angle range of 0 degrees, the oil groove 291 provided on the thrust bearing 220, the outer peripheral space 37 outside the lap support disk 818c, and the oil groove 8 provided on the sliding surface of the end plate 815b.
It leads to the suction chamber 17 sequentially via 91.

In FIG. 13, the horizontal axis represents the rotation angle of the drive shaft 704, the vertical axis represents the refrigerant pressure, and the pressure change state of the refrigerant gas during the suction, compression and discharge processes.
2 indicates a pressure change during operation at normal pressure, and a dotted line 63 indicates a pressure change during abnormal pressure rise.

The operation of the scroll refrigerant compressor configured as described above will be described.

1 to 13, when the drive shaft 704 is rotationally driven by the motor 703, the orbiting scroll 8 is rotated.
The drive shaft 7 is driven by a crank mechanism of the drive shaft 704.
The key section on the side of the orbiting scroll 818 of the Oldham ring 24 is about to rotate around the main axis of the 04 (see FIG. 2).
Is engaged with the key groove 71 of the orbiting scroll 818, and the key portion on the opposite side is engaged with the key groove 71a (see FIG. 1) of the main body frame 805. Along with 815, the volume of the compression chamber is changed to perform a suction / compression operation of the refrigerant gas.

The release gap 827 on the back side of the thrust bearing 220 communicating with the discharge chamber oil reservoir 34 communicating with the discharge port 16 of the compression chamber is filled with lubricating oil on which the pressure of the discharged refrigerant gas acts.

The thrust bearing 220 is pressed against the end plate mounting surface 15b1 of the fixed scroll 115 by the high-pressure lubricating oil, the elastic force of the coil spring 131 and the seal ring 70 as time elapses after the start of compression. Thereby, the lap support disk 818c of the orbiting scroll 818 is pinched between the end plate sliding surface 15b2 and the thrust bearing 220 (15 to 15).
20 micron assembly gap).

Then, the suction refrigerant of the gas-liquid mixture containing the lubricating oil flows from the refrigerating cycle connected to the compressor into the accumulator chamber 846 through the suction pipe 47 and collides with the outer surface of the end plate 15b of the fixed scroll 815 after the collision. Through the upper space of the accumulator chamber 846, two suction holes 4
3 (see FIG. 12) and flows into the suction chamber 17.

On the other hand, the liquid refrigerant and the lubricating oil separated from the refrigerant gas by the weight difference between the gas and the liquid and the inertia force at the time of the inflow direction change are once collected at the bottom of the accumulator chamber 846, and the suction refrigerant gas is collected at the suction hole 43. Is sucked up into the suction hole 43 in an atomized state through the oil suction holes A9a and B9b by the negative pressure generated when passing through the suction port A9a and the oil suction hole B9b, and again mixed into the suction refrigerant gas.

The refrigerant gas that has been separated into gas and liquid is supplied to the suction chamber 1
7. Enclosed in the compression chamber via the first compression chambers 61a and 61b (see FIG. 12) formed between the orbiting scroll 818 and the fixed scroll 815, the second compression chamber 51
a, 51b and the third compression chambers 60a, 60b are sequentially transferred and compressed, and then discharged from the central discharge port 16 to the check valve chamber 50a, and are discharged to the discharge chamber 2, the gas passage B80b, and the gas passage A8.
0a and the motor chamber 80 sequentially through the discharge chamber 2b.
6 is discharged.

Since the compression chamber and the discharge port 16 are opened immediately after the completion of the compression, the compressed refrigerant gas undergoes rapid primary expansion when flowing into the check valve chamber 50a from the compression chamber. During the period from the completion stroke to the compression completion stroke, the refrigerant gas discharged from the check valve chamber 50a temporarily flows back to the compression chamber.

As a result, the refrigerant gas intermittently flows out of the third compression chambers (60a, 60b).
a, 60b), while flowing out from the third compression chamber (60a, 60b) to the discharge chamber 2 as a whole flow, the refrigerant gas discharged from the check valve chamber 50a and the discharge chamber 2 is the third flow. Pressure fluctuations occur during the inflow and outflow to and from the compression chambers (60a, 60b), causing a pulsation phenomenon.

The discharged refrigerant gas undergoes secondary expansion when flowing toward the spherical wall surface forming the discharge chamber 2 through the small discharge hole 50h of the check valve device 50, and further collides with the spherical wall surface. Distribute evenly. Thereafter, the two discharge passages 880 arranged at the symmetrical positions merge in the discharge chamber 2c and the motor chamber 806, so that the pulsation of the discharge gas from each discharge passage 880 cancels each other.
Due to the fourth expansion, the motor chamber 80 attenuates sequentially.
The pressure pulsation of 6 becomes extremely small.

When the discharged refrigerant gas instantaneously flows backward from the discharge chamber 2 to the check valve chamber 50a, the valve body 50b tries to move in a direction to close the discharge port 16 following the flow. During the operation of the machine, the coil spring 50c having the shape memory characteristic is completely contracted by the ambient temperature and does not exert an urging force on the valve element 50b, and the valve element 50b is connected to the discharge port 1.
6 is not blocked.

The refrigerant gas discharged from the small holes 81a of the discharge guide 881 and discharged to the motor chamber 806 collides with the annular closing plate 86 and the windings of the motor 703, and then the cooling passage 35 on the outer side of the stator 703b. The fluid flows to the upper side of the motor chamber 806 while cooling the motor 703 through the passage inside and inside, and is sent from the discharge pipe 831 to an external refrigeration cycle.

At this time, part of the lubricating oil in the discharged refrigerant gas adheres to the surface of the lower winding of the motor 703 and separates from the refrigerant gas and is collected in the discharge chamber oil reservoir 34. The lubricating oil in the discharged refrigerant gas passing through the outer periphery of the weight 775 and the lower balance weight 776 is centrifuged by the rotation of the upper balance weight 775 and the lower balance weight 776, and is diffused to the inner surface of the winding of the motor 703. , Flows down along the internal space of the winding bundle, and is collected in the discharge chamber oil reservoir 34.

The lubricating oil in the discharge chamber oil reservoir 34 is supplied to the oil chamber A 778a, the oil chamber B 778b, and the back pressure chamber 8 through a path described later.
39, and finally flows into the suction chamber 17, while gradually turning the orbiting scroll 81 by the lubricating oil pressure in the oil supply path.
8 increases the back pressure applying force.

The lap support disk 818c gradually contacts the end plate sliding surface 15b2 of the fixed scroll 815 with an appropriate pressing force following the rise in the pressure of the motor chamber 806. Tip of fixed scroll wrap 815a and orbiting scroll 818
The gap between the lap support disk 818c and the compression chamber is sealed, the suction refrigerant gas is efficiently compressed, and the stable operation is continued.

The axial gap between the end of the orbiting scroll wrap 818a and the end plate 815b of the fixed scroll 815 is formed when the refrigerant gas during compression leaks to the adjacent low-pressure side compression chamber 98 (see FIG. 3), and the gas back pressure causes the tip seal 98a to be pressed against the side surface of the low compression chamber of the tip seal groove 98a and the end plate 815b of the fixed scroll 815 to be sealed.

When the compressor is stopped, the orbiting scroll 818 instantaneously makes a reverse orbital motion due to the backflow based on the pressure difference of the refrigerant gas in the compression chamber. However, since the refrigerant gas flows back from the compression chamber to the suction chamber 17, As shown in FIG. 12, the orbiting scroll 818 has the first compression chambers 61a and 61b
Stop at the turning angle that leads to. As shown in FIG. 8, in this stopped state, the annular ring 94 closes the lubricating oil inlet to the back pressure chamber 839.

When the compressor is stopped, the refrigerant gas in the compression chamber flows back into the suction chamber 17 so that the refrigerant gas pressure in the discharge port 16 drops sharply, and the refrigerant gas pressure difference between the discharge port 16 and the discharge chamber 2 is reduced. As a result, the valve body 50b is
To prevent continuous backflow of the refrigerant gas discharged from the discharge chamber 2 to the compression chamber.

Due to the temporary reverse flow of the discharged refrigerant gas immediately after the compressor is stopped and the reverse rotation of the orbiting scroll 818, the magnetic valve body 50b is separated from the bottom surface of the check valve chamber 50a,
Until the refrigerating cycle balances the pressure, the valve body 51b keeps closing the discharge port 16 due to the pressure difference. At the same time, the temperature of the coil spring 50 having the shape memory characteristic decreases and the coil spring 50 expands.
0b keeps closing the discharge port 16.

When the compressor is stopped for a long time, the pressure in the compressor is balanced, and the liquid refrigerant flows into the compression chamber as well as the accumulator chamber 846, so that liquid compression is likely to occur in the initial stage of the cold start of the compressor. A thrust force in the direction opposite to the discharge port 16 acts on the orbiting scroll 818 by the pressure of the liquid compressed refrigerant in the compression chamber. As a result, the orbiting scroll 818
Are separated from the fixed scroll 815 in the axial direction, and the compression load is reduced.

On the other hand, the back pressure chamber 839 at the initial stage of the cold start of the compressor.
Is almost equivalent to the suction pressure because the rise in the lubricating oil pressure in the discharge chamber oil reservoir 34 is low. As a result, the lap support disk 818c of the orbiting scroll 818 is separated from the end plate sliding surface 15b2 in a state where the back pressure is applied only by the lubricating oil in the oil chamber A778a with a low pressure rise, and the thrust bearing 22
0 , and is supported to the gap between the wrap support disk 818c and the tip of the fixed scroll wrap 815a (about 0. 0).
015 to 0.020 microns), the compression chamber pressure is reduced, and the compression load at the initial stage of startup is reduced.

If, for example, liquid compression occurs in the compression chamber during continuous operation and the pressure in the compression chamber rises abnormally instantaneously, the thrust force acting on the orbiting scroll 818 is applied to the back of the orbiting scroll 818. The orbiting scroll 818 moves in the axial direction,
It is supported by a thrust bearing 220. Then, the sealing of the compression chamber is released in the same manner as described above, the compression chamber pressure is reduced, and the compression load is reduced.

The back pressure chamber 839 is connected to the first compression chamber 61
Since a and 61b communicate with the outer peripheral space 37 via the oil groove 291 provided in the thrust bearing 220 within a turning angle range of about 180 degrees before the suction refrigerant gas is completely confined,
The lubricating oil in the back pressure chamber 839 does not continuously flow into the compression chamber via the oil groove 891 and the suction chamber 17, thereby suppressing the generation of oil compression in the compression chamber.

The lubricating oil in the discharge chamber oil reservoir 34 at the beginning of the cold start of the compressor is supplied to the spiral oil groove 741 provided on the drive shaft 704.
a, oil hole A838 by the screw pump action of 741b
The oil is sucked into the oil chamber A 778a via a.

Thereafter, a part of the lubricating oil is
b, the oil chamber B 778b, and the lubrication hole 112d sequentially lubricate the sliding surface of the turning bearing 818b on the way, and are supplied to the sliding surface of the main bearing 812 and sent out to the oil sump 772.

The main bearing 812 is formed by the spiral oil groove 741a.
The lubricating oil supplied to the lubricating oil joins with the lubricating oil that has passed through the oil chamber B778b in the oil sump 772, and then a part of the lubricating oil is depressurized in the throttle passage portion of the oil hole B738b (see FIG. 8), so that the back pressure is reduced. The chamber 839 is intermittently refueled. The remaining lubricating oil is returned to the discharge chamber oil sump 34 after lubricating the sliding surfaces of the thrust bearing portion 713 supporting the weight of the drive shaft 704 and the rotor 703a.

The refrigerant gas in the motor chamber 806 is supplied to the oil sump 77 by the lubricating oil passing through the thrust bearing 713.
Backflow to 2 is prevented.

The vertical vibration of the drive shaft 704 caused by the end face of the lower balance weight 776 slidably contacting the thrust bearing 713 at a high speed causes the upper bearing 811 in which the end face of the upper balance weight 775 is disposed on the upper frame 126.
Is regulated by abutting against the end portion.

The oil supply to the upper bearing 811 is performed by the cooling passage 3
5, drain hole 129 through an oil separation space is separated from the inflow refrigerant gas 128a lubricant spiral oil groove collected in the central portion of the upper frame 126 of the upper frame 126 741d
Is supplied by the screw pumping action.

The pressure of the refrigerant gas discharged from the motor chamber 806 rises following the passage of time after the start of the compressor in cold mode, and the lubricating oil in the oil chamber 34 of the discharge chamber is also oiled by the pressure difference between the back chamber 839 and the back pressure chamber 839. The spiral oil grooves 741a, 741 are supplied to the chamber A778a.
The oil is supplied to the back pressure chamber 839 together with the screw pumping action of b. The pressure in the back pressure chamber 839 gradually increases, and the oil chamber A77
8A acts on the wrap support disk 818c of the orbiting scroll 818. As a result, the thrust load acting to separate the orbiting scroll 818 from the fixed scroll 815 is canceled by the refrigerant gas pressure in the compression chamber, and the thrust force acting on the orbiting scroll 818 is reduced.

Therefore, while the pressure rise in the motor chamber 806 after the cold start of the compressor is low, the force exerted on the orbiting scroll 818 by the lubricating oil pressure in the oil chamber A 778a and the back pressure chamber 839 increases the refrigerant gas pressure in the compression chamber. Orbiting scroll 81
8 less than the thrust load. As a result, the orbiting scroll 818 is separated from the fixed scroll 815 and supported by the thrust bearing 220 which receives the elastic force of the coil spring 131 and the seal ring 70 and the back pressure due to the lubricating oil introduced from the discharge chamber oil reservoir 34.

When the pressure difference between the discharge pressure and the suction pressure exceeds the required pressure, the force exerted on the orbiting scroll 818 by the lubricating oil pressure in the oil chamber A 778a and the back pressure chamber 839 causes the orbiting by the refrigerant gas pressure in the compression chamber. It becomes larger than the thrust load on the scroll 818. And the orbiting scroll 818
Are supported by the fixed scroll 815.

The center of the compression chamber, the center of the slewing bearing 818e,
In the arrangement in which the centers of the annular rings 94 are substantially coincident with each other, since the annular ring 94 orbits together with the orbiting scroll 818, the annular ring 94 tends to jump out of the annular seal groove 95 provided in the orbiting boss 818e by the inertia force at that time. . The annular ring 94 expands its inner diameter by the pressure difference between the oil chamber A 778a and the back pressure chamber 839, and closes the cutout 94b together with the thermal expansion. By these actions, the annular ring 94 is pressed against the outer surfaces of the main body frame 805 and the annular seal groove 95, and the annular seal groove 95 and the annular ring 94 are scraped by the oil scraping action of the annular ring 94.
Between the oil chamber A 778a and the back pressure chamber 839 to prevent excessive leakage of the lubricating oil.

Further, the resin-made annular ring 94 having excellent flexibility expands its inner diameter along the outer surface of the annular seal groove 95 due to a pressure difference between the back pressure chamber 839 and the oil chamber A778a, thereby reducing heat. The cutout 94b is closed together with the expansion, and at the same time, the cutout 94b is pressed against the outer surface of the annular seal groove 95, so that leakage between the two spaces is further reduced.

The annular ring 94 is formed by an oil film of lubricating oil accumulated in an oil groove 94a provided on the surface of the annular groove 94.
By lubricating the sliding surface between the sliding surface and the body frame 805, wear and sliding resistance of the sliding surface are reduced.

During the normal operation of the compressor, the high pressure oil chamber A778
The orbiting scroll 818 is given a back pressure to the fixed scroll 815 side by the lubricating oil pressure of a and the lubricating oil pressure of the back pressure chamber 839, and the lap support disk 818c and the end plate sliding surface 15b
2 and slide smoothly while maintaining an appropriate contact force,
The axial clearance in the compression chamber is minimized.

The lubricating oil flowing into the back pressure chamber 839 intermittently flows into the outer peripheral space 37 through an oil groove 291 provided in the thrust bearing 220, and further flows through an oil groove 891 provided in the end plate 815b. And flows into the suction chamber 17. The lubricating oil lubricates each sliding surface in the middle of the passage and seals the sliding gap.

The lubricating oil that has flowed into the compression chamber (compression space) together with the suctioned refrigerant gas seals a minute gap between adjacent compression chambers with an oil film to prevent leakage of the compressed refrigerant gas and lubricate the sliding surfaces between the compression chambers. The compressed refrigerant gas is discharged again to the motor chamber 806 via the discharge port 16 together with the compressed refrigerant gas.

In the oil supply path from the discharge chamber oil reservoir 34 through the back pressure chamber 839 to the suction chamber 17, the back pressure chamber 839 maintains an appropriate intermediate pressure between the discharge pressure and the suction pressure.

Further, since the compression ratio of the scroll refrigerant compressor is constant, when the differential pressure between the suction chamber 17 and the discharge chamber 2 is small, such as immediately after the start in cold operation, or abnormal liquid compression occurs. In such a case, as described above, the orbiting scroll 8
18 moves away from the fixed scroll 815 and is supported by the thrust bearing 220.

However, the thrust bearing 220 urged by the back pressure cannot support the abnormally increased compression chamber pressure load, and retreats in a direction to reduce the release gap 827 .
The axial gap between the wrap support disk 818c of the orbiting scroll 818 and the tip of the fixed scroll wrap 815a of the fixed scroll 815 increases. As a result, a large amount of leakage occurs between the compression chambers, and the pressure in the compression chamber suddenly drops during the compression as shown by the one-dot chain line 63a in FIG.

The orbiting scroll 818 is the fixed scroll 8
Since the maximum distance apart from 15 in the axial direction is regulated to about 70 microns, an oil film remains in each gap between the sliding surfaces on both sides of the lap support disk 818c, and the lubricating oil flows from the outer peripheral space 37 to the suction chamber 17. After the pressure change in the back pressure chamber 839 due to the excessive inflow is suppressed and the compression load is instantaneously reduced, the thrust bearing 220 can instantly return to the original position, and the stable operation is continued again.

When the orbiting scroll 818 retreats toward the thrust bearing 220, the orbiting scroll wrap 81
Although the axial dimension between the tip of the fixed scroll 815 and the tip of the fixed scroll 815 also increases, since the tip seal 98a is pressed against the fixed scroll 15 by the gas pressure on the back surface, compressed refrigerant gas leaks from this portion. Rarely occurs.

On the other hand, the gap between the wrap support disk 818c of the orbiting scroll 818 and the tip of the fixed scroll wrap 815b of the fixed scroll 815 is enlarged, and compressed refrigerant gas leaks in the compression chamber, causing a sudden increase in the pressure in the compression chamber. descend.

Also, when foreign matter is caught in the axial gap between the orbiting scroll 818 and the fixed scroll 815, the thrust bearing 220 retreats and removes the foreign matter as described above.

In the initial stage of cold start or during steady-state operation, when the instantaneous liquid compression occurs, the compression chamber pressure is abnormally over-compressed as shown by a dotted line 63 in FIG.
The high pressure space volume communicating with the
0a, the discharge chamber 2, and the discharge chamber 2c, the expansion is repeated while passing sequentially, and the pressure in the motor chamber 806 hardly changes.

In the above embodiment, the oil hole B 738b of the main frame 805, the oil groove 291 of the thrust bearing 220, and the oil groove 891 of the end plate 815b are set so that the back pressure chamber 839 has an intermediate pressure between the discharge pressure and the suction pressure. However, the back pressure chamber 839 may be set to be equivalent to the suction pressure according to the load condition of the compressor.
8 depends only on the lubricating oil pressure of the oil chamber A778a.

Further, in the above embodiment, the outer peripheral space 37 is communicated with the suction chamber 17, but the outer peripheral space 37 is provided in the oil hole 83 provided in the lap support disk 818c of the orbiting scroll 818.
It may communicate with the first compression chambers 61a and 61b via 8c (see FIG. 10).

As described above, according to the above embodiment, the operation and effect of the embodiment described below can be obtained.

That is, according to the first embodiment, the crankshaft 71 provided at the tip of the drive shaft 704 so that the drive shaft 704 engages with the orbiting bearing 818 b of the orbiting scroll 818.
Reference numeral 4 denotes a main bearing provided on the main body frame 805 with a diameter of a rotation locus of the outer peripheral surface of the drive shaft 704 with respect to the main shaft.
12 is set to be equal to or smaller than the bearing inner diameter of the drive shaft 70.
4 from the motor 703 side to the main bearing 812 and the slewing bearing 81
8b, the upper bearing 811 supporting the drive shaft 704 together with the main body frame 805 is provided on the non-compression chamber side of the motor 703.
1 and is configured to regulate the range in which the drive shaft 704 moves in the axial direction by the main body frame 805 and the upper bearing 811 . According to this configuration, the fixed scroll 815, the orbiting scroll 818, and the main bearing 81
The drive shaft 704 can be detached and replaced without changing the assembly state of the drive shaft 2, and the drive shaft 704 adapted to the dimensions of the fixed scroll 815, the orbiting scroll 818, and the main bearing 812 can be selectively assembled, and the clearance in the radial direction of the compression chamber can be minutely assembled. In addition to reducing gas leakage during compression, the drive shaft 70
4 prevents the axial vibration of the drive system and the accompanying noise by restricting the free axial movement of the drive shaft 4, and the drive shaft 704.
Of the sliding portion can be simultaneously improved.

According to the second embodiment, the upper balance weight 775 and the lower balance weight 776 of the drive shaft system disposed at the end of the rotor 703a of the motor 703 regulate the axial movement range of the drive shaft 704. It is. According to this configuration, the axial vibration of the drive shaft system can be prevented by simple means.

According to the third embodiment, at least the main body frame 805, the drive shaft 704, the motor 703, the upper shaft
The receiver 811 is arranged in the high-pressure space of the closed case 801, and after collecting the lubricating oil separated from the discharge gas discharged from the discharge port 16 into the high-pressure space in the closed case 801 in the discharge chamber oil reservoir 34, the bearing 811 rotates with the main bearing 812. all Jun supplied to the bearing 818b
Of the lubricating oil amount, most of the lubricating oil is again discharged into the discharge chamber oil reservoir 34.
While back in and vacuum the remaining lubricating oil, the compression chamber (61
a, 61b) and the suction chamber 17 are provided with oil supply means. And according to this configuration,
The oil film sealing of the compression chamber gap by proper oil supply to the suction chamber 17 and the durability improvement by sufficient oil supply to the main bearing 812, the swivel bearing 818b, and the auxiliary bearing 811 can be realized at the same time. In particular, the durability of the slewing bearing 818b having a smaller diameter than the main bearing 812 can be easily secured.

According to the fourth embodiment, the drive shaft 704 is
As means for restricting movement to the compression chamber side, the drive shaft 7
Lower balance weight 77 arranged on the compression chamber side of system 04
6 is the rotor 703 of the motor 703 of the main body frame 805.
To be supported by a thrust bearing 713 disposed at the end on the a side
After forming and lubricating the main bearing 812,
Thrust as the lubrication passage immediately before returning to the
G bearing part 713 is provided. According to this configuration, the vibration in the axial direction of the drive shaft 704 caused by the change in the oil supply state due to the variable speed operation of the compressor on the bearing portion supporting the drive shaft 704 is prevented by the simple means using the lubricating oil film. Durability can be improved at the same time. Also,
Since the thrust bearing portion 713 is the final lubrication passage,
Lubricating oil degraded due to temperature rise due to dynamic heat directly
It is not supplied to the next sliding part,
Effect can be maintained.

[0109] In the above embodiment has been described refrigerant compressor can be expected oxygen, nitrogen, the same effects even if other gas compressor such as helium that use lubricating oils.

The original application of the present application (Japanese Patent Application No. 1-2835)
As described in 61), in the above-described embodiment, the configuration of the vertical compressor is shown and its effect is described. However, the same operation and effect can be expected for the configuration of the horizontal compressor. I
Accordingly, the upper frame 126 and the upper bearing 811 are “upper”.
It is clear that `` department '' does not have a functional meaning.
It will be clear.

In the above embodiment, the lubricating oil in the discharge chamber oil reservoir is supplied to the suction chamber by differential pressure. However, the same effect can be expected when lubricating oil is supplied to the compression chamber during compression.

[0112]

As is apparent from the above embodiment, the first aspect of the present invention is as follows.
The crankshaft provided at the tip of the drive shaft so that the drive shaft engages with the orbiting bearing of the orbiting scroll has a diameter of a rotation locus of an outer peripheral surface of the drive shaft with respect to a main shaft of the orbiting scroll provided on the main body frame. In a configuration in which the drive shaft is set to be equal to or less than the bearing inner diameter of the main bearing, and the drive shaft is dimensioned so that it can be sequentially inserted into the main bearing and the slewing bearing from the motor side, the drive shaft together with the main body frame is mounted on the non-compression chamber side of the motor. The upper bearing to be supported is arranged in a sealed case, and the range in which the drive shaft moves in the axial direction is regulated by the main body frame and the upper bearing . According to this configuration, the drive shaft can be detached and replaced without changing the assembly state of the fixed scroll, the orbiting scroll, and the main bearing, and the drive shaft suitable for the dimensions of the fixed scroll, the orbiting scroll, and the main bearing can be selectively assembled. In addition to micro-assembly of the radial gap in the compression chamber to reduce gas leakage during compression and to restrict the free axial movement of the drive shaft, it prevents axial vibration of the drive system and the accompanying noise. And the durability of the sliding portion of the drive shaft can be improved at the same time. Furthermore, since the orbiting scroll is not hindered by the drive shaft when the orbiting scroll moves in the axial direction, when the compression chamber pressure instantaneously abnormally rises, the orbiting scroll quickly separates from the fixed scroll in the axial direction, and the compression chamber gap increases. , The pressure in the compression chamber is reduced, and the overload can be reduced, so that there is an effect that the durability of the compressor can be improved.

According to the second aspect of the present invention, the balance weight of the drive shaft system disposed at the end of the rotor of the motor regulates the axial movement range of the drive shaft. According to this configuration, the axial vibration of the drive shaft system during the operation of the compressor can be prevented by simple means.

According to the third aspect of the present invention, at least the main body frame, the drive shaft, the motor, and the upper bearing are arranged in the high-pressure space of the closed case, and the lubrication separated from the discharge gas discharged from the discharge port to the high-pressure space in the closed case. After collecting the oil in the discharge chamber sump, the total amount of lubricating oil
While most of the lubricating oil is returned to the discharge chamber oil sump,
Oil supply means is provided for reducing the pressure of the remaining lubricating oil and supplying it to one of the compression chamber and the suction chamber. According to this configuration, it is possible to simultaneously achieve oil film sealing of the compression chamber gap by proper lubrication to the compression chamber (suction chamber) and to improve durability by sufficient lubrication to the main bearing and the slewing bearing. In particular, durability can be easily ensured even with a slewing bearing smaller in diameter than the main bearing.

According to a fourth aspect of the present invention, the drive shaft is located on the compression chamber side.
As a means to restrict movement to the
The balance weights on the side of the
Formed to be supported by thrust bearings located at the side ends
At the same time, after lubricating the main bearing, return it to
A thrust bearing portion is provided as a lubricating passage just before the lubrication passage . According to this configuration, the axial vibration of the drive shaft caused by the change in the lubrication state due to the variable speed operation of the compressor to the bearing portion supporting the drive shaft is prevented by the simple means of the lubricating oil film, and the bearing durability is improved. Can also be improved at the same time. In addition, the thrust bearing is the final lubrication passage.
The lubricating oil that has deteriorated due to temperature rise due to sliding heat
The lubricating oil film is not directly supplied to the next sliding part.
This has the effect that the effect of use can be maintained .

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a scroll refrigerant compressor showing one embodiment of the present invention.

FIG. 2 is an exploded view of main parts of the compressor.

FIG. 3 is a partial sectional view of a check valve device arranged at a discharge port of the compressor.

FIG. 4 is a perspective view of components of the check valve device in FIG. 3;

FIG. 5 is a perspective view of a main part of the check valve device.

FIG. 6 is a perspective view of a main part of the check valve device.

FIG. 7 is an exploded perspective view of small parts in the compressor.

FIG. 8 is a partial cross-sectional view of a main bearing in the compressor.

FIG. 9 is a perspective view of a seal component in the compressor.

FIG. 10 is a partial cross-sectional view of a thrust bearing portion of the compressor.

11 is a perspective view of the thrust bearing in FIG.

FIG. 12 is a transverse sectional view taken along line AA in FIG. 1;

FIG. 13 is a characteristic diagram showing a change in pressure of the refrigerant gas from a suction stroke to a discharge stroke of the compressor.

FIG. 14 is a longitudinal sectional view of a conventional scroll compressor.

[Explanation of symbols]

2 discharge chamber 16 discharge port 17 suction chamber 24 rotation prevention member ( Oldham ring) 34 discharge chamber oil reservoir 126 upper frame 220 thrust bearing 703 motor 704 drive shaft 801 sealed case 805 main body frame 806 motor room 811 upper bearing 812 main bearing 815 fixed Scroll 815b End plate 815a Fixed scroll wrap 818 Orbiting scroll 818a Orbiting scroll wrap 818b Orbit bearing 818c Wrap support disk

Claims (4)

(57) [Claims] An orbiting scroll wrap on a wrap support disk forming a part of a orbiting scroll is rotatably engaged with a spiral fixed scroll wrap formed on one surface of a head plate forming a part of a fixed scroll. In addition, a spiral compression space is formed between both scrolls, a discharge port is provided at the center of the fixed scroll wrap, and a suction chamber is provided outside the fixed scroll wrap, and the compression space is discharged from the suction side. A body frame having the lap support disk, the head plate, and a main bearing on a side close to the compression chamber that supports the drive shaft and is divided into a plurality of compression chambers that continuously transition toward the compression chamber; And a thrust bearing for supporting the anti-compression chamber side of the lap support disk in a loose state, and a front end between the lap support disk and the main body frame. A closed casing is provided with a scroll compression mechanism for orbiting the orbiting scroll via a orbiting bearing in which the rotation preventing member of the orbiting scroll is engaged and the drive shaft and the lap support disk are engaged, and a motor connected to the drive shaft. The crankshaft provided at the tip of the drive shaft so that the drive shaft engages with the orbiting scroll has a diameter of a rotation locus of an outer peripheral surface of the crankshaft with respect to the main shaft of the drive shaft. Is set to be
In a configuration in which the drive shaft is dimensionally insertable into the main bearing and the slewing bearing from the motor side, an upper bearing that supports the drive shaft together with the main body frame on the non-compression chamber side of the motor is provided. A scroll gas compressor arranged in a dense case, wherein the range in which the drive shaft moves in the axial direction is regulated by the main body frame and the upper bearing . 2. The scroll gas compressor according to claim 1, wherein the balance weight of the drive shaft system disposed at the end of the rotor of the motor regulates the axial movement range of the drive shaft. 3. A high-pressure space in at least a main body frame, a drive shaft, a motor, and an upper bearing are disposed in a high-pressure space in a closed case, and a lubricating oil separated from a discharge gas discharged from the discharge port into the high-pressure space in the closed case is supplied to a discharge chamber. After collection in the oil sump, most of the total lubricating oil amount supplied to the main bearing and the slewing bearing is returned to the discharge chamber sump again, while the remaining lubricating oil is depressurized and compressed. 2. The scroll compressor according to claim 1, further comprising an oil supply means for supplying the oil to one of the suction chamber and the suction chamber. 4. Restricting movement of the drive shaft toward the compression chamber.
As means, a balun arranged on the compression chamber side of the drive shaft system
A weight is placed on the motor-side end of the body frame.
It is formed to be supported by the thrust bearing part
After lubricating the bearings, lubricate immediately before returning to the closed case.
The thrust bearing portion is provided as a smooth passage.
A scroll gas compressor as described.