JP2785807B2 - 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 an oil supply passage for a bearing of a scroll gas compressor and to a biasing force applied to the oil supply passage to a rear side of the orbiting scroll opposite to the compression side.

[0002]

2. Description of the Related Art In a scroll compressor having low vibration and low noise characteristics, a suction chamber is provided at an outer peripheral portion, a discharge port is provided at a central portion of a spiral, and a flow of a compressed fluid is reciprocated in one direction. It does not require a discharge valve for compressing fluid like a compressor or rotary compressor, has a constant compression ratio, has a small discharge pulsation, and does not require a large discharge space. Chemical research is being 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, the cost of the scroll gas compressor is high and the performance varies greatly due to the complexity of the component shape and the variation in the dimensional accuracy of the spiral part. Particularly, in the low-speed operation state of the compressor, the gas leakage rate during compression is large, and the compression efficiency is high. Has the disadvantage that it is lower than reciprocating compressors and rotary compressors.

Accordingly, as a measure for solving this kind of problem, it is expected that the productivity of the spiral part dimensional accuracy is optimized and the compression efficiency is improved by an oil film sealing effect using a lubricating oil to prevent gas leakage during compression. It is large,
As described in Japanese Patent No. 8386, a proposal has been made to improve the above-mentioned drawbacks by injecting an appropriate amount of lubricating oil into a compression chamber in the middle of compression, sealing the gap between the compression chambers with an oil film of the lubricating oil.

FIG. 25 shows an example of a general structure of a medium to large class scroll refrigerant compressor having a high-pressure space inside a sealed case. In the figure, the compression unit and the discharge chamber 1031 are at the top, the motor (electric element) is at the bottom, the oil sump is at the bottom,
The discharge pipe 1042, which is the final outlet of the compressor, is arranged near the motor (electric element). After the discharge refrigerant gas and the lubricating oil are separated in the discharge chamber 1031, the lubricating oil is discharged to the oil drain holes 1035, 1036. And returns to the space for storing the motor (electric element), and is collected in the oil reservoir at the bottom, and the discharged refrigerant gas passes through the space for storing the motor (electric element) from the upper part of the discharge chamber 1031 through another passage. Are discharged from the discharge pipe 1042.

Further, in order to reduce leakage of refrigerant gas during compression from the initial stage of starting the compressor in which the pressure in the high-pressure space in the closed case is low, the refrigerant gas in the compression chamber 1015 is supplied to the end plate 1004 provided on the end plate 1004 of the orbiting scroll 1006. Pressure hole 1017
And presses the orbiting scroll 1006 toward the fixed scroll 1003 from the initial stage of compressor startup by the refrigerant gas pressure to reduce the axial gap of the compression chamber 1015.

Further, in order to seal the gap between the compression chambers, lubricating oil at the bottom of a sealed case (chamber) 1013 is provided with an oil pumping hole 1 provided inside a drive shaft (crankshaft) 1008.
019, a bearing sliding surface through a clearance of a bearing of a main body frame (frame) 1009 supporting a drive shaft (crankshaft) 1008 and fixing a fixed scroll 1003, and a clearance of a crankshaft portion of the drive shaft (crankshaft) 1008. After the lubrication of the orbiting scroll 1006, the lubricating oil is caused to flow into a back pressure chamber 1025 provided on the back of the orbiting scroll 1006, and the intermediate pressure lubricating oil reduced in the middle of the path and the high pressure lubricating oil on the upper part of the crankshaft are used to clean the back of the orbiting scroll 1006. The back pressure is set so that the energized orbiting scroll 1006 does not always separate from the fixed scroll 1003.

The lubricating oil in the back pressure chamber 1025
After flowing into the compression chamber 1015 in the middle of compression via the compressor 7, it 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 (Japanese Patent Application Laid-Open No. 56-165788). No.).

[0009]

However, as shown in FIG. 25, two sliding portions [drive shaft (crankshaft)] to be engaged with the drive shaft (crankshaft) 1008.
Body frame (frame) 1009 supporting 1008
In the configuration in which a sufficient amount of lubricating oil is supplied to the upper bearing impulsive part provided in the above and a bearing sliding part of a crank part for orbiting the orbiting scroll 1006], the lubricating oil flows into the compression chamber 1015. The lubricating oil and the refrigerant gas mixed into the lubricating oil flow into the compression chamber 1015 in the middle of compression, and the compression efficiency decreases.

In the initial stage of starting the compressor, the compression chamber 1015
The pressure of the back pressure chamber 1025 into which the refrigerant gas flows from is higher than the lubricating oil pressure at the bottom of the closed case (chamber) 1013.
There was a problem that the differential pressure lubrication to the bearing portion supporting the 1008 could not be performed, causing seizure of the drive shaft (crankshaft) 1008 at the initial stage of the compressor startup.

When continuous liquid compression or the like occurs in the compression chamber 1015, the back pressure hole 1017 is removed from the compression chamber 1015.
The abnormal high pressure refrigerant gas flows into the back pressure chamber 1025 through the back pressure chamber, and the back pressure chamber 1025 abnormally rises in pressure from the discharge pressure,
The orbiting scroll 1006 is excessively pressed by the fixed scroll 1003, and the compression load increases rapidly. as a result,
There has been a problem that the differential pressure oil cannot be supplied from the oil reservoir at the bottom to the bearing supporting the drive shaft (crankshaft) 1008, causing seizure of the drive shaft (crankshaft) 1008.

As a measure for solving the above-mentioned problem, when the pressure in the compression chamber rises abnormally, the orbiting scroll is always pressed toward the fixed scroll from the initial stage of compressor startup without excessively pressing the orbiting scroll toward the fixed scroll. There has been proposed a compressor which presses to reduce the axial clearance in the compression chamber, sufficiently supplies oil to the bearing portion of the drive shaft, and can supply oil to the compression chamber through another oil supply passage.

FIGS. 26 and 27 show the orbiting scroll 142.
4, a back pressure region 1450 having a large back area on which the discharge pressure acts is provided, and a low pressure region 145 is provided on the outer periphery thereof.
1 and to form a back pressure region 1450, the back surface of the orbiting scroll 1424 is slid by an annular ring (annular thrust seal) 1449 fixed to the main body frame (frame) 1413 and having a large back pressure urging area. The dynamic scroll is performed, and the orbiting scroll 1424 is constantly pressed against the fixed scroll 1426. Further, the lubricating oil at the inner bottom portion of the closed case is reduced in pressure through the thin tube, and is supplied to the outer peripheral portion of the orbiting scroll 1424 and the sliding contact surface of the fixed scroll 1426 with a differential pressure.

A high-pressure lubricating oil at the bottom of the sealed case is pumped up by a centrifugal pump action by an oil passage (not shown) provided in the drive shaft 1417, and is passed through a bearing portion of the drive shaft 1417 to form an annular ring (annular ring). Thrust seal) 14
After refueling inside 49, it is configured to return to the bottom inside the closed case again (the specification of US Pat. No. 4,522,575).

However, since the orbiting scroll 1424 is constantly pressed against the fixed scroll 1426, it is necessary to secure the amount of oil supply to the contact portion in the axial direction between the two scrolls. Therefore, the amount of oil supply to the suction chamber and the compression chamber through the narrow tube is reduced. Since it is larger than the required amount for sealing, it is necessary to prevent the sealing portion from leaking outside the long annular ring (annular thrust seal) 1449. From such a technical idea, the annular ring (annular thrust seal) 1449 is required. To increase the back pressure bias. As a result, the frictional resistance at the sliding contact between the annular ring (annular thrust seal) 1449 and the orbiting scroll 1424 becomes large, and it is required to improve the input loss and airtight durability of the sliding contact.

On the other hand, as a measure for improving the input loss at the sliding contact portion of the annular ring, a sealing member for partitioning the back surface of the orbiting scroll on the side opposite to the compression chamber into an intermediate pressure gas region and a low pressure gas region is provided in the concave groove. Two means have been proposed which are disposed and do not apply an excessive contact force to the seal sliding contact surface of the seal member.

That is, the first means is shown in FIGS.
As shown in the figure, the rear surface of the orbiting scroll 1505 on the side opposite to the compression chamber is provided on the low pressure side of the orbiting bearing peripheral portion 1507i at the center of the rear surface, and on the end plate 1505a of the orbiting scroll 1505 from the compression chamber on the outer peripheral side of the rear surface. Communication hole 1505f
Pressure chamber 1507 for introducing gas in the middle of compression via
Square ring (sealing member)
The annular ring (seal member) 1505e is made of a synthetic resin or a metal material, and the seal sliding contact surface is sealed by the gas pressure guided to the bottom of the concave groove 1550. (JP-A-61-169686).

Further, as shown in FIGS. 30 to 33, the second means is a communication hole 1 formed in the end plate (flat portion) 1630 of the orbiting scroll 1623 from the compression chamber (compression space) 1625.
The high-pressure gas is guided to the high-pressure chamber 1635 provided on the anti-compression chamber side of the orbiting scroll 1623 through the 636, and the high-pressure receiving ring 162 is provided while the orbiting scroll 1623 is provided on the back surface.
9 to support the orbiting scroll 1623
The seal sliding contact surface 16
An annular oil groove 1644 provided in 41c and a cut (notch) 1
The annular rings (elastic seal rings) 1637a and 1637b having the holes 642a and 1642b are arranged, and the annular rings (elastic seal rings (1
637a and 1637b are provided with seal sliding surfaces, and
The lubricating oil in the high-pressure gas accumulated in the oil groove 1644 is used for the high-pressure chamber 1
A low pressure side space 1698 disposed inside and outside the 635;
It is a structure that seals with 1699 (actual opening 61-12)
No. 8396).

However, in order to prevent the compression efficiency from lowering, the above two sealing means do not allow the gas in the middle of compression introduced from the compression chamber to leak to the low pressure side. And lack of cooling. As a result, during sliding operation of the compressor for a long time, the sliding surface of the seal is abnormally worn, and the sealing function of the annular ring is reduced, the frictional resistance of the sliding portion is increased, and the function of the annular ring is lost. Was.

In the first means, since the annular ring (seal member) 1505e is made of synthetic resin, the annular ring (seal member) 1505e thermally expands due to a rise in temperature during operation of the compressor. A gap is formed between the inner surface of the concave groove 1550 and the inner surface of the annular ring (seal member) 1505e, and the annular ring (seal member) 1505 is formed.
There is also a problem that the sealing performance between the groove e and the recessed groove 1550 is impaired.

Further, in the above-described second means, the annular oil groove 1644 provided on the seal sliding contact surface 1641c communicates with the cuts (notches) 1642a and 1642b, and the lubricating oil in the annular oil groove 1644 is removed. Cut (notch) 1642a, 16
Since the gas flows out to the low pressure side of the outer peripheral portion via 42b, there is a problem that the sealing performance of the seal sliding contact surface is deteriorated, and it has been desired to realize an annular ring seal structure that can withstand practical use.

An object of the present invention is to solve such a conventional problem, and an object of the present invention is to provide a structure of a refueling passage for improving the airtight durability of an annular ring defining a rear surface of an orbiting scroll.

[0023]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a seal for an annular ring which is arranged to partition a high-pressure oil chamber provided on the back of a central portion of an orbiting scroll and an outer peripheral portion of the oil chamber. The sliding surface is a pressure reducing passage in a differential pressure oil supply passage to one of the compression chamber and the suction chamber.

Since the lubricating oil passes through the seal sliding surface of the annular ring, the pressure reducing passage can be formed by simple means, thereby improving the durability of the seal sliding surface of the annular ring and stably maintaining the lubricating oil pressure in the oil chamber. Can be.

[0025]

DETAILED DESCRIPTION OF THE INVENTION According to the first aspect of the present invention, the wrap support disk of the orbiting scroll is provided between the end plate of the fixed scroll and the thrust bearing provided on the main body frame supporting the drive shaft. The sliding surface is arranged so as to have at least a minute gap capable of forming an oil film. The sliding surface is arranged on the anti-compression chamber side of the orbiting scroll and inside the thrust bearing, and is adjacent to the lap support disk and connected to the drive shaft. A discharge chamber oil reservoir disposed in a lower part of a motor chamber which communicates with a discharge port and which is disposed in an oil chamber which is partitioned and provided adjacent to a orbiting bearing sliding portion and a main bearing engaged with the orbiting scroll. In a configuration having a passage for supplying the lubricating oil of the discharge chamber in a state where the discharge pressure acts thereon and supplying the lubricating oil of the discharge chamber oil reservoir to the main bearing, the swivel bearing and the compression space, For slewing bearings Between the oil chamber of the discharge chamber and the oil chamber by the screw pump action of the helical oil groove provided on the bearing sliding part of the drive shaft in the oil chamber and the pump action of the positive displacement pump device driven by the drive shaft. The oil is supplied to the oil chamber to supply the main bearing and the slewing bearing, and then most of the lubricating oil supplied to the oil chamber is returned to the discharge chamber oil sump while the remaining oil is supplied to the oil chamber. Either the first compression chamber or the suction chamber intermittently communicating with the suction chamber via the thrust bearing, the locking portion of the rotation preventing member, and the sliding surface between the end plate and the lap support disk by reducing the pressure of the lubricating oil. While the differential pressure oil supply passage to be supplied to either side is formed, the lap support disk is supported by the thrust bearing at the time of low speed operation including the initial stage of compressor startup and when the pressure in the compression chamber rises abnormally, and at least during the rated load operation. The orbiting scroll is supported by the end plate. As a throttle passage means for setting the back pressure applying force to the orbiting scroll by the lubricating oil supplied to the compression side and depressurizing the lubricating oil and supplying it to the thrust bearing, a space between the oil chamber and the outer peripheral portion of the oil chamber is provided. An annular ring is arranged between the lap support disk and the main body frame to partition, and an annular seal groove for mounting the annular ring in a loose state is arranged on one of the lap support disk and the main body frame, Of the minute gap between the outer surface of the annular seal groove and the annular ring and the seal sliding contact surface of the annular ring, at least the seal sliding contact surface of the annular ring is passed. According to this configuration, sufficient lubricating oil is supplied to the bearing portion of the drive shaft, and the axial contact force between the orbiting scroll and the fixed scroll is small, so that the amount of oil supplied to the sliding contact portion of the orbiting scroll can be reduced.

Further, when the lubricating oil in the oil chamber passes through the seal sliding contact surface of the annular ring under reduced pressure, lubrication of the seal sliding contact surface and stabilization of the depressurizing action on the seal sliding contact surface are achieved. After lubricating the thrust bearing and the rotation preventing member arranged on the outer peripheral portion of the compression chamber, it is finally used for sealing the oil film in the gap of the compression chamber.

According to a second aspect of the present invention, the lubricating oil on which the discharge pressure acts is reduced and supplied to the thrust bearing, the locking portion of the rotation preventing member, and the sliding surface between the end plate and the lap support disk. Is added to the differential pressure oil supply passage. According to this configuration, it is possible to supplement the variation of the differential pressure oil supply amount through the seal sliding contact surface of the annular ring, and to stabilize the entire differential pressure oil supply amount.

According to a third aspect of the present invention, another differential pressure oil supply passage is provided with an oil passage having a throttle passage communicating between an oil chamber communicating with the swivel bearing and a space in which the rotation preventing member is disposed. It is configured. According to this configuration, the lubricating oil in the oil chamber passes through the two-system simple-structured differential pressure oil supply passage,
It is effectively supplied to the sliding contact portion of the orbiting scroll, and contributes to stable airtight maintenance and lubrication of the seal portion.

According to a fourth aspect of the present invention, the throttle passage is formed by mounting and fixing the orbiting bearing in a bearing mounting hole provided in the orbiting scroll, and making one surface of a cylindrical outer peripheral portion of the orbiting bearing flat. It is a thing. According to this configuration, the lubricating oil in the oil chamber passes through the throttle passage with little variation, whereby stable differential pressure lubrication is performed, and an excessive or insufficient lubrication amount is avoided.

According to a fifth aspect of the present invention, the annular ring is formed so that the outer peripheral surface of the annular ring is expanded by the differential pressure between the inner oil chamber and the outer back pressure chamber and is brought into close contact with the outer surface of the annular seal groove. In the configuration in which the cutout is provided, the annular ring has flexibility. According to this configuration, the entire circumference of the outer surface of the annular ring is uniformly and closely contacted with the outer surface of the annular seal groove by the lubricating oil pressure of the annular ring, and the sealing performance of the closely contact portion is improved.

According to a sixth aspect of the present invention, the annular ring has a larger coefficient of thermal expansion than the member accommodating the annular ring. According to this configuration, as the differential pressure between the suction pressure and the discharge pressure increases, the compressor load increases, the thermal expansion of the annular ring also increases, and the cut portion of the annular ring is closed.

According to a seventh aspect of the present invention, a discontinuous annular oil groove that does not communicate with the cut is provided on the sliding surface of the annular ring. According to this configuration, a part of the lubricating oil passing through the sliding contact surface of the annular ring is captured by the discontinuous annular oil groove, and the oil film reduces the amount of gas flowing into the lubricating oil and stabilizes the oil. To

According to the invention described in claim 8, the annular ring increases in flexibility as the temperature rises. According to this configuration, as the differential pressure between the suction pressure and the discharge pressure increases, the sealing performance of the annular ring is stabilized.

[0034]

【Example】

(Embodiment 1) Hereinafter, a scroll refrigerant compressor according to a first embodiment of the present invention will be described with reference to FIGS.

In FIG. 1, reference numeral 1 denotes an iron sealed case.
The fixed scroll 15, the inside of which meshes with the orbiting scroll 18 to form a compression chamber, is bolted and the drive shaft 4
Is divided into an upper motor chamber 6 and a lower accumulator chamber 46 by the main body frame 5 supporting the motor.

The motor chamber 6 is in a high-pressure atmosphere. The main body frame 5 that supports the drive shaft 4 having the motor 3 at the upper part and the compression part at the lower part and the rotor 3a of the motor 3 connected and fixed thereto has sliding characteristics and welding characteristics. It is made of eutectic graphite cast iron having excellent heat resistance, and a protrusion 79a provided on the outer peripheral surface thereof is in contact with the inner wall surface and the end surface of the upper sealed case 1a and the lower sealed case 1b. Sealed case 1a and lower sealed case 1
and b are hermetically welded by a single welding bead 79b.

The drive shaft 4 includes an upper bearing 11 provided at the upper end of the main body frame 5, a main bearing 12 provided at the center,
A orbiting scroll 18 is provided with a crankshaft 14 at a lower end portion, which is provided on an upper end surface of the main body frame 5 and is supported by a thrust bearing portion 13 having a plurality of radially shallow grooves 7 and is eccentric from the main shaft of the drive shaft 4. It is engaged with the turning bearing 18b of the turning boss 18e.

The fixed scroll 15 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 15a as shown in FIG. 15b, and a fixed scroll wrap 1 is provided at the center of the end plate 15b.
The discharge port 16 opening at the winding start portion of the motor chamber
A suction chamber 17 is provided on the outer periphery of the fixed scroll wrap 15a.

On the end plate 15b on the anti-orbiting scroll side,
A check valve device 50 is attached so as to cover the discharge port 16, and the check valve device 50 is formed of a thin steel plate having a shape in which the outer peripheral portion is cut out at several places as described in detail in FIGS. 3 to 6. A valve case 99 having a valve body 50b (or a valve body 50e having a discontinuous annular hole 50ea), a check valve hole 50a, a central hole 50g, and a plurality of small discharge holes 50h around the valve hole 99a.
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.
It has a shape memory characteristic that expands below. During operation of the compressor, it receives the refrigerant gas pressure and shrinks to the bottom of the check valve hole 50a, and stops the compressor when its own temperature is 50 ° C or less. The inside is set so as to press the valve body 50 against the end plate 15b so as to close the discharge port 16.

As shown in FIGS. 1 and 14, a spiral scroll wrap 18a meshing with the fixed scroll wrap 15a to form a compression chamber side wall, and a rotary boss 18e engaged with the crankshaft 14 of the drive shaft 4. The orbiting scroll 18 made of an aluminum alloy, which is composed of a lap supporting disk 18c having a vertical upright, is disposed so as to be surrounded by the fixed scroll 15 and the main body frame 5, and the lap supporting disk 1
The surfaces of 8c and the orbiting scroll wrap 18a are subjected to hardening treatment such as porous nickel plating. As shown in FIG. 3, a spiral tip seal groove 98 is provided at the tip of the orbiting scroll wrap 18a, and a resin tip seal 98a is mounted in the tip seal groove 98 with a small gap. I have. When the orbiting scroll 18 is pressed in the axial direction of the fixed scroll 15, the flat portion of the wrap support disk 18c contacts the tip of the fixed scroll wrap 15a, but the tip of the orbiting scroll wrap 18a does not A minute distance of about a micron is maintained.

The discharge passage 80 (see FIG. 1) is provided in the fixed scroll 15 and the discharge chamber 2 formed by the discharge cover 2a mounted on the end plate 15b and the end plate 15b so as to cover the check valve device 50. Gas passage B80b, gas passage A80a provided in main body frame 5, main bearing 12
, A discharge guide 81 attached to the main body frame 5 so as to surround the main body frame 5, and a discharge chamber 2b formed by the main body frame 5, the gas passage A80a and the gas passage B8.
0b is provided at each target position (see FIG. 14).

On the upper surface of the discharge guide 81, as shown in FIG.
Many small holes 81a are provided.

The accumulator chamber 46 communicating with the evaporator side of the refrigerating cycle is formed by the lower sealed case 1b, the fixed scroll 15, and the main body frame 5, and a suction pipe 47 communicating therewith is provided on a side surface of the lower sealed case 1b. Two suction holes 43 are provided in the fixed scroll 15 at positions separated by about 90 degrees from the position facing the suction pipe 47 (see FIG. 14).

The low-pressure oil reservoir 46a at the bottom of the accumulator chamber 46 communicates with the suction hole 43 via an oil suction hole A9a provided on the discharge cover 2a and a small-diameter oil suction hole B9b provided on the fixed scroll 15. The oil suction holes (9a, 9b) are set so that the refrigerant liquid and the lubricating oil accumulated in the low-pressure oil reservoir 46a are sucked up by the generation of negative pressure when the refrigerant gas passes through the suction holes 43. I have.

A plate-shaped thrust bearing 20 which is restricted in movement in the rotational direction by a split pin-shaped parallel pin 19 fixed to the main body frame 5 and is movable only in the axial direction is provided.
The main body frame is disposed between the lap support disk 18c and the main body frame 5 by the elastic force of an annular seal ring (made of rubber) 70 (see FIG. 10) interposed between the thrust bearing 20 and the main body frame 5. 5 and the fixed scroll 15 are in contact with the end plate mounting surface 15b1.

The wrap support disk 18 of the orbiting scroll 18
c from the sliding surface 15b2 of the head sliding on
The height up to 5b1 is set to be approximately 0.015 to 0.020 mm larger than the thickness of the lap support disk 18c in order to improve the sealing property of the sliding portion by the oil film of the lap support disk 18c.

As shown in FIGS. 1 and 8, an annular seal groove 95 concentric with the center of the orbital bearing 18b is provided on the end face of the orbiting boss 18e of the orbiting scroll 18 on the body frame 5 side. As shown in FIG. 9, a flexible resin annular ring 94 having a cutout 94b is attached to the 95, as shown in FIG. Annular ring 9
The outer peripheral surface of the annular ring 94 is in close contact with the side surface of the annular seal groove 95 due to the thermal expansion of the annular ring 94 and the lubricating oil pressure inside the annular ring 94 during the operation of the compressor. Are arranged so as to be in close contact with each other. The annular ring 94 seals between the back pressure chamber 39 of the orbiting scroll 18 formed by the orbiting scroll 18, the main body frame 5 and the thrust bearing 20 and the oil chamber A 98 a on the main bearing 12 supporting the drive shaft 4. This prevents excessive leakage from the oil chamber A98a to the back pressure chamber 39.

The annular thrust bearing 20 is made of a sintered alloy whose hole can be easily formed. As shown in FIGS. 10 and 11, the two guide holes 93 into which the split pins 19 are movably inserted and the annular oil groove 9 are formed.
It has an oil hole 91 and is mounted in the thrust ring groove 90 of the main body frame 5.

A release gap 27 of about 0.05 mm is provided between the main body frame 5 and the thrust bearing 20, and a seal ring 7 is provided inside and outside the release gap 27.
0 is provided in the annular groove 28. The seal ring 70 seals between the release gap 27 and the back pressure chamber 39.

The release gap 27 is formed by the thrust back pressure introducing hole A89a provided in the main body frame 5 and the thrust back pressure introducing hole B89b provided in the fixed scroll 15 in the third compression chamber 60b (FIG. 14) in the final compression stroke. See also).

As shown in FIGS. 1 and 2, the thrust bearing 2
The rotation preventing member (hereinafter referred to as the Oldham ring) 24 of the orbiting scroll 18 disposed inside the inner ring 0 is made of a light alloy or a reinforcing fiber composite material suitable for sinter molding, injection molding, or the like. A key portion having a parallel key shape orthogonal to each other is provided on both surfaces. The key portion on the upper surface is provided in a key groove 71a provided in the main body frame 5, and the key portion on the lower surface is provided in a lap support disk 18c. It engages with the groove 71 and slides.

The thickness of the ring of the Oldham ring 24 is set such that the Oldham ring 24 slides smoothly between the main frame 5 and the lap support disk 18c and does not cause a jumping phenomenon when the Oldham ring 24 reciprocates. I have.

The discharge pipe 31 is mounted on the outer peripheral portion of the upper end wall of the upper sealed case 1a, and a glass terminal 88 for connecting a motor power supply is mounted on the central portion.

An oil separator 87 attached to the upper sealed case 1a separates the side of the discharge pipe 31 and the glass terminal 88 from the side of the motor 3. The rotor 3a of the motor 3, which is positioned in the axial direction by the stepped portion of the drive shaft 4, is bolted to the drive shaft 4 together with the upper balance weight 75, and the upper balance weight 75 has a disk shape, and its outer diameter is rotating. It is set larger than the outer diameter of the child 3a.

Between the lower balance weight 76 attached to the lower end of the rotor 3a and the discharge guide 81, a shielding plate 86 attached to the main frame 5 is arranged close to the lower balance weight.

The discharge chamber oil reservoir 34 provided in the lower part of the motor chamber 6 is communicated with the upper part of the motor chamber 6 by a cooling passage 35 provided by cutting out a part of the outer periphery of the stator 3b of the motor 3. .

Further, the discharge chamber oil sump 34 is
The oil chamber A78a is located at an intermediate position between the main bearing 12 and the slewing bearing 18b via an oil hole A38a provided in the main shaft 12a.

As shown in FIGS. 1 and 8, on the sliding shaft portion 4a of the drive shaft 4 and the surface of the crankshaft 14, when the drive shaft 4 rotates forward, the lubricating oil in the oil chamber A78a is provided with the slewing bearing 18b.
The oil chamber B78b formed by the oil pump and the crankshaft 14 and the helical oil groove 41 in the direction in which the screw pump oil is supplied to the motor 3 side.
a, 41b are provided, the upper end of which is the thrust bearing 1
It has reached three.

The oil chamber B78b and the surface of the main bearing 12 correspond to the drive shaft 4
The oil reservoir 72 and the back pressure chamber 39 between the upper bearing 11 and the main bearing 12 communicate with each other through an oil supply hole 73a provided in the main body frame 5. The oil hole B has a throttle passage portion provided in the main body frame 5.
38b, and the opening end of the oil hole B38b on the back pressure chamber 39 side is a discontinuous oil groove 94 provided in the annular ring 94.
a is intermittently opened, and is provided at a position intermittently opened and closed by an annular ring 94.

As shown in FIGS. 1, 10, and 14, the back pressure chamber 39 is provided with the first compression chamber 6 which intermittently communicates with the suction chamber 17.
1a and 61b are approximately 180 degrees before the suction refrigerant gas is completely confined.
The oil hole 91 provided in the thrust bearing 20 and the outer peripheral space 3 outside the lap support disk 18c within the turning angle range of degrees.
7, an oil hole C38c provided in the lap support disk 18c,
Small-diameter injection holes 52 arranged at symmetric positions
a, 52b
4 communicates with the first compression chambers 61a and 61b,
The oil hole 91 provided in the thrust bearing 20 is opened and closed intermittently by the lap support disk 18c.

As shown in FIGS. 12 and 13, a back pressure control valve device 25 for controlling the pressure of the back pressure chamber 39 is mounted on the lap support disk 18c.

The back pressure control valve device 25 is provided with the lap supporting disc 1
8c is a stepped cylinder 2 which is provided in the radial direction and comprises a large-diameter cylinder 26a and a small-diameter cylinder 26b.
6, a stepped plunger 29 movable in the cylinder, a cap 32 for closing a part of an opening end on the outer peripheral space 37 side of the cylinder 26, a cap 32 and the plunger 2
9 and the plunger 29 and the crankshaft 1
Coil spring 53 biasing to the side of 4 and large diameter portion cylinder 26
The oil hole 5 for communicating the suction shaft 17 with the crankshaft 14 side of FIG.
4a, an oil hole 5 for communicating the crankshaft 14 side of the small diameter portion cylinder 26b with the oil chamber B78b and the back pressure chamber 39, respectively.
4b and 54c. The operation is performed when the pressure in the back pressure chamber 39 is within an appropriate range, as shown in FIG.
When the small-diameter end face of the plunger 29 closes the cylinder-side opening end of the oil hole 54b and the pressure in the back pressure chamber 39 is insufficient, as shown in FIG. The plunger 29 moves toward the outer peripheral space 37 due to the biasing force acting on both sides of the oil hole 54.
The biasing force of the coil spring 53 and the dimensions of each part of the cylinder 26 are set so that the cylinder-side opening end of b is opened, and the oil chamber B78b and the back pressure chamber 39 communicate with each other.

Reference numeral 55 denotes an O-ring mounted on the small-diameter portion cylinder 26b for sealing the small-diameter outer peripheral portion of the plunger 29.

In FIG. 15, the horizontal axis indicates the rotation angle of the drive shaft 4, the vertical axis indicates the refrigerant pressure, the pressure change state of the refrigerant gas in the suction, compression and discharge processes, and the solid line 62 indicates the normal operation at normal pressure. The dotted line 63 shows the pressure change when the abnormal pressure rises.

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

In FIG. 1 to FIG. 15, when the drive shaft 4 is driven to rotate by the motor 3, the orbiting scroll 18 tries to rotate around the main axis of the drive shaft 4 by the crank mechanism of the drive shaft 4. The key portion (see FIG. 2) on the side of the orbiting scroll 18 is
Since the key portion 71 of the main frame 5 is engaged with the key groove 71a of the main body frame 5 (see FIG. 1), the rotation is prevented and the orbital motion is made. To perform the suction / compression action of the refrigerant gas.

Then, from the refrigerating cycle connected to the compressor, the suction refrigerant of the gas-liquid mixture containing the lubricating oil flows into the accumulator chamber 46 from the suction pipe 47 and the fixed scroll 1
After colliding with the outer surface of the end plate 15b, the air flows into the suction chamber 17 through two suction holes 43 (see FIG. 14) through the space above the accumulator chamber 46.

On the other hand, the liquid refrigerant and the lubricating oil separated from the refrigerant gas due to 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 46, 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, and is again mixed into the suction refrigerant gas.

The suction refrigerant gas separated into gas and liquid is supplied to the suction chamber 1
7. Enclosed in the compression chamber via first compression chambers 61a, 61b (see FIG. 14) formed between the orbiting scroll 18 and the fixed scroll 15, and the second compression chambers 51a, 51
b, after sequentially transferring and compressing to the third compression chambers 60a and 60b,
The gas is discharged from the central discharge port 16 to the check valve chamber 50a, the discharge chamber 2, the gas passage B80b, the gas passage A80a,
The liquid is discharged to the motor chamber 6 via the discharge chamber 2b sequentially.

Immediately after the completion of compression, the third compression chambers 60a, 60b
When the compressed refrigerant gas flows into the check valve chamber 50a from the third compression chambers 60a and 60b, the compressed refrigerant gas undergoes rapid primary expansion, and the compression completion stroke starts immediately after the discharge completion stroke. During this time, the refrigerant gas discharged from the check valve chamber 50a temporarily flows back to the third compression chambers 60a and 60b.

As a result, the refrigerant gas intermittently flows out of the third compression chamber (60a, 60b).
While repeatedly flowing into the discharge chamber 60b), the refrigerant flows out of the third compression chamber (60a, 60b) into the discharge chamber 2 as a whole flow, and 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 out toward the spherical wall surface constituting the discharge chamber 2 through the small discharge hole 50h of the check valve device 50, and further collides with the spherical wall surface to be uniform. Spread. Thereafter, the two discharge passages 80 disposed at further symmetrical positions are merged in the discharge chamber 2b and the motor chamber 6, so that the pulsation of the discharge gas from each discharge passage 80 is attenuated. Due to the fourth-order expansion, the pressure is further attenuated, and the pressure in the motor chamber 6 hardly changes.

When the discharged refrigerant gas instantaneously flows backward from the discharge chamber 2 to the check valve chamber 50a, the valve body 50b attempts to move in the direction of closing the discharge port 16 following the flow. During operation of the machine, the coil spring 50c having the shape memory characteristic is completely contracted due to the ambient temperature and does not exert an urging force on the valve body 50b, and the magnetic valve body 50b is attracted to the bottom surface of the check valve chamber 50a. And the valve body 50b
Does not block the discharge port 16.

The refrigerant gas discharged from the small holes 81a of the discharge guide 81 and discharged into the motor chamber 6 is supplied to the annular closing plate 8a.
6. After colliding with the windings of the motor 3, it flows to the upper side of the motor chamber 6 while cooling the motor 3 through the cooling passage 35 on the outside of the stator 3 b and the passage on the inside of the stator 3 b. To the refrigeration cycle.

At this time, a part of the lubricating oil in the discharged refrigerant gas adheres to the surface of the lower winding of the motor 3 and is separated from the refrigerant gas and collected in the discharge chamber oil reservoir 34. The lubricating oil in the discharged refrigerant gas passing through the outer periphery of the weight 75 and the lower balance weight 76 is centrifugally separated by the rotation of the upper balance weight 75 and the lower balance weight 76 and diffused to the inner surface of the winding of the motor 3. ,
It flows down to the lower part along the internal space of the winding bundle,
Collect at 4.

The release gap 27 on the back side of the thrust bearing 20, which communicates with the compression chamber in the final compression stroke (the compression space immediately before the compression chamber communicates with the discharge port 16), is filled with high-pressure refrigerant gas as time elapses after the start of compression. Is done. The thrust bearing 20 is pressed against the end plate mounting surface 15b1 of the fixed scroll 15 by the back pressure and the elastic force of the seal ring 70. Thereby, the lap support disk 18c of the orbiting scroll 18 is held between the end plate sliding surface 15b2 and the thrust bearing 20 (an assembly gap of 15 to 20 microns).

The lubricating oil in the discharge chamber oil reservoir 34 flows into the oil chamber A 78a, the oil chamber B 78b, and the back pressure chamber 39 via a path described later, and the back pressure applying force to the orbiting scroll 18 gradually increases.

Following the rise in the pressure in the motor chamber 6, the lap support disk 18c gradually comes into contact with the end plate sliding surface 15b2 of the fixed scroll 15 with an appropriate pressing force. There is no gap between the tip of the fixed scroll wrap 15a and the wrap support disk 18c of the orbiting scroll 18, whereby the compression chamber is sealed, the suction refrigerant gas is efficiently compressed, and stable operation is continued.

The axial gap between the end of the orbiting scroll wrap 18a and the end plate 15b of the fixed scroll 15 is provided with a tip seal groove 98 (see FIG. 4) when the refrigerant gas during compression leaks to the adjacent low pressure side compression chamber. 3), and the tip seal 98a is pressed against the side face of the low compression chamber of the tip seal groove 98a and the end plate 15b of the fixed scroll 15 by the gas back pressure to be sealed.

When the compressor is stopped, the orbiting scroll 18 instantaneously makes a reverse orbiting motion due to the reverse flow based on the pressure difference of the refrigerant gas in the compression chamber.
7, the orbiting scroll 18 stops at the orbital angle where the first compression chambers 61a and 61b communicate with the suction chamber 17, as shown in FIG. As shown in FIG. 8, in this stopped state, the annular ring 94 blocks the lubricating oil inflow port to the back pressure chamber 39.

When the compressor is stopped, the refrigerant gas in the compression chamber flows back into the suction chamber 17 so that the pressure of the refrigerant gas in the discharge port 16 drops sharply. 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 18, the magnetic valve element 50b is separated from the bottom surface of the check valve chamber 50a, and the refrigeration cycle is pressure-balanced. Until the pressure difference, the valve element 51b keeps closing the discharge port 16. At the same time, the temperature of the coil spring 50 having the shape memory characteristic decreases and the coil spring 50 expands.
b keeps closing the discharge port 16.

The first compression chambers 61a and 61b intermittently communicating with the suction chamber 17 and the back pressure chamber 39 are formed by the first compression chambers 61a and 61b.
Only when 1b is within 180 degrees before the closing is completed, it communicates with the thrust bearing 20 through the oil hole 91 (see FIG. 10), and between the thrust bearing 20 and the lap support disk 18c. Since it is sealed by the lubricating oil film, the refrigerant gas does not flow backward from the compression chamber to the back pressure chamber 39 during compression.

When the compressor is stopped for a long time, the pressure in the compressor is balanced, and the liquid refrigerant flows into the accumulator chamber 46 as well as into the compression chamber. A thrust force in the direction opposite to the discharge port 16 acts on the orbiting scroll 18 by the pressure of the liquid compressed refrigerant in the compression chamber. As a result, the orbiting scroll 18 is separated from the fixed scroll 15 in the axial direction, and the compression load is reduced.

On the other hand, the pressure in the back pressure chamber 39 at the initial stage of the start of the cold operation of the compressor is substantially equivalent to the suction pressure because the pressure rise of the lubricating oil in the discharge chamber oil reservoir 34 is low. As a result, the lap support disk 18c of the orbiting scroll 18 is in the oil chamber A where the pressure rise is low.
In a state where the back pressure is applied only by the lubricating oil of 78a, the thrust bearing 20 is retracted and supported away from the end plate sliding surface 15b2, and a gap (approximately) is provided between the lap support disk 18c and the tip of the fixed scroll wrap 15a. 0.015-0.
020 microns), lowering the compression chamber pressure and reducing the initial compression load.

In the event that liquid compression or the like occurs in the compression chamber and the pressure of the compression chamber rises abnormally instantaneously during continuous operation, the thrust force acting on the orbiting scroll 18 is applied to the back of the orbiting scroll 18. The orbiting scroll 18 moves in the axial direction, and is supported by the thrust bearing 20. 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 39 includes a first compression chamber 61a,
An oil hole 9b provided in the thrust bearing 20 is provided within a swirl angle range of about 180 degrees before the suction refrigerant gas is completely confined.
Since it communicates with the outer peripheral space 37 via 1, liquid compression does not occur within this communication turning range.

Therefore, in any compressor operating state including the occurrence of liquid compression in the compression chamber, the backflow of the refrigerant gas in the compression chamber to the back pressure chamber 39 is avoided, and the reduction of the compression load is not hindered.

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 grooves 41 a and 41 provided on the drive shaft 4.
The oil is sucked into the oil chamber A78a via the oil hole A38a by the screw pump action of b.

Thereafter, a part of the lubricating oil is
The lubricating surface of the swing bearing 18b is lubricated while passing through the oil chamber B 78b and the oil supply hole 73a sequentially, and is supplied to the sliding surface of the main bearing 12 and sent out to the oil sump 72.

The lubricating oil supplied to the main bearing 12 by the helical oil groove 41a joins with the lubricating oil passing through the oil chamber B78b in the oil sump 72, and a part of the lubricating oil is turned into the oil hole B.
38b (see FIG. 8), the pressure in the throttle passage
After lubricating the sliding surfaces of the upper bearing 11 and the thrust bearing 13, the remaining lubricating oil is collected again in the discharge chamber oil reservoir 34.

The refrigerant gas in the motor chamber 6 is prevented from flowing back into the oil sump 72 by the lubricating oil passing through the upper bearing 11.

The refrigerant gas pressure discharged from the motor chamber 6 rises following the elapse of time after the start of the compressor when the compressor is cold, and the discharge chamber oil reservoir 34
The lubricating oil is also supplied to the oil chamber A7 by the pressure difference between the lubricating oil and the back pressure chamber 39.
The oil is supplied to the back pressure chamber 39 together with the screw pump action of the spiral oil grooves 41a and 41b. The pressure in the back pressure chamber 39 gradually increases, and a combined force with the lubricating oil pressure corresponding to the discharge pressure of the oil chamber A 78a acts on the lap support disk 18c of the orbiting scroll 18. As a result, the orbiting scroll 18 is fixed to the fixed scroll 15 by the refrigerant gas pressure in the compression chamber.
The thrust load acting to move away from is offset,
The thrust force acting on the orbiting scroll 18 is reduced.

Therefore, while the pressure increase in the motor chamber 6 after the start of the compressor in a cold state is low, the force exerted on the orbiting scroll 18 by the lubricating oil pressure in the oil chamber A 78a and the back pressure chamber 39 increases the refrigerant gas pressure in the compression chamber. Is smaller than the thrust load on the orbiting scroll 18 due to this. As a result, the orbiting scroll 18 separates from the fixed scroll 15, and is supported by the thrust bearing 20 which receives the elastic force of the seal ring 70 and the back pressure by the refrigerant gas introduced from the compression chamber in the final compression stroke.

When the differential pressure between the discharge pressure and the suction pressure exceeds the required pressure, the force applied to the orbiting scroll 18 by the lubricating oil pressure in the oil chamber A 78a and the back pressure chamber 39 causes the orbiting by the refrigerant gas pressure in the compression chamber. It becomes larger than the thrust load on the scroll 18. The orbiting scroll 18 is supported by the fixed scroll 15.

In an arrangement in which the center of the compression chamber, the center of the orbiting bearing 18e, and the center of the annular ring 94 are substantially coincident with each other, the annular ring 94 orbits together with the orbiting scroll 18, so that the inertial force at that time causes the orbital boss portion. 18
Attempts to jump out of the annular seal groove 95 provided in e. Further, the annular ring 94 includes the oil chamber A 78 a and the back pressure chamber 3.
9, the inner diameter is expanded, and the cutout 94b is closed together with the thermal expansion. By these actions, the annular ring 94 is pressed against the outer surface of the main body frame 5 and the annular seal groove 95, and lubricating oil is generated between the annular seal groove 95 and the annular ring 94 by the oil scraping action of the annular ring 94. The lubricating oil is pushed in and prevents excessive lubricating oil leakage from the oil chamber A 78a to the back pressure chamber 39.

Further, the annular ring 94 made of resin having excellent flexibility expands the inner diameter thereof along the outer surface of the annular seal groove 95 due to the pressure difference between the back pressure chamber 39 and the oil chamber A 78 a, thereby reducing the heat. Since the cutout 94b is closed together with the expansion and pressed against the outer surface of the annular seal groove 95, direct leakage between the two spaces is further reduced.

Incidentally, the annular ring 94 is formed by the oil film of the lubricating oil accumulated in the 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 5, wear and sliding resistance of the sliding surface are reduced.

During the normal operation of the compressor, the high-pressure oil chamber A 78a
The orbiting scroll 18 is provided with a back pressure on the fixed scroll 15 side by the lubricating oil pressure of the back pressure chamber 39 and the lubricating oil pressure of the back pressure chamber 39, and a suitable contact force is maintained between the lap support disk 18c and the end plate sliding surface 15b2. While sliding smoothly to minimize the axial clearance of the compression chamber.

The lubricating oil flowing into the back pressure chamber 39 intermittently flows into the outer peripheral space 37 through an oil hole 91 provided in the thrust bearing 20, and further flows into an oil hole C38c provided in the lap support disk 18c. The pressure is gradually reduced through the small-diameter injection hole 52 (see FIG. 14), and the first compression chamber 61a,
61b. The lubricating oil lubricates each sliding surface in the middle of the passage and seals the sliding gap.

The lubricating oil injected into the first compression chambers 61a and 61b merges with the lubricating oil flowing into the compression chamber (compression space) together with the suctioned refrigerant gas, and seals a minute gap between adjacent compression chambers with an oil film. The compressed refrigerant gas is discharged again to the motor chamber 6 through the discharge port 16 together with the compressed refrigerant gas while preventing the leakage of the compressed refrigerant gas and lubricating the sliding surfaces between the compression chambers.

In the oil supply path from the discharge chamber oil reservoir 34 via the back pressure chamber 39 to the first compression chambers 61a and 61b, the back pressure chamber 39 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 a cold state, or abnormal liquid compression occurs. In such a case, as described above, the orbiting scroll 1
8 separates from the fixed scroll 15 and the thrust bearing 20
Supported by

However, the thrust bearing 20 urged by the back pressure cannot support the abnormally increased compression chamber pressure load.
Retreating in the direction to reduce the release gap 27, the axial gap between the wrap support disk 18c of the orbiting scroll 18 and the tip of the fixed scroll wrap 15a of the fixed scroll 15 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 dashed line 63a in FIG.

When the orbiting scroll 18 is the fixed scroll 15
Is restricted to about 70 microns, so that an oil film remains in each gap between the sliding surfaces on both sides of the lap support disk 18c, and the outer peripheral space 37 and the suction chamber 17 communicate directly. The pressure change in the back pressure chamber 39 due to this is suppressed, and the compression load is instantaneously reduced.
Can return to the original position instantly, and stable operation resumes.

When the orbiting scroll 18 retreats toward the thrust bearing 20, the axial dimension between the tip of the orbiting scroll wrap 18a and the fixed scroll 15 also increases. Compressed refrigerant gas leakage hardly occurs from this portion because the compressed refrigerant gas is pressed to the fixed scroll 15 side.

On the other hand, the gap between the wrap support disk 18c of the orbiting scroll 18 and the tip of the fixed scroll wrap 15b of the fixed scroll 15 is enlarged, and compressed refrigerant gas leaks in the compression chamber, and the pressure in the compression chamber suddenly increases. descend.

Also, when foreign matter is caught in the axial gap between the orbiting scroll 18 and the fixed scroll 15, the thrust bearing 20 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 pressure in the compression chamber 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 2b are sequentially expanded while passing through the discharge chamber 2b, and the pressure in the motor chamber 6 hardly changes.

Further, as the operating speed of the compressor increases, the leakage of refrigerant gas in the compression chamber per unit time decreases. On the other hand, the injection holes 52a, 52 per one turning motion
b, the amount of oil injection into the compression chamber per one turning motion is suppressed, unnecessary oil compression is reduced, and the passage between the oil hole B38b and the back pressure chamber 39 is increased by the number of shutoffs. The resistance is increased, the amount of lubricating oil flowing into the back pressure chamber 39 from the oil chamber A 78a is suppressed, and the pressure in the back pressure chamber 39 is appropriately maintained.

Further, when the scroll refrigerant compressor incorporated in the heat pump refrigeration cycle and operating is switched from the heating operation to the defrosting operation, for a short time, the high pressure side becomes the evaporator and the low pressure side becomes the condenser side. Due to the connection, the pressure in the motor chamber 6 decreases instantaneously. Oil hole B following it
38b, the oil sump 72, and the oil chamber A78a sequentially reduce the pressure of the back pressure chamber 39 and the pressure of the outer peripheral space 37, which communicate with the motor chamber 6, while temporarily reducing the pressure of the suction chamber 17 and the compression chamber. If the back pressure rises and the proper back pressure cannot be maintained, the plunger 29 of the back pressure control valve device 25 provided on the lap support disk 18c as shown in FIG.
1 against the back pressure of the lubricating oil communicating with the coil spring 53 and the back pressure chamber 39 by the lubricating oil pressure of the oil hole 54b communicating with the oil hole 54b.
3 and move toward the outer peripheral space 37, and the oil chamber B78b
The high-pressure lubricating oil flows into the back pressure chamber 39, and the back pressure chamber 39 is returned to an appropriate pressure.
The plunger 29 is moved to the oil chamber B78b side as described above, and the oil chamber B78b and the back pressure chamber 39 are shut off.

When the heat load on the evaporator side is high and the condensation capacity on the condenser side is high, the operation is performed with the suction pressure relatively high and the discharge pressure relatively low.

In such a case, since the pressure in the compression chamber is higher than that in the normal operation, it is necessary to make the pressure in the back pressure chamber higher than usual. The lubricating oil pressure in the oil hole 54b communicating with the oil chamber B78b and the refrigerant pressure on the suction side communicating with the suction chamber 17 through the oil hole 54a resist the back pressure of the lubricating oil communicating with the coil spring 53 and the back pressure chamber 39. 13, the oil chamber B78b and the back pressure chamber 39 intermittently (or partially) communicate with each other, and the high-pressure lubricating oil flows into the back pressure chamber 3 as shown in FIG.
9 to maintain the back pressure chamber 39 at an appropriate pressure.

Of course, the plunger 29 is
Under the influence of the inertial force and the frictional force acting on the plunger 29, the communication area between the small-diameter portion cylinder 26b and the oil hole 54c is increased in an attempt to move toward the outer peripheral space 37. The pressure increases as the compressor operating speed increases.

In the above embodiment, the compressed refrigerant gas during the final compression stroke is introduced into the release gap 27 provided on the rear surface of the thrust bearing 20. However, the discharge gas in the region where the compression chamber and the discharge port 16 communicate with each other in the final compression stroke is discharged. Refrigerant gas may be introduced into the release gap 27.

In the above embodiment, the orbiting scroll 18
The sliding gap between the lap support disk 18c and the thrust bearing 20 was sealed only with an oil film of lubricating oil, but as disclosed in Japanese Patent Application No. 63-159996 by the inventor,
An annular ring (82) may be attached to the back side of the lap support disk 18c to improve the sealing performance of the sliding portion gap between the back pressure chamber 39 and the outer peripheral space 37.

In FIG. 8, the oil hole B38b and the back pressure chamber 3
9 are intermittently communicated with each other, the number of sections per one turning motion is set large. However, in the case of a compressor operating condition where the compression load is relatively small, the oil hole B38b and the back pressure chamber 39 per one turning motion are set. The opening position of the oil hole B38b is moved toward the center of the main body frame 5 so that the communication section is reduced, and the oil chamber A7 is closed.
It will be apparent from the description of the prior art that it is necessary to reduce the amount of the lubricating oil 8a flowing into the back pressure chamber 39 and the compression chamber. Accordingly, the pressure in the back pressure chamber 39 and the outer space 37 also decreases.

As described above, according to the above embodiment, during the period from the start of the compressor to the time when the compressor reaches the steady operation,
When the pressure in the compression chamber rises abnormally due to liquid compression or the like, the lap support disk 18c of the orbiting scroll 18 separates from the end plate 15b of the fixed scroll 15 and is supported by the thrust bearing 20, so that the rated load acts as in the case of steady operation. The high-pressure lubricating oil supplied to the oil chamber A 78a on the non-compression side of the orbiting scroll and the back pressure chamber 3 so as to be supported by the end plate 15b at times.
9, the back pressure applying force of the lubricating oil supplied under reduced pressure to the orbiting scroll 18 is set. Even when the load specification of the compressor is small, the arrangement of the oil chamber A78a is changed in accordance with the specification. By reducing the amount of oil supplied to the pressure chamber 39 and reducing the back pressure applying force, the orbiting scroll 18 can be operated as described above.

That is, the first compression chambers 61a, 61b passing through the back pressure chamber 39 on the side opposite to the compression chamber of the orbiting scroll 18
The amount of refueling to the (suction chamber 17) can be reduced.

As a result, a small amount of lubricating oil leaking through the seal sliding contact surface of the annular ring 94 can be allowed to lubricate the seal sliding contact surface of the annular ring 94. It is used as a lubricating oil passage to the chamber 39 and a simple lubricating oil depressurizing means, and it is possible to realize a reduction in friction loss and an improvement in durability of the seal sliding surface of the annular ring 94.

(Embodiment 2) FIG. 16 is a longitudinal sectional view of a scroll refrigerant compressor according to a second embodiment of the present invention. The scroll refrigerant compressor is provided in a discharge chamber oil reservoir 34 through an oil hole A 238a provided in a main body frame 205. A partitioning cap 101 made of a steel plate having an external shape as shown in FIG. 17 is press-fitted into the stepped inner wall of the high-pressure oil chamber A 278a, and covers the brim portion 102 of the drive shaft 204 as shown in FIG. It is arranged in a form. The cap 101 has a cut 101a in a part thereof, and the cut 101 is attached to the stepped inner wall of the oil chamber A278a.
a, the oil chamber A 278a is partitioned into the main bearing 212 side and the swing bearing 218b side.

The orbiting boss 218 of the orbiting scroll 218
e shows a slewing bearing 2 whose appearance is shown in FIG.
18b is press-fitted. Slewing bearing 21 having a cylindrical shape
A part of the outer peripheral portion of 8b is flattened, and the step C is set to about 100 microns. As shown in FIG. 19, the step C is formed by the turning boss 218e.
The throttle passage 103 is formed in a state in which the throttle passage 103 is press-fitted.

The turning boss 218e is provided with an annular groove 104 and a small-diameter oil hole 105. The discharge chamber oil reservoir 34 and the back pressure chamber 239 communicate with each other through an oil hole A 238a, an oil chamber A 278a, a spiral oil groove 241b, an oil chamber B 278b, a throttle passage 103, an annular groove 104, and an oil hole 105.

As shown in FIG. 20, the outer peripheral space 37 and the back pressure chamber 239 are connected to the thrust bearing 220 only when the first compression chambers 61a and 61b are within a turning angle range of about 180 degrees before the closing is completed. Through the shallow groove 291 provided on the surface of the orbiting scroll 218, so as to be cut off by the lap support disk 218c of the orbiting scroll 218 at other times.
Position 1 is set.

The other structure is the same as that of FIG.
Then, according to this embodiment, the pressure in the motor chamber 6 filled with the discharged refrigerant gas gradually increases with the lapse of time after the compressor is started.

The lubricating oil in the discharge chamber oil reservoir 34 at the bottom of the motor chamber 6 is provided on the main body frame 205 by the screw pump action of the spiral oil grooves 241a and 241b provided on the drive shaft 204, as in the case of FIG. The oil is sucked into the oil chamber A278a through the oil hole A238a. At this time, the partition cap 101 guides the lubricating oil to pass through the vicinity of the surface of the drive shaft 204 and flow into the oil chamber A 278a and the spiral oil groove 241b. As a result, the lubricating oil becomes oil hole A238a.
When the oil flows into the oil chamber A 278a, the oil is sucked into the spiral oil groove 241a without being affected by centrifugal diffusion caused by the high speed rotation of the drive shaft 204, and excellent screw pump oiling is performed.

The lubricating oil supplied to the oil chamber B 278b by the pressure difference between the discharge chamber oil reservoir 34 and the back pressure chamber 239 of the orbiting scroll 218 and the screw pump action of the spiral oil groove 241b passes through the orbital bearing in the middle of the passage. After lubricating the sliding surface of 218b, it flows into the back pressure chamber 239 via the throttle passage 103, the annular groove 104, and the oil hole 105.

On the other hand, the lubricating oil of the oil chamber A 278a is in contact with the back pressure chamber 2 of the seal ring between the oil ring A 278a and the main frame 205 of the annular ring 94 that separates the oil chamber A 278a from the back pressure chamber 239.
Lubricated by allowing micro leaks to 39,
The seal durability of the seal sliding contact surface and reduction of sliding friction loss are guaranteed.

Oil chamber A27 almost equal to the pressure of motor chamber 6
The lubricating oil 8a is divided into two parts: a throttle passage 103 which can be secured simply and as a precision throttle passage, a precision pressure reduction passage via an oil hole 105, and a sliding pressure reduction passage via a seal sliding contact surface of an annular ring 94. The pressure is supplied to the back pressure chamber 239 through the two pressure reducing passages. As a result, the differential pressure oil supply amount to the back pressure chamber 239 is stabilized, and the inside of the back pressure chamber 239 can be maintained at an appropriate pressure.

The lubricating oil in the discharge chamber oil sump 34 is
In addition to the screw pump action of 1b, the pressure is supplied to the sliding portion of the slewing bearing by the pressure difference between the back pressure chamber 239 and the amount of oil supplied to the back pressure chamber 239 can be stabilized.

A space between the outer peripheral space 37 and the back pressure chamber 239 is
As in the case of FIG. 1, since the fluid is communicated via the oil groove 291 provided on the surface of the thrust bearing 220, the lubricating oil in the back pressure chamber 239 is intermittently supplied to the outer peripheral space 37.

Thereafter, the lubricating oil is supplied to the compression chamber as in the case of FIG. 1, and is discharged again to the motor chamber 6 together with the compressed refrigerant gas, and is used for sealing the compression chamber gap in the process.

In the above-described embodiment, the annular ring 94 is provided in the annular seal groove 95 provided in the orbiting boss 218e of the orbiting scroll 218.
As described in Japanese Patent Publication No. 8396, when the annular seal groove and the annular ring are provided in the main body frame 205, the same operation as described above is performed.

(Embodiment 3) FIG. 21 is a longitudinal sectional view of a scroll refrigerant compressor according to a third embodiment of the present invention. In addition to the screw pump function shown in FIG. 1, a positive displacement pump device is provided at the tip of the drive shaft. 1 shows a configuration of a bearing lubrication that can be provided, and in particular, can maintain extremely low speed operation of a compressor.

That is, as shown in FIG. 16, a partition cap made of a steel plate is formed on the stepped inner wall of the high-pressure oil chamber A 378a which communicates with the discharge chamber oil reservoir 34 through the oil hole A 338a provided in the main body frame 305. 101 is press-fitted,
The oil chamber A 378a is disposed so as to cover the flange portion 102 of the drive shaft 304, and partitions the oil chamber A 378a into a main bearing 312 side and a swing bearing 318b side.

The orbiting boss 318 of the orbiting scroll 318
A swing bearing 318b is press-fitted in e, and a trochoid pump device 106 including an outer rotor 106a and an inner rotor 106b is mounted on the bottom thereof.

The trochoid pump device 106 is
4 is connected to and driven by a drive end shaft 107 provided at the end of the crankshaft 314 at the end of the fourth end. The crankshaft 314 and the drive end shaft 107 are concentric.

As shown in FIG. 23, between the slewing bearing 318b and the trochoid pump device 106, a suction hole 108 is provided.
And a partition plate 110 having a central hole 109 is fixedly mounted.

Wrap support disk 3 of orbiting scroll 318
The oil groove 111 provided at the central portion of 18c serves as a discharge port of the trochoid pump device 106.
The sliding surface of the main bearing 312 is in communication with an axial oil hole 112 and a radial oil hole 113 provided in the drive shaft 304.

The discharge chamber oil reservoir 34 and the back pressure chamber 339 of the orbiting scroll 318 are connected to an oil hole A338a, an oil chamber A378a,
Oil supply passage A communicating with the oil sump 72 via the spiral oil groove 341b, the suction hole 108, the trochoid pump device 106, the oil groove 111, the axial oil hole 112, the radial oil hole 113, and the bearing gap of the main bearing 312. And an oil supply passage C composed of an oil supply passage B which communicates with the oil sump 72 from the oil chamber A 378a via the spiral oil groove 341a, and an oil hole B38b.

Other structures are the same as those in FIG. 1, and the description is omitted. According to this embodiment, the oil hole A 338a and the oil chamber A 378 are operated from the extremely low speed operation at the initial stage of the compressor startup.
The lubricating oil in the discharge chamber oil reservoir 34 can be sucked in by the trochoid pump device 106 through a, and can be supplied to the sliding surface between the crankshaft 314 and the main bearing 312 in a required amount.

Accordingly, even when the pressure rise in the motor chamber 6 is small, the annular ring 94 is expanded outward by the lubricating oil pressure difference between the oil chamber A 378a and the back pressure chamber 339, and the cutout 94b of the annular ring 94 is formed. And annular ring 9
4 and the outer surface of the annular seal groove 95 can be sealed. Also, the lubricating oil leaks from the oil chamber A 378a to the back pressure chamber 39 in accordance with the pressure difference between the inside and outside of the seal sliding surface of the annular ring 94 to lubricate the seal sliding surface of the annular ring 94, and the anti-compression of the orbiting scroll 18 The amount of oil supplied to the first compression chambers 61a and 61b (the suction chamber 17) via the back pressure chamber 39 on the chamber side can be stabilized. As a result, extremely low speed operation for energy saving operation can be maintained.

(Embodiment 4) FIG. 24 is a longitudinal sectional view of a scroll refrigerant compressor according to a fourth embodiment of the present invention. The inside of a sealed case 801 made of soft iron is driven similarly to the case of FIG. An upper sealed case 801a and a lower sealed case 801b are partitioned by a main body frame 805 supporting a shaft 704. The inside of the upper sealed case 801a is a high-pressure space in which a motor 703 is built, and the lower sealed case 801
The inside of b constitutes an accumulator chamber 846 with a low-pressure space communicating with the downstream side of the evaporator.

The drive shaft 704 connecting the motor 703 is
Main bearing 812 of main body frame 805 and upper frame 12
6 and supported.

The discharge chamber 2 is connected to a high pressure side via a gas passage B 880b provided in the fixed scroll 815, a gas passage A 880a provided in the main frame 805, and a discharge chamber 2c formed by the main frame 805 and the discharge guide 81. Of the motor room 806.

The discharge pipe 831 provided at the upper end of the upper sealed case 801a communicates with the motor chamber 806 via a gas hole 129 provided in the upper frame 126.

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. The end faces of the coil springs 131 are pressed by a discharge guide 881 attached to the main body frame 805, and the thrust is reduced. 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 through 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.

The outer peripheral space 37 of the orbiting scroll 818
Communicates intermittently with the back pressure chamber 839 via the shallow groove 891 provided in the thrust bearing 220, and does not communicate with the first compression chambers 61a and 61b which intermittently communicate with the suction chamber 17,
The fixed scroll 815 communicates with the suction chamber 17 via an oil groove 899 provided on the sliding surface of the end plate 815b.

According to this embodiment, the back pressure chamber 83
9 holds a pressure close to the pressure of the suction chamber 17.

Therefore, the back pressure applying force to the orbiting scroll 818 acting on the fixed scroll 815 depends only on the lubricating oil pressure in the oil chamber A 878a.

According to this back pressure application mode, the wrap support disk 818c of the orbiting scroll 818 during the period from the start of the compressor to the steady operation, and when the pressure in the compression chamber rises abnormally due to liquid compression or the like. Moves away from the end plate 815b of the fixed scroll 815 and the thrust bearing 22
0 and the back pressure applied to the orbiting scroll 818 by the high-pressure lubricating oil supplied to the oil chamber A 878a on the anti-compression side of the orbiting scroll so as to be supported by the end plate 815b when the rated load is applied as in the steady operation. Power can be set.

As a result, between the orbiting scroll 818 and the fixed scroll 815, and between the orbiting scroll 8
By avoiding excessive axial contact between the shaft 18 and the thrust bearing 220, it is possible to prevent excessive compression, reduce compression input, and improve the durability of the sliding portion and the smooth startability.

It should be noted that the positive displacement pump device shown in FIG. 16 can be added to the end of the drive shaft 704 to maintain extremely low speed operation.

In the above embodiment, the main bearing 12 and the slewing bearing 18b are arranged adjacent to each other in the main shaft direction of the drive shaft 4. However, as shown in FIG. 26, an eccentric bearing portion disposed above the drive shaft 1417 is provided. A bearing configuration in which a revolving shaft 1424a provided on the anti-compression chamber side of the revolving scroll 1424 is engaged with the revolving scroll 1424, and further disclosed in Japanese Patent Application Laid-Open Nos.
As shown in Japanese Patent Application Laid-Open No. 3-205490, it is clear that the same operation and effect as described above can be expected even in the case of the configuration in which the slewing bearing is disposed inside the main bearing.

In the above embodiment, the refrigerant compressor has been described. However, similar effects can be expected in the case of other gas compressors using lubricating oil, such as oxygen and nitrogen, and liquid pumps such as refrigerant pumps.

In the above embodiment, the operation and effect of the vertical compressor are described.
The same operation and effect can be expected for the configuration of a horizontal compressor in which the upstream side of (38a and others) is the bottom side of the sealed case (1 and others).

[0159]

As is clear from the above embodiment, the invention according to claim 1 is characterized in that the orbiting scroll lap support disk is provided on a main body frame having a fixed scroll end plate and a main bearing for supporting a drive shaft. A configuration in which both sliding surfaces of the lap support disk are arranged so as to have at least a minute gap capable of forming an oil film between the bearing and the bearing, are arranged on the anti-compression chamber side of the orbiting scroll and inside the thrust bearing, and The discharge pressure acts on the lubricating oil in the discharge chamber oil reservoir that communicates with the discharge port on the oil chamber adjacent to the lap support disk and partitioned through the orbiting bearing sliding portion where the drive shaft and the orbiting scroll engage. In a configuration having a passage for supplying the lubricating oil of the discharge chamber oil reservoir to the main bearing, the swivel bearing and the compression space, the lubricating oil of the discharge chamber oil reservoir is driven into an oil chamber communicating with the swivel bearing. Axis rotation After supplying most of the lubricating oil, including the oil chamber and the supply passage to the oil chamber, to at least the main bearing, the oil is returned to the discharge chamber oil sump, while the oil chamber and the oil chamber are supplied to the oil chamber. The remaining lubricating oil in the lubricating oil including the supply path is depressurized to intermittently enter the suction chamber via the thrust bearing, the locking portion of the rotation prevention member, and the sliding surface between the head plate and the lap support disk. A differential pressure oil supply passage is provided to supply either one of the first compression chamber and the suction chamber that communicates with each other, and when the lap support disk is operated at low speed including the initial stage of compressor startup and when the pressure in the compression chamber rises abnormally, the thrust is increased. The back pressure is applied to the orbiting scroll by the pressure of the lubricating oil supplied to the anti-compression side of the orbiting scroll so that the lubricating oil is supplied to the orbiting scroll so as to be supported by the bearing and at least at the end plate during the rated load operation. Throttle to reduce pressure and supply to thrust bearing As a passage means, arranged an annular ring between the wrap support disk and the main frame in order to define between the outer peripheral portion of the oil chamber and the oil chamber,
An annular seal groove for mounting the annular ring in a loose state is provided on one of the wrap support disk and the main body frame, and a minute gap between the outer wall of the annular seal groove and the annular ring, and a seal sliding contact surface of the annular ring. , At least through the seal sliding contact surface of the annular ring. According to this configuration,
A sufficient amount of lubricating oil is supplied to the bearing portion of the drive shaft, and the axial contact force between the orbiting scroll and the fixed scroll is small, so that the amount of oil supplied to the back pressure chamber and the sliding contact portion of the orbiting scroll can be reduced. As a result, the seal sliding contact surface of the annular ring can be used as a reduced pressure oil supply passage from the oil chamber to the back pressure chamber in the outer peripheral portion, so that a differential pressure oil supply passage passing through the oil chamber can be configured, and the lubrication passage can be simplified. And the cost can be reduced.

In addition, since the lubricating oil in the oil chamber passes through the seal sliding contact surface of the annular ring, it is possible to improve the durability of the seal sliding contact surface and reduce the friction loss of the seal sliding contact portion.

Furthermore, by ensuring the reliability of the annular ring,
Prevents excessive flow of lubricating oil from the discharge chamber oil sump into the compression chamber, maintains lubricating oil pressure in the oil chamber, and reduces thrust force by applying proper back pressure to the orbiting scroll, reducing compressor input during normal operation and abnormally excessive compression. This has the effect of realizing the effect of reducing the load at the time.

According to a second aspect of the present invention, the lubricating oil to which the discharge pressure acts is reduced and supplied to the thrust bearing, the locking portion of the rotation preventing member, and the sliding surface between the end plate and the lap support disk. According to this configuration, it is possible to supplement the variation of the differential pressure lubrication amount through the seal sliding contact surface of the annular ring, and to stabilize the entire differential pressure lubrication amount. This has the effect of stabilizing machine performance and quality.

According to a third aspect of the present invention, another differential pressure oil supply passage is provided with an oil passage having a throttle passage communicating between an oil chamber communicating with the swivel bearing and a space in which the rotation preventing member is disposed. According to this configuration, since the lubricating oil in the oil chamber is stably supplied to the sliding portion of the rotation preventing member, the durability of the rotation preventing member can be improved. As a result, there is an effect that a reduction in compression efficiency can be prevented by preventing the expansion of the compression chamber gap and stably supplying oil to the compression chamber.

According to a fourth aspect of the present invention, the throttle passage is formed by mounting and fixing the orbiting bearing in a bearing mounting hole provided in the orbiting scroll and making one surface of a cylindrical outer peripheral portion of the orbiting bearing flat. According to this configuration, a throttle passage with high pressure reduction accuracy can be simply configured.

Further, there is an effect that the compression efficiency can be improved by supplying a stable appropriate amount of differential pressure oil to the back pressure chamber and the compression chamber.

According to a fifth aspect of the present invention, the annular ring is formed so that the outer peripheral surface of the annular ring is expanded by the pressure difference between the inner oil chamber and the outer back pressure chamber and is brought into close contact with the outer surface of the annular seal groove. The annular ring is made of a material having flexibility, and according to this configuration, the entire circumference of the outer surface of the annular ring is uniformly formed on the outer surface of the annular seal groove by the lubricating oil pressure of the annular ring. Since the seal is tightly contacted and the sealing property of the close contact portion is enhanced, it is possible to increase the proportion of lubricating oil leaking to the back pressure chamber via the annular ring to the seal sliding contact surface of the annular ring. As a result, there is an effect that the durability of the seal sliding contact surface of the annular ring can be improved, and the amount of oil supplied to the back pressure chamber via the annular ring can be stabilized.

According to a sixth aspect of the present invention, the annular ring is made of a material having a larger coefficient of thermal expansion than the member for accommodating the annular ring. Since the cut end is closed, the sealing performance of the annular ring is improved with an increase in compressor load,
There is an effect that a sealing function corresponding to a decrease in the viscosity of the lubricating oil can be exhibited.

According to the seventh aspect of the present invention, a discontinuous annular oil groove that does not communicate with the cut is provided in the sliding surface of the annular ring. According to this configuration, the oil passage passes through the sliding surface of the annular ring. Part of the lubricating oil is caught by a discontinuous annular oil groove, and the amount of gas blown into the lubricating oil can be suppressed by the oil film.
This has the effect of preventing a decrease in compression efficiency.

According to an eighth aspect of the present invention, the annular ring is made of a material that increases flexibility with an increase in temperature. According to this configuration, as the differential pressure between the suction pressure and the discharge pressure increases, Since the compression load increases and the sealing performance of the annular ring is improved following the rise in temperature, it is possible to stabilize the oil supply from the oil chamber to the compression chamber.

[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 sectional view for explaining the operation of the back pressure control valve device in the compressor.

FIG. 13 is a sectional view for explaining the operation.

FIG. 14 is a cross-sectional view taken along line AA in FIG. 1;

FIG. 15 is a characteristic diagram showing a change in pressure of refrigerant gas from a suction stroke to a discharge stroke of the compressor.

FIG. 16 is a longitudinal sectional view of a scroll refrigerant compressor showing another embodiment of the present invention.

FIG. 17 is a perspective view of a partition cap component in the compressor.

FIG. 18 is a perspective view of a bearing part of the compressor.

FIG. 19 is a partial cross-sectional view of a main bearing in the compressor.

FIG. 20 is a partial sectional view of a thrust bearing portion in the compressor.

FIG. 21 is a longitudinal sectional view of a scroll refrigerant compressor showing still another embodiment of the present invention.

FIG. 22 is a partial cross-sectional view of a main bearing in the compressor.

FIG. 23 is a perspective view of a partition plate used in the trochoid pump device in FIG. 23;

FIG. 24 is a longitudinal sectional view of a scroll refrigerant compressor showing still another embodiment of the present invention.

FIG. 25 is a longitudinal sectional view of a conventional scroll compressor.

FIG. 26 is a longitudinal sectional view of another conventional scroll compressor.

FIG. 27 is a transverse sectional view taken along line 3-3 in FIG. 26;

FIG. 28 is a longitudinal sectional view of a conventional scroll compressor.

FIG. 29 is a partial sectional view of another conventional example in FIG. 28;

FIG. 30 is a longitudinal sectional view of a conventional scroll compressor.

FIG. 31 is a partial cross-sectional view of another conventional example in FIG. 30;

FIG. 32 is a partial sectional view of the same.

FIG. 33 is a partial sectional view of the same.

[Explanation of symbols]

 Reference Signs List 1 sealed case 4 drive shaft 5 body frame 12 main bearing 15 fixed scroll 15b end plate 15a fixed scroll wrap 16 discharge port 17 suction chamber 18 orbiting scroll 18a orbiting scroll wrap 18c lap support disk 20 thrust bearing 24 rotation preventing member 34 discharge chamber oil reservoir 39 back pressure chamber 61a, 61b first compression chamber 78a oil chamber A 78b oil chamber B 94 annular ring 94a annular oil groove 94b cut end 95 annular seal groove 103 throttle passage 106 trochoid pump device 204 drive shaft 218 orbiting scroll 218b orbit bearing 239 Back pressure chamber 278a Oil chamber A 278b Oil chamber B 304 Drive shaft 318 Turning scroll 318b Turning bearing 339 Back pressure chamber 378a, 378b Oil chamber 804 Drive shaft 818 Turning scroll 818b Turning bearing 839 Back pressure Chamber 878a Oil chamber A 878b Oil chamber B

Claims (8)

(57) [Claims] An orbiting scroll wrap on a wrap supporting 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 the two scrolls, a discharge port is provided at the center of the fixed scroll wrap or the orbiting scroll wrap, and a suction chamber is provided outside the fixed scroll wrap. Is divided into a plurality of compression chambers which continuously shift from the suction side to the discharge side, and compresses the fluid, between the main body frame having a main bearing supporting the drive shaft at the center and the orbiting scroll. Forming a scroll compression mechanism for engaging the rotation preventing member of the orbiting scroll to orbit the orbiting scroll, and The motor connected to the drive shaft is housed in a closed case, and the lap support disk is formed between the end plate and the thrust bearing provided on the main body frame, and at least both sliding surfaces of the lap support disk can form an oil film. The orbiting scroll and the orbiting scroll are disposed on the anti-compression chamber side of the orbiting scroll and inside the thrust bearing, and are adjacent to the lap support disk, and the drive shaft and the orbiting scroll are arranged. A discharge chamber oil sump is provided in an oil chamber which is partitioned and disposed adjacent to the rotating bearing sliding portion to be engaged and the main bearing and communicates with the discharge port and is provided at a lower portion of a motor chamber which houses the motor. In a configuration having a passage for supplying lubricating oil in a state where discharge pressure acts and supplying lubricating oil for the discharge chamber oil reservoir to the main bearing, the swivel bearing portion and the compression space, Serial lubricating oil,
The discharge chamber is formed by a screw pump action of a helical oil groove provided in a bearing sliding portion of the drive shaft in the oil chamber communicating with the swivel bearing section, and a pump action of a positive displacement pump device driven by the drive shaft. The lubricating oil is supplied through an oil hole communicating between an oil reservoir and the oil chamber, and is supplied to the oil chamber so as to be supplied to the main bearing and the swivel bearing. While returning the portion to the discharge chamber oil sump, the remaining lubricating oil is depressurized and passes through the thrust bearing, the locking portion of the rotation preventing member, and the sliding surface between the end plate and the lap support disk. A differential pressure oil supply passage for supplying one of the first compression chamber and the suction chamber intermittently communicating with the suction chamber, wherein the lap support disk is operated at a low speed operation including an initial stage of compressor start-up and the compression operation. When the chamber pressure rises abnormally, the thrust The oil chamber forms a back pressure applying force to the orbiting scroll by the pressure of the lubricating oil supplied to the non-compression side of the orbiting scroll so as to be supported by a bearing and to be supported by the head plate at least during rated load operation. An annular ring between the lap support disk and the main body frame to define a space between the oil chamber and an outer peripheral portion of the oil chamber as a throttle passage means for reducing the pressure of the lubricating oil and supplying the reduced pressure to the thrust bearing. Is disposed, and an annular seal groove for mounting the annular ring in a loose state is provided in one of the lap support disk and the main body frame, and a minute gap between an outer wall of the annular seal groove and the annular ring and the annular seal groove are provided. A scroll gas compressor that passes at least the seal sliding contact surface of the annular ring among the seal sliding contact surfaces of the annular ring. 2. A thrust bearing, a locking portion of a rotation preventing member, and another differential pressure lubrication passage for supplying lubricating oil to which a discharge pressure acts to supply a sliding surface between a head plate and a lap support disk. The scroll gas compressor according to claim 1, wherein: 3. An oil passage having a throttle passage communicating between an oil chamber communicating with the swivel bearing portion and a space in which the rotation preventing member is disposed, wherein the another differential pressure oil supply passage is provided. Scroll gas compressor. 4. The scroll gas according to claim 3, wherein the throttle passage is formed by mounting the orbiting bearing in a bearing mounting hole provided in the orbiting scroll and making one surface of a cylindrical outer peripheral portion of the orbiting bearing flat. 5. A cut is formed in the annular ring so that an outer peripheral surface of the annular ring is expanded by a pressure difference between an inner oil chamber and an outer back pressure chamber to be in close contact with an outer surface of a storage portion of the annular ring. 2. The scroll gas compressor according to claim 1, wherein said annular ring is made of a flexible material. 6. The scroll gas compressor according to claim 1, wherein the annular ring is made of a material having a larger coefficient of thermal expansion than a member accommodating the annular ring. 7. The scroll gas compressor according to claim 1, wherein a discontinuous annular oil groove that does not communicate with the cut is provided on a sliding surface of the annular ring. 8. The scroll gas compressor according to claim 1, wherein the annular ring is made of a material whose flexibility increases with increasing temperature.