JPH08303364A - Scroll gas compressor - Google Patents

Abstract

PURPOSE: To provide a scroll gas compressor which is manufactured at low cost and provided with a pump constitution having substantially high oil supply efficiency to a bearing sliding part. CONSTITUTION: A displacement pump device 106 driven and operated by a drive shaft 304 is arranged in either a main body frame 305 for supporting the drive shaft 304 or a turning scroll 318. A compression chamber side bearing sliding part of the drive shaft 304 is arranged on the way to a bearing oil supply path where lubricating oil of an oil sump 34 in the compressor is sucked and discharged by the displacement pump device 106 and returned again in the oil sump 34 in the compressor. And an oil path in the suction side of the displacement pump device 106 and an oil path in the discharge side are provided in the main body frame 305 and then the oil path in the suction side is communicated with the oil sump 34 in the compressor. This constitution can shorten the oil paths in the suction and discharge sides of the displace pump device without penetrating the inside of a motor 3.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil supply device and an oil supply passage for a bearing portion of a scroll compressor.

[0002]

2. Description of the Related Art A scroll compressor having low vibration and low noise characteristics has a suction chamber at the outer peripheral portion, a discharge port at the center of a spiral, and a reciprocating compression flow of a compressed fluid in one direction. If there is no need for a discharge valve for compressing fluid, such as a compressor or rotary compressor, and there is no large fluctuation in the operating compression ratio determined by the suction pressure and the discharge pressure, the suction volume of the compression chamber and the final compression By setting the volume ratio, which is determined by the chamber volume, to an appropriate value, the discharge pulsation is small and a large discharge space is not required.

However, since the compression chamber has a large number of sealing portions, a large amount of compressed fluid leaks. Especially, in the case of a scroll gas compressor having a small exclusion capacity such as a refrigerant compressor for home air conditioning,
In order to reduce the leakage gap of the compression part, it is necessary to make the dimensional accuracy of the spiral part extremely high.

However, due to the complexity of the shape of the parts, the scroll gas compressor is high in cost due to variations in the dimensional accuracy of the spiral portion, and the variations in performance are large. Especially, in the low speed operation state of the compressor, the gas in the middle of compression is compressed. It has the drawbacks of high leak rate and lower compression efficiency than reciprocating compressors and rotary compressors.

Therefore, as a measure for solving this kind of problem, it is expected that the dimensional accuracy of the spiral portion is optimized to prevent gas leakage during compression and that the compression efficiency is improved by the oil film sealing effect using lubricating oil. Is large, and JP-A-57-83
As described in Japanese Patent No. 86, a proposal has been made to improve the above-mentioned drawbacks by injecting an appropriate amount of lubricating oil into the compression chamber during compression and sealing the gap between the compression chambers with an oil film of the lubricating oil.

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

FIG. 24 shows an example of a general structure of a medium to large class scroll refrigerant compressor having a closed case (chamber) as a high pressure space. In the figure, the compression unit and the discharge chamber 1031 are in the upper part, the motor (electric element) is in the lower part,
The bottom of the oil sump is the discharge pipe 104 which is the final outlet of the compressor.
2 is arranged in the vicinity of the motor (electric element), and after the discharge refrigerant gas and the lubricating oil are separated in the discharge chamber 1031, the lubricating oil stores the motor (electric element) through the oil drain holes 1035, 1036. Returning to the space, the refrigerant is collected in the bottom oil sump, and the discharged refrigerant gas is discharged from the discharge pipe 1042 again after passing through the space for accommodating the motor (electric element) from the upper portion of the discharge chamber 1031 through another passage. It Further, in order to reduce the axial gap of the compression chamber, lubricating oil under the pressure of the discharge of the bottom of the hermetically sealed case (chamber) 1013 is provided inside the drive shaft (crankshaft) 1008. Crankshaft) 1
After lubricating the bearing sliding surface through the bearing gap of the main body frame (frame) 1009 supporting the fixed scroll 1003 supporting the 008 and the gap of the crank shaft portion of the drive shaft (crank shaft) 1008, the orbiting scroll 1
Into the back pressure chamber 1025 provided on the back surface of 006, the intermediate pressure lubricating oil depressurized in the middle of the path is made to flow, and the intermediate pressure lubricating oil and the high pressure lubricating oil above the crankshaft move the rear surface of the orbiting scroll 1006. Energize. Thereby, the back pressure biasing force is set so as to prevent the orbiting scroll 1006 from separating from the fixed scroll against the compression chamber gas pressure.

Lubricating oil of back pressure 1025 flows into the compression chamber 1015 in the middle of compression through the back pressure hole 1017 provided in the end plate 1004 of the orbiting scroll 1006, and then the compression chamber 1
Compresses together with the suction refrigerant gas while sealing the gap of 015
It is configured to be discharged and discharged into the discharge chamber 1031.
(JP-A-56-165788).

[0009]

However, the structure as shown in FIG. 24 has the following problems.

The gist of the problem is that the oil supply to the bearing portion is insufficient immediately after the compressor is started.

That is, the compression section is arranged at the upper part and the oil sump is arranged at the bottom part to supply oil to each bearing part which engages with the drive shaft (crankshaft) 1008 during compression with the oil sump on which the discharge pressure acts. Pressure difference between the compression chamber 1015 and the oil guide hole 10 provided in the drive shaft (crankshaft) 1008
In the configuration performed by utilizing the centrifugal pump action of 19, when the discharge pressure rises only a little at a low speed operation and the lubricating oil temperature is low such as in the initial stage of compressor startup, the lubricating oil pressure is lower than the lubricating oil pressure in the oil sump. In some cases, the pressure in the compression chamber 1015 during compression is higher and differential pressure oil supply cannot be performed. Further, even if there is a slight differential pressure, it is difficult for highly viscous lubricating oil to pass through the minute gaps in the bearing sliding portion. In addition, the compressed gas guided from the compression chamber 1015 to the back pressure chamber 1025 causes the orbiting scroll 1006 to move to the fixed scroll 1003 from the initial stage of compressor activation.
Is pressed, and the axial gap of the compression chamber 1015 is also sealed, so that a required compression load is generated in the bearing sliding portion, and seizure occurs in the sliding portion that engages with the drive shaft (crankshaft) 1008. .

As a measure for solving the above problems, a configuration in which a bearing sliding portion is supplied with oil by a positive displacement pump from the initial stage of compressor activation is shown in FIG. 25, which is shown in Japanese Patent Laid-Open No. 59-60092 and FIGS. It is proposed in Japanese Patent Laid-Open No. 62-87693. The former configuration (FIG. 25) is a positive displacement pump device in which a drive shaft 1906 supported by a scroll compression mechanism portion disposed on both sides of a motor (drive motor) and a pump housing 1930 is disposed at an end of the pump housing 1930 side. By driving the (oil supply mechanism) 1932, the lubricating oil in the bottom portion (oil reservoir chamber) 1944 in the closed case (housing) 1901 on which the discharge pressure acts is driven via the oil feed passage 1945 provided in the drive shaft 1906. A main bearing (bearing hole) 1905 that supports the shaft 1906, an orbiting bearing (eccentric hole) 1911, and an orbiting scroll 1912.
Of the drive shaft 1906 and the orbiting scroll 191 even when operating at low speed.
Sufficient oil can be supplied to the second anti-compression chamber side. However, in order to dispose the positive displacement pump device (oil supply mechanism) 1932, it is essential to install the pump housing 1930.
The problem of extremely high cost for refueling arises.

A positive displacement pump device (oil supply mechanism) 19
32 is arranged at the end of the anti-compression chamber of the drive shaft 1906, and the oil supply passage from the positive displacement pump device (oil supply mechanism) 1932 to the compression chamber side bearing sliding part of the drive shaft 19069 is long. Immediately after starting at low speed, a delay in oil supply rise occurs, and the compression chamber side bearing sliding portion of the drive shaft 1906 (bearing hole 19
05 and eccentric hole 1911) may be seized.

Further, the positive displacement pump device (oil supply mechanism) 19
When the lubricating oil discharged from 32 is heated by the heat of the motor when passing through the inside of the rotor 1909 of the motor (driving motor) and the lubricating oil characteristic is deteriorated, the bearing load of the driving shaft 1906 is large. Compression chamber side bearing sliding part (bearing hole 1
Since it is supplied to the 905 and the eccentric hole 1911), there is a problem that the friction loss of the bearing sliding portion (the bearing hole 1905 and the eccentric hole 1911) is large and the input of the compressor is increased.

On the other hand, the latter configuration (FIGS. 26 to 28) is
At a low pressure in the closed case (closed container) 2107, a positive displacement pump device (trochoid pump) 2109 is provided between the end of the shaft 2102c of the orbiting scroll 2102 and the bottom of the eccentric hole 2105a of the drive shaft 2105. Is placed, and the lubricating oil at the bottom of the closed case (closed container) 2107 is sucked up via the oil supply hole 2105c provided in the drive shaft 2105, oil is supplied to the bearing sliding surface at the end of the drive shaft 2105, and then sealed again. In addition to returning to the bottom of the case (closed container) 2107k, part of the lubricating oil is returned to the thrust bearing (bearing) 2106d and the suction chamber arranged to support the pressure load of the compression chamber acting on the orbiting scroll 2102 in the middle of the route. A positive displacement pump device (trochoidal pump)
2109 can be easily arranged. However,
Since the oil supply hole 2105c on the suction side of the positive displacement pump device (trochoidal pump) 2109 penetrates the inside of the drive shaft 2105 connected to the motor 2108, the suction passage is long and the oil supply rise delay immediately after the low speed start of the compressor is started. Occurs. Further, since the lubricating oil in the middle of the suction passage is affected by the temperature rise by the motor 2108, there is a problem similar to the above in that the friction loss of the bearing sliding portion is large and the compressor input is increased.

A configuration in which a positive displacement pump device is arranged and an oil supply passage which does not penetrate the drive shaft is provided is proposed in Japanese Patent Laid-Open No. 63-205490 shown in FIGS.

In this structure, the orbiting bearing (eccentric hole) 30 with which the drive shaft 3005 and the orbiting scroll 3702 are slidably engaged.
Displacement type pump device (trochoid type pump) 3009 operated by rotation of the drive shaft 3005c at the bottom of 05b.
The positive displacement pump device (trochoidal pump) 3009 is used to provide a closed case (closed container) 3007.
Lubricating oil acting on the suction pressure of the inner bottom portion is sucked up through the compression chamber side bearing sliding portion of the drive shaft 3005 without passing through the rotor of the motor 3008, and the discharged lubricating oil is again sealed case (sealed container). A bearing oil supply passage returning to the inner bottom of 3007 is formed.

However, in this structure, since the lubricating oil discharged from the positive displacement pump device (trochoid pump) 3009 communicates with the sliding surface of the slewing bearing (eccentric hole) 3005b, the positive displacement pump device (trochoid pump). Thirty
The suction side and the discharge side of 09 are short-circuited, especially when the compressor is operating at low speed, positive displacement pump device (trochoidal pump)
Since the oil supply capacity of 3009 is remarkably reduced, there is a problem that the function of the positive displacement pump device (trochoid pump) 3009 is not substantially exhibited.

The present invention is intended to solve such a conventional problem, and it is an object of the present invention to realize a pump structure which is low in cost and has a substantially high oil supply efficiency to a sliding portion of a bearing.

[0020]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a positive displacement pump device which is driven by a drive shaft and operates in either a main body frame supporting the drive shaft or an orbiting scroll. Then, the positive displacement pump device sucks in and discharges the lubricating oil in the oil reservoir in the compressor,
Again, the compression chamber side bearing sliding part of the drive shaft is arranged in the middle of the bearing oil supply passage that returns to the oil reservoir in the compressor, and the suction side oil passage and the discharge side oil passage of the positive displacement pump device are located inside the main body frame. The oil passage on the suction side is communicated with the oil reservoir in the compressor.

[0021]

According to a first aspect of the present invention, a positive displacement pump device driven and driven by a drive shaft is arranged in either one of a main body frame supporting a drive shaft and an orbiting scroll. The positive displacement pump device sucks in and discharges the lubricating oil from the oil reservoir placed in the closed case,
The bearing oil supply passage for returning to the oil reservoir is formed again, and the main bearing on the side closer to the compression chamber and the orbiting bearing in which the drive shaft and the orbiting scroll engage with each other are formed in the middle of the bearing oil supply passage. And the oil passage on the suction side and the oil passage on the discharge side of the positive displacement pump device are provided in the main body frame, and the oil passage on the suction side communicates with the oil sump. According to this configuration, the oil passages on the suction side and the discharge side of the positive displacement pump device can be shortened, and the rising of oil supply to the sliding portion at the early stage of low speed start of the compressor can be accelerated.

Further, the lubricating oil is supplied to the bearing sliding portion without causing the deterioration of the lubricating characteristic due to the heating of the motor, and the required lubricating action can be effectively exhibited.

According to a second aspect of the present invention, the positive displacement pump device is a rotary pump device, and any one of the suction / discharge passages is provided to prevent the discharge side lubricating oil of the rotary pump device from flowing back to the suction side. A partition plate that also has one of the functions is arranged on the side surface side of the pump chamber of the rotary pump device. According to this configuration, the oil supply efficiency of the rotary pump device is improved, and the oil supply amount during the low speed operation of the compressor can be secured. Further, the oil passage can be formed at a required position.

According to the third aspect of the present invention, the drive shaft operates between the end of the crankshaft provided at the tip of the drive shaft and the bottom of the orbiting bearing so that the drive shaft engages with the orbiting scroll. A positive displacement rotary pump device is arranged, the suction side of the positive displacement rotary pump device communicates with the oil reservoir in the sealed case via at least the crankshaft, and the discharge side of the positive displacement rotary pump device is connected to the drive shaft. A bearing oil supply passage communicating with an oil reservoir via at least the main bearing through an axial oil hole provided therein is provided. According to this configuration, it is possible to dispose the positive displacement rotary pump device with a simple configuration.

Further, it becomes possible to dispose a slewing bearing and a main bearing on the suction side and the discharge side of the positive displacement rotary pump device.
Realization of equal amount of oil supply to both bearings makes it possible to avoid excessive or insufficient oil supply.

According to a fourth aspect of the present invention, the oil sump is used as a discharge chamber oil sump on which a discharge pressure acts, and the lubricating oil in the discharge chamber oil sump is branched and depressurized from the discharge side of the positive displacement pump device to prevent the orbiting scroll from rotating. A differential pressure oil supply passage that supplies oil to a compression bearing or a suction chamber after oil is supplied to a thrust bearing that supports the compression chamber side and is arranged in the main body frame is provided. According to this configuration, the oil supply head loss of the positive displacement pump device is reduced, and the pump input is reduced.

Further, even when the compressor is operating at a low speed, sufficient oil can be supplied to the sliding portion that supports the orbiting scroll.

According to a fifth aspect of the present invention, the orbiting scroll is made of a material having a higher thermal conductivity and a larger thermal expansion coefficient than the positive displacement rotary pump device and the drive shaft. According to this configuration, even when the temperature of the positive displacement rotary pump device is increased due to high-speed operation of the compressor, the gap between the housing portion in which the positive displacement rotary pump device is disposed and the positive displacement rotary pump device is abnormally reduced. Can be avoided.

According to a sixth aspect of the present invention, the positive displacement rotary pump device is arranged in the lap support disk of the orbiting scroll. With this configuration, the center of gravity of the orbiting body member including the orbiting scroll can be brought closer to the compression chamber, and the orbiting motion of the orbiting scroll can be stabilized.

According to a seventh aspect of the present invention, the oil surface of the oil sump is arranged at a position higher than that of the positive displacement pump device. With this configuration, suction of the positive displacement pump device is facilitated, and the amount of oil supply can be increased during low-speed operation of the compressor.

[0031]

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

(Embodiment 1) In FIGS. 1 to 15, reference numeral 1 denotes an iron hermetic case, the inside of which is an orbiting scroll 318.
The main body frame 3 for fixing the fixed scroll 15 which meshes with the driving shaft 304 by bolts and supports the drive shaft 304.
By 05, the upper motor chamber 6 and the lower accumulator chamber 46 are partitioned.

The motor chamber 6 has a high-pressure atmosphere, the motor 3 is arranged in the upper part, and the compression part is arranged in the lower part.
Is made of eutectic graphite cast iron having excellent sliding properties and weldability, and the protrusions 79a provided on the outer peripheral surface thereof are in contact with the inner wall surface and the end surface of the upper closed case 1a and the lower closed case 1b. The protrusion 79a, the upper closed case 1a, and the lower closed case 1b are hermetically welded by a single welding bead 79b.

The drive shaft 304 is provided with an upper bearing 311 provided at the upper end of the main body frame 305, a main bearing 312 provided at the center, a plurality of shallow grooves 7 provided on the upper end surface of the main body frame 305 and having radial lines. Thrust bearing portion 313 having
The crankshaft 314 at the lower end, which is eccentric from the main shaft of the drive shaft 304, is engaged with the orbiting bearing 318b of the orbiting boss portion 318e provided on the orbiting scroll 318.

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 and an end plate as shown in FIG. 15b, and a fixed scroll wrap 1 is provided at the center of the end plate 15b.
The discharge boat 16 opening at the winding start portion of 5a
The suction chamber 17 is provided in communication with the discharge passage 80 opened to the outside, and the suction chamber 17 is provided on the outer peripheral portion of the fixed scroll wrap 15a.

On the end plate 15b on the anti-orbiting scroll side,
A non-return valve device 50 is attached so as to cover the discharge port 16, and the non-return valve device 50 is made of a thin steel plate in which the outer peripheral portion is cut out at several places, as illustrated 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 discharge small holes 50h around the check hole 50a.
And a spring device 50c interposed between the valve body 50b and the valve case 99. The spring device 50c contracts when the temperature of the spring device 50c exceeds 50 ° C, and the temperature of the spring device 50c increases by 50 ° C.
It has a shape memory characteristic that expands below and contracts to the bottom of the check valve hole 50a under the discharge refrigerant gas pressure during operation of the compressor, and the compressor itself is in a state of 50 ° C. or less. The inside is set so as to press the valve body 50 against the end plate 15b to close the discharge port 16.

As shown in FIGS. 1 and 14, a spiral orbiting scroll wrap 318a which meshes with the fixed scroll wrap 15a to form a side wall of the compression chamber, and a drive shaft 30.
The orbiting scroll 318 made of an aluminum alloy, which includes a wrap support disk 318c in which an orbiting boss portion 318e engaged with the crankshaft 314 of 4 is upright, and is disposed surrounded by the fixed scroll 15 and the main body frame 305. The surfaces of the lap support disk 318c and the orbiting scroll wrap 318a are hardened by porous nickel plating or the like. As shown in FIG. 3, a spiral tip seal groove 98 is formed at the tip of the orbiting scroll wrap 318a.
Is provided, and a chip seal 98a made of resin is mounted in the chip seal groove 98 with a minute gap.
When the orbiting scroll 318 is pressed in the axial direction of the fixed scroll 15, the flat portion of the lap support disk 318c contacts the tip of the fixed scroll wrap 15a, but the tip of the orbiting scroll wrap 318a does not contact the fixed scroll 15. It keeps a microscopic distance.

The discharge passage 80 (see FIG. 1) is provided in the discharge chamber 2 and the fixed scroll 15 formed by the discharge cover 2a and the mirror plate 15b mounted on the mirror plate 15b so as to cover the check valve device 50. The gas passage A80 includes a gas passage B80b, a gas passage A80a provided in the body frame 305, a discharge guide 81 attached to the body frame 305 so as to surround the main bearing 312, and a discharge chamber 2b formed by the body frame 305.
a and the gas passage B80b are provided at target positions (see FIG. 14).

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

The accumulator chamber 46 communicating with the evaporator side of the refrigeration cycle is formed by the lower closed case 1b, the fixed scroll 15 and the main body frame 305, and the suction pipe 47 communicating therewith is provided on the side surface of the lower closed case 1b. About 90 each from the position facing the suction pipe 47
The suction holes 43 are fixed at two positions spaced apart from each other.
5 (see FIG. 14).

The low pressure oil reservoir 46a at the bottom of the accumulator chamber 46 and the suction hole 43 communicate with each other through an oil suction hole A9a provided in the discharge cover 2a and a small diameter oil suction hole B9b provided in 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 sump 46a are sucked up by the negative pressure generated when the refrigerant gas passes through the suction hole 43. There is.

A flat plate-shaped thrust bearing 22 capable of moving only in the axial direction by being restricted from moving in the rotational direction by the split pin-shaped parallel pin 19 fixed to the main body frame 305.
0 is arranged between the lap support disk 318c and the main body frame 305, and the elastic force of the annular seal ring (made of rubber) 70 (see FIG. 12) interposed between the thrust bearing 220 and the main body frame 305. By the end plate mounting surface 1 between the main body frame 305 and the fixed scroll 15
It is in contact with 5b1.

Lap support disk 3 of orbiting scroll 318
The height from the end plate sliding surface 15b2 slidingly contacting 18c to the end plate mounting surface 15b1 is set so that the lap support disk 318c improves the sealing property of the sliding portion by the oil film.
It is set to be about 0.015 to 0.020 mm larger than the thickness of 18c.

As shown in FIGS. 1 and 8, an annular seal groove 9 concentric with the center of the orbiting bearing 318b is formed on the end face of the orbiting boss portion 318e of the orbiting scroll 318 on the main body frame 305 side.
5, an annular ring 94 made of a flexible resin is attached to the annular seal groove 95, as shown in FIG. The outer peripheral surface of the annular ring 94 is the annular ring 9 during operation of the compressor.
Due to the thermal expansion of No. 4 and the lubricating oil pressure inside the annular ring 94, the cut 94b comes into close contact with the side surface of the annular seal groove 95 and has an inclination angle with respect to the outer peripheral surface of the annular ring 94.
Are arranged so as to be in close contact with each other. Annular ring 94
Is an oil chamber A on the side of the main bearing 312 that supports the drive shaft 304.
Orbiting scroll 318, body frame 30 from 378a
5. The orbiting scroll 318 formed by the thrust bearing 220 is sealed so as to prevent excessive leakage to the back pressure chamber 339.

The annular thrust bearing 220 is made of a sintered alloy which is easy to form a hole, and as shown in FIGS. 11 and 13, two guide holes 93 into which the split pin 19 is movably inserted, an annular oil groove 92, and a shallow oil groove 92. It has a groove 291 and a main body frame 305.
Is mounted in the thrust ring groove 90.

Body frame 305 and thrust bearing 220
A release gap 27 of about 0.05 mm is provided between the release gap 27 and the release gap 27, and an annular groove 28 for mounting a seal ring 70 is provided inside and outside the release gap 27. The seal ring 70 seals between the release gap 27 and the back pressure chamber 339.

The release gap 27 is formed by the body frame 305.
The thrust back pressure introducing hole A89a provided in the fixed scroll 15 and the thrust back pressure introducing hole B89b provided in the fixed scroll 15 communicate with the third compression chamber 60b (see FIG. 14) in the final compression stroke.

As shown in FIGS. 1 and 2, the thrust bearing 2
The rotation prevention member (hereinafter referred to as Oldham ring) 24 of the orbiting scroll 318 arranged inside the 20 is made of a light alloy or a reinforced fiber composite material suitable for sintering molding, injection molding, etc., and has a flat ring shape. Both sides are provided with parallel key-shaped key portions that are orthogonal to each other. The key portion on the upper surface side is the key groove 71a provided on the main body frame 305, and the key portion on the lower surface side is the key provided on the lap support disk 318c. It engages with the groove 71 and slides.

The thickness of the Oldham ring 24 is determined by the thickness of the body frame 30 when the Oldham ring 24 reciprocates.
5 and the lap support disk 318c are slid smoothly and no jumping phenomenon occurs.

A discharge pipe 31 is attached to the outer peripheral portion of the upper end wall of the upper closed case 1a, and a glass terminal 88 for connecting the motor power source is attached to the central portion.

An oil separator 87 attached to the upper closed case 1a partitions the discharge pipe 31 and the glass terminal 88 from the motor 3 side. The rotor 3 a of the motor 3, which is axially positioned by the stepped portion of the drive shaft 304, drives the drive shaft 30 together with the upper balance weight 75.
4, the upper balance weight 75 has a disk shape, and its outer diameter is set to be larger than the outer diameter of the rotor 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 body frame 305 is arranged close to the lower balance weight.

The discharge chamber oil sump 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. .

The discharge chamber oil sump 34 is formed by the body frame 3
05 through the oil hole A338a provided in the main bearing 312
To the oil chamber A 378a at an intermediate position between the rotary bearing 318b and the orbiting bearing 318b.

As shown in FIGS. 1 and 8, on the surfaces of the sliding shaft portion 304a of the drive shaft 304 and the crank shaft 314,
When the drive shaft 304 rotates in the forward direction, the oil in the oil chamber A 378a is formed by the orbiting bearing 318b and the crankshaft 314, and the spiral oil grooves 341a and 341b are formed in the direction in which screw pump oil is supplied to the motor 3 side. Provided,
Its upper end reaches the thrust bearing 313.

The oil chamber B 378 b and the surface of the main bearing 312 are communicated with each other by an oil hole 112 provided in the drive shaft 304, and the oil sump 72 between the upper bearing 311 and the main bearing 312 and the back pressure chamber 339 are the main body frame. An oil hole B38b having a throttle passage portion provided at 305 communicates with the oil hole B38.
The opening end of b on the back pressure chamber 339 side is intermittently opened to a discontinuous oil groove 94a provided in the annular ring 94, and is provided at a position that is intermittently opened and closed by the annular ring 94.

As shown in FIGS. 1, 10 and 14, the back pressure chamber 339 has about 18 levels before the first refrigerant compression chambers 61a and 61b communicating with the suction chamber 17 are completely closed.
Within the swing angle range of 0 degree, the shallow groove 291, the outer peripheral space 37 outside the lap support disk 318c provided in the thrust bearing 220, the oil hole C38c provided in the lap support disk 318c, and the symmetrical positions are provided. Injection passage 74 constituted by a small diameter injection hole 52
And the shallow groove 291 provided in the thrust bearing 220 is intermittently opened and closed by the lap support disk 318c.

High pressure oil chamber A37 communicating with discharge chamber oil sump 34
As shown in FIG. 8, a partitioning cap 101 made of steel plate is press-fitted into the stepped inner wall of 8a and arranged so as to cover the brim 102 of the drive shaft 304, and the oil chamber A378a is swung with the main bearing 312 side. It is separated from the bearing 318b side.

Revolving boss portion 318 of revolving scroll 318
A slewing bearing 318b is press-fitted into e, and a trochoid pump device 106 including an outer rotor 106a and an inner rotor 106b is attached to the bottom of the slewing bearing 318b.

The trochoid pump device 106 has a drive shaft 30.
4 is connected to a driving end shaft 107 provided at the tip of the crank shaft 314 at the end of the No. 4, and is driven. The crankshaft 314 and the drive end shaft 107 are concentric.

A suction hole 108 as shown in FIG. 10 is provided between the slewing bearing 318b and the trochoid pump device 106.
A partition plate 110 having a central hole 109 is attached and fixed.

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

The discharge chamber oil sump 34 and the back pressure chamber 339 of the orbiting scroll 318 are composed of an oil hole A338a, an oil chamber A378a,
Oil supply passage A communicating with the oil sump 72 via the bearing gaps of 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 main bearing 312. And an oil supply passage C formed of an oil supply passage B communicating with the oil sump 72 from the oil chamber A378a via the spiral oil groove 341a and an oil hole B38b.

As described above, in addition to the screw pump action by the spiral oil grooves 341a and 341b provided on the surface of the drive shaft 304, a positive displacement pump device is arranged at the tip of the drive shaft 304. The bearing lubrication means is formed so that the operation can be continued.

In FIG. 15, the horizontal axis represents the rotation angle of the drive shaft 304, the vertical axis represents the refrigerant pressure, and the pressure change state of the refrigerant gas during the suction / compression / discharge processes.
2 shows the pressure change at the time of normal pressure operation, and the dotted line 63 shows the pressure change at the time of abnormal pressure rise.

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

1 to 15, when the drive shaft 304 is rotationally driven by the motor 3, the orbiting scroll 318
Is driven by the crank mechanism of the drive shaft 304.
Try to rotate around the main axis of the Oldham ring 24
The key portion on the side of the orbiting scroll 318 (see FIG. 2) is engaged with the key groove 71 of the orbiting scroll 318, and the key portion on the opposite side is the key groove 71a of the main body frame 305 (see FIG. 1).
Since it is engaged with, the rotation is prevented, and the orbital motion is performed to change the volume of the compression chamber together with the fixed scroll 15, and the refrigerant gas is sucked and compressed.

Third compression chambers 60a, 60b in the final compression stroke
The release gap 27 on the back side of the thrust bearing 220 that communicates with (the compression space in the stroke immediately before the compression chamber communicates with the discharge port 16) is filled with high-pressure refrigerant gas with the lapse of time after the start of compression. The thrust bearing 220 is pressed against the end plate mounting surface 15b1 of the fixed scroll 15 by the back pressure bias and the elastic force of the seal ring 70. Thereby,
The lap support disk 318c of the orbiting scroll 318 is sandwiched between the end plate sliding surface 15b2 and the thrust bearing 220 (1
5 to 20 micron assembly gap).

Then, the suction refrigerant of the gas-liquid mixture containing the lubricating oil from the refrigeration cycle connected to the compressor 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 of No. 5 through the upper space of the accumulator chamber 46, it flows into the suction chamber 17 through the two suction holes 43 (see FIG. 14).

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 inertial force at the time of changing the inflow direction are temporarily collected at the bottom of the accumulator chamber 46, and the sucked refrigerant gas is sucked into the suction hole 43. Due to the negative pressure generated when passing through, the oil is sucked up into the suction hole 43 in an atomized state through the oil suction hole A9a and the oil suction hole B9b, and is mixed into the suction refrigerant gas again.

The sucked refrigerant gas separated into gas and liquid is sucked into the suction chamber 1.
7. First compression chambers 61a and 61b formed between the orbiting scroll 318 and the fixed scroll 15 (see FIG. 14)
Through the second compression chamber 51a, 5
1b, and the third compression chamber 60a, 60b to the check valve chamber 50a is discharged from the discharge port 16 in the central portion after sequentially transferred compression, discharge chamber 2, gas passage B80b, gas passage A80.
a and the discharge chamber 2b are sequentially discharged to the motor chamber 6.

The discharged refrigerant gas discharged into the motor chamber 6 collides with the annular shielding plate 86 and the winding of the motor 3, and then passes through the cooling passage 35 on the outer side of the stator 3b and the passage on the inner side of the motor 3 to pass through the motor 3. Flowing to the upper side of the motor chamber 6 while cooling,
It is delivered from the discharge pipe 31 to an external 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 sump 34. The lubricating oil in the discharged refrigerant gas passing through the outer peripheral portions 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 inner space of the winding bundle, and the discharge chamber oil sump 3
Collect in 4.

Lubricating oil in the discharge chamber oil reservoir 34 is passed through a route described later to form an oil chamber A378a, an oil chamber B378b, and a back pressure chamber 3.
39, and the back pressure applying force to the orbiting scroll 318 gradually increases.

Following the increase in pressure in the motor chamber 6, the lap support disk 318c gradually contacts the end plate sliding surface 15b2 of the fixed scroll 15 with an appropriate pressing force. The gap between the tip of the fixed scroll wrap 15a and the wrap support disk 318c of the orbiting scroll 318 disappears, thereby sealing the compression chamber and efficiently compressing the sucked refrigerant gas, so that stable operation is continued.

The axial gap between the tip of the orbiting scroll wrap 318a and the end plate 15b of the fixed scroll 15 is such that the tip seal groove 98 (Fig. 3)) and the gas back pressure causes the tip seal 98a to be pressed against the side surface of the low compression chamber of the tip seal groove 98a and the end plate 15b of the fixed scroll 15 for sealing.

When the compressor is stopped, the orbiting scroll 318 instantaneously makes a reverse swirling motion due to the reverse flow based on the pressure difference of the refrigerant gas in the compression chamber, but since the refrigerant gas flows backward from the compression chamber to the suction chamber 17, The orbiting scroll 318 is shown in FIG.
As shown in FIG. 4, the first compression chambers 61a and 61b stop at the turning angle in a state where the first compression chambers 61a and 61b communicate with the suction chamber 17. In this stopped state, the annular ring 94 is set so as to block 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 to the suction chamber 17, so that the pressure of the refrigerant gas in the discharge port 16 suddenly drops and the difference in the refrigerant gas pressure between the discharge port 16 and the discharge chamber 2 is caused. The valve body 50b is the discharge port 16
To prevent continuous backflow of the discharged refrigerant gas from the discharge chamber 2 to the compression chamber.

Due to the temporary backflow of the discharged refrigerant gas immediately after the compressor is stopped and the reverse orbit of the orbiting scroll 318, the valve body 5
0b separates from the bottom surface of the check valve chamber 50a, and until the refrigeration cycle is pressure balanced, the valve body 51 is depleted due to the pressure difference.
b continues to block the discharge port 16. At the same time, the temperature of the coil spring 50 having a shape memory characteristic is lowered and the coil spring 50 expands, and the urging force of the coil spring 50 keeps the valve body 50b closing the discharge port 16.

The first compression chambers 61a, 61b and the back pressure chamber 339 which are intermittently communicated with the suction chamber 17 are the first compression chamber 61a,
Only when 61b is within 180 degrees before completion of closing, the thrust bearing 220 communicates with each other via the shallow groove 291 (see FIG. 11), and the lubricating oil film is formed between the thrust bearing 220 and the lap support disk 318c. Therefore, the refrigerant gas does not flow backward from the compression chamber to the back pressure chamber 339 during the compression.

When the compressor is stopped for a long time, the pressure in the compressor is equalized, and the liquid refrigerant flows not only into the accumulator chamber 46 but also into the compression chamber. The thrust force in the direction opposite to the discharge port 16 acts on the orbiting scroll 318 due to the pressure of the liquid compressed refrigerant in the compression chamber. As a result, the orbiting scroll 318 is separated from the fixed scroll 15 in the axial direction, and the compression load is reduced.

On the other hand, the back pressure chamber 339 in the initial stage of starting when the compressor is cold.
Since the increase in the lubricating oil pressure in the discharge chamber oil sump 34 is low, the pressure is substantially equivalent to the suction pressure. As a result, the lap support disk 318c of the orbiting scroll 318 is separated from the end plate sliding surface 15b2 in the state where the back pressure is applied only by the lubricating oil in the oil chamber A378a having a low pressure rise, and the thrust bearing 22
It is retracted to 0 and supported, and a gap (about 0.0 mm) is formed between the lap support disk 318c and the tip of the fixed scroll wrap 15a.
15-0.020 micron), the pressure in the compression chamber drops, and the compression load in the initial stage of starting is reduced.

In the unlikely event that liquid compression occurs in the compression chamber during continuous operation and the pressure in the compression chamber suddenly rises abnormally, the thrust force acting on the orbiting scroll 318 is applied to the rear surface of the orbiting scroll 318. It becomes larger than the applied back pressure biasing force, the orbiting scroll 318 moves in the axial direction,
It is supported by the thrust bearing 220. Then, the sealing of the compression chamber is released in the same manner as described above, the compression chamber pressure is reduced, and the compression load is reduced.

The back pressure chamber 339 is the first compression chamber 61.
Since a and 61b communicate with the outer peripheral space 37 through the shallow groove 291 provided in the thrust bearing 220 within the swivel angle range of about 180 degrees before the completion of the intake refrigerant gas confinement,
Liquid compression does not occur within this communication swirl range. Therefore, in any compressor operating state including generation of liquid compression in the compression chamber, backflow of the refrigerant gas in the compression chamber to the back pressure chamber 339 is avoided, and the reduction of the compression load is not hindered.

The lubricating oil in the discharge chamber oil sump 34 at the initial stage of cold start of the compressor is a spiral oil groove 341 provided on the drive shaft 304.
a, 341b screw pump action and the trochoid pump device 106, through the oil hole A338a, the oil chamber A37
8a is sucked.

After that, most of the lubricating oil in the oil chamber A 378a lubricates the sliding surface of the slewing bearing 318b while passing through the spiral oil groove 341b, passes through the suction hole 108 of the partition plate 110, and is pumped by the trochoid pump device 106. Sucked into the room,
After being discharged into the oil groove 111, it is supplied to the sliding surface of the main bearing 12 via an oil hole 112 provided in the drive shaft 304,
It is sent to the oil sump 72.

The remaining part of the lubricating oil in the oil chamber A378a is supplied to the main bearing 312 by the screw pump action of the spiral oil groove 341a, joins with the lubricating oil that has passed through the oil hole 112, and then the lubricating oil Part of the oil hole B38b (Fig. 8
The pressure is reduced in the throttle passage portion of (3) and intermittently supplied to the back pressure chamber 339, and the remaining lubricating oil is re-collected in the discharge chamber oil sump 34 after lubricating the sliding surfaces of the upper bearing 311 and the thrust bearing 313. It

Further, a very small part of the lubricating oil in the oil chamber A378a is decompressed via the sliding groove surface of the mounting groove portion of the annular ring 94 and leaks to the back pressure chamber 339.

The refrigerant gas in the motor chamber 6 is blocked from flowing back to the upper bearing 11 between the oil sump 72 and the motor chamber 6 due to the sealing action of the oil film that lubricates the upper bearing 311.

On the other hand, a part of the refrigerant gas mixed in the lubricating oil in the oil sump 72 is degassed and discharged into the motor chamber 6 together with the lubricating oil for the upper bearing 311. As a result, the back pressure chamber 33
The mixed amount of the refrigerant gas in the lubricating oil intermittently lubricated in 9 is reduced, and the lubricating characteristics are improved.

The pressure of the refrigerant gas discharged from the motor chamber 6 rises following the lapse of time after the compressor starts cold, and the discharge chamber oil sump 34
The lubricating oil in the oil chamber A is also affected by the pressure difference between it and the back pressure chamber 339.
It is supplied to the back pressure chamber 339 together with the trochoid pump device 106 and the screw pump action of the spiral oil grooves 341a and 341b. The pressure of the back pressure chamber 339 gradually increases, and the combined force with the lubricating oil pressure corresponding to the discharge pressure of the oil chamber A378a acts on the lap support disk 318c of the orbiting scroll 318. As a result, the thrust load acting to separate the orbiting scroll 318 from the fixed scroll 15 is offset by the refrigerant gas pressure in the compression chamber, and the thrust force acting on the orbiting scroll 318 is reduced.

Therefore, while the pressure rise in the motor chamber 6 after the cold start of the compressor is low, the oil chamber A 378a and the back pressure chamber 33 are kept.
The force exerted on the orbiting scroll 318 by the lubricating oil pressure of No. 9 is smaller than the thrust load on the orbiting scroll 318 by the refrigerant gas pressure in the compression chamber. As a result, the orbiting scroll 318 separates from the fixed scroll 15, and the elastic force of the seal ring 70 and the third compression chamber 60a in the final compression stroke,
It is supported by a thrust bearing 220 which receives a back pressure due to the refrigerant gas introduced from 60b.

When the differential pressure between the discharge pressure and the suction pressure exceeds the required pressure, the force imparted to the orbiting scroll 318 by the lubricating oil pressure in the oil chamber A 378a and the back pressure chamber 339 orbits by the refrigerant gas pressure in the compression chamber. It becomes larger than the thrust load on the scroll 318. And the orbiting scroll 318
Are supported by the fixed scroll 15.

The center of the compression chamber, the center of the slewing bearing 318e,
In the arrangement in which the centers of the annular rings 94 are substantially coincident with each other, the annular rings 94 orbit together with the orbiting scroll 318, so that the inertial force at that time attempts to jump out from the annular seal groove 95 provided in the orbiting boss portion 318e. . Further, the annular ring 94 expands its inner diameter by the pressure difference between the oil chamber A 378a and the back pressure chamber 339, and closes the cut end 94b together with thermal expansion. By these actions, the annular ring 94 is pressed against the outer surfaces of the main body frame 305 and the annular seal groove 95, and the oil scraping action of the annular ring 94 causes the annular seal groove 95 and the annular ring 94 to move.
Lubricating oil is pushed in between and to prevent excessive leakage of lubricating oil between the oil chamber A 378 a and the back pressure chamber 339.

Further, the resinous annular ring 94 having excellent flexibility expands its inner diameter along the outer side surface of the annular seal groove 95 due to the pressure difference between the back pressure chamber 339 and the oil chamber A 378a, and heat The cut 94b is closed together with the expansion and is pressed against the outer side surface of the annular seal groove 95, so that the leakage between both spaces is further reduced.

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 main body frame 305 and the main body frame 305, wear and sliding resistance of the sliding surface are reduced.

During normal operation of the compressor, the high pressure oil chamber A378
The orbiting scroll 318 is given back pressure to the fixed scroll 15 side by the lubricating oil pressure of a and the lubricating oil pressure of the back pressure chamber 339, and the lap support disk 318c and the end plate sliding surface 15b2.
Smoothly slides while maintaining an appropriate contact force, and minimizes the axial clearance of the compression chamber.

The lubricating oil flowing into the back pressure chamber 339 intermittently flows into the outer peripheral space 37 through the shallow groove 291 provided in the thrust bearing 320, and further the lap supporting disk 318c.
The oil pressure is gradually reduced through the oil hole c38c provided in the cylinder and the small diameter injection holes 52a and 52b (see FIG. 14) arranged symmetrically to the first compression chambers 61a and 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 that has flowed into the compression chamber (compression space) together with the suction refrigerant gas, and seals a minute gap between the adjacent compression chambers with an oil film. The compressed refrigerant gas is prevented from leaking, and the sliding surface of the compression space is lubricated, and the compressed refrigerant gas is discharged again to the motor chamber 6 through the discharge port 16.

In the oil supply path from the discharge chamber oil reservoir 34 via the back pressure chamber 339 to the first compression chambers 61a, 61b,
The back pressure chamber 339 maintains a proper 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 as immediately after the cold start, or abnormal liquid compression occurs. In the case, the orbiting scroll 3 is used as described above.
18 is separated from the fixed scroll 15, and the thrust bearing 2
Supported by 20.

However, the thrust bearing 220 urged by the back pressure cannot support the abnormally increased pressure load of the compression chamber, and is retracted in the direction of decreasing the release gap 27 and fixed to the lap support disk 318c of the orbiting scroll 318. The axial gap between the scroll 15 and the tip of the fixed scroll wrap 15a increases. As a result, a large amount of leakage occurs between the compression chambers, and the pressure in the compression chamber suddenly drops during compression, as indicated by the alternate long and short dash line 63a in FIG.

The orbiting scroll 318 is the fixed scroll 1.
Since the maximum distance apart from 5 in the axial direction is regulated to about 70 microns, an oil film remains in each gap between the sliding surfaces on both sides of the lap support disk 318c, and the outer peripheral space 37 and the suction chamber 1
The pressure change in the back pressure chamber 339 due to the direct communication with 7 is suppressed, the compression load is instantly reduced, the thrust bearing 220 can be instantly returned to the original position, and the stable operation is continued.

When the orbiting scroll 318 retreats toward the thrust bearing 220, the orbiting scroll wrap 31
The axial dimension between the tip of 8a and the fixed scroll 15 also increases, but since the tip seal 98a is pressed toward the fixed scroll 15 by the gas pressure on its back surface,
Almost no compressed refrigerant gas leaks from this portion.

On the other hand, the gap between the lap support disk 318c of the orbiting scroll 318 and the tip of the fixed scroll wrap 15b of the fixed scroll 15 expands, compressed refrigerant gas leaks in the compression chamber, and the pressure in the compression chamber drops sharply. To do.

Also, when foreign matter is caught in the axial gap between the orbiting scroll 318 and the fixed scroll 15, the thrust bearing 220 retreats and removes the foreign matter in the same manner as described above.

Further, in the initial stage of cold start-up or during steady operation, the pressure in the compression chamber when an instantaneous liquid compression occurs causes abnormal overcompression as indicated by the dotted line 63 in FIG.
Has a large high-pressure space communicating with the check valve chamber 5
0a, the discharge chamber 2 and the discharge chamber 2b are sequentially expanded, and the pressure in the motor chamber 6 hardly changes.

Further, as the compressor operating speed increases, the refrigerant gas leakage in the compression chamber per unit time decreases. On the other hand, the injection holes 52a, 52 per turning motion
The opening time of b is shortened, the amount of oil injection into the compression chamber per turning motion is suppressed, and unnecessary oil compression is reduced, and the passage due to the increase in the number of cutoffs between the oil hole B38b and the back pressure chamber 339. Resistance increased, oil chamber A378a
The amount of lubricating oil flowing into the back pressure chamber 339 is also suppressed, and the pressure in the back pressure chamber 339 is appropriately maintained.

In FIG. 8, the oil hole B38b and the back pressure chamber 3
39 is set to a large number of sections per one swirl motion that communicates intermittently with 39, but when the compressor operating conditions are such that the compression load is comparatively small, per swirl motion between the oil hole B38b and the back pressure chamber 339 is set. The opening position of the oil hole B38b is moved to the center side of the main body frame 305 so that the communication section is reduced,
It will be apparent from the description of the prior art that it is necessary to reduce the amount of lubricating oil in the oil chamber A 378a flowing into the back pressure chamber 339 and the compression chamber. Along with this, the pressures of the back pressure chamber 339 and the outer peripheral space 37 also decrease.

As described above, according to the above embodiment, the effects of the embodiments described below can be obtained.

That is, in the first embodiment, the drive shaft 3
The trochoid pump device 106 driven and driven by the drive shaft 304 is arranged inside the main body frame 305 supporting 04 and the bottom part of the orbiting bearing 318e of the orbiting scroll 318, and the trochoid pump device 106 arranges the discharge in the sealed case 1. The lubricating oil for the chamber oil sump 34 is supplied to the oil hole A338a and the oil chamber A378 provided in the body frame 305.
a, spiral oil groove 341b, suction hole 10 of partition plate 110
Suction and discharge through 8 in sequence, and again discharge chamber oil sump 3
A bearing oil supply passage for returning to No. 4 is formed, and in the middle of the bearing oil supply passage, there are a main bearing 312 that supports the drive shaft 304 and a swing bearing 318b that engages with the drive shaft 304 and the orbiting scroll 318. Helical oil groove 341 of sliding part
The trochoid pump device 1 is provided with an axial passage by b.
No. 06, an oil hole A338a serving as an oil passage on the suction side, a main bearing 312 and an upper bearing 311 serving as oil passages on the discharge side are provided in the main body frame 305, and an oil hole A338a serving as an oil passage on the suction side is provided in the discharge chamber oil sump 34. It was made to communicate with. Further, according to this configuration, the oil passages on the suction side and the discharge side of the trochoid pump device 106 can be shortened, and the rising of oil supply to the sliding portions of the slewing bearing 318b and the main bearing 312 at the early stage of the low speed start of the compressor can be accelerated. Thus, the durability at the initial stage of starting the compressor can be improved.

Further, the lubricating oil in the discharge chamber oil sump 34 does not cause deterioration of the lubricating characteristics due to heating of the motor, and the slewing bearing 318b.
Can be supplied to the sliding parts of the main bearing 312 and the main bearing 312, effectively exhibiting the required lubrication effect, and the slewing bearing 31 during overload operation.
8b and the durability of the sliding portion between the main bearing 312 can be improved.

It is possible to reduce the heating of the compression chamber by supplying a part of the lubricating oil supplied to the pump to the compression chamber and to improve the compression efficiency.

In the second embodiment, a partition provided with a suction hole 108 is provided to prevent the lubricating oil in the oil groove 111 on the discharge side of the trochoid pump device 106 from flowing back to the spiral oil groove 341b on the suction side. The plate 110 is connected to the inner rotor 106b and the outer rotor 1 of the trochoid pump device 106.
It is arranged with a suitable gap on the side surface of the pump chamber formed with the part 06a. And according to this configuration,
The oil supply efficiency of the trochoid pump device 106 is improved, and the oil supply amount during low-speed operation of the compressor can be secured. Also,
An oil passage can be formed at a desired position, and an effective lubrication path can be configured.

In the third embodiment, the drive shaft 304 is provided between the end of the crankshaft 314 provided at the tip of the drive shaft 304 so that the drive shaft 304 engages with the orbiting scroll 318 and the bottom of the orbiting bearing 318b. The trochoid pump device 106, which is driven and operated by the
6 and the discharge chamber oil sump 34 in the closed case 1 communicate with each other via a crankshaft 314, and the discharge side of the trochoid pump device 106 via an axial oil hole 112 provided in the drive shaft 304. A bearing oil supply passage communicating with the discharge chamber oil sump 34 via the main bearing 312 is provided. According to this configuration, the trochoid pump device 1 has a simple configuration.
It is possible to arrange 06.

Further, it becomes possible to dispose the slewing bearing 318b and the main bearing 312 on the suction side and the discharge side of the trochoid pump device 106, and it is possible to avoid excessive or insufficient oil supply by realizing equal amount oil supply to both bearings.

In the fourth embodiment, the lubricating oil in the discharge chamber oil sump 34 is supplied to the oil sump 7 on the discharge side of the trochoid pump device 106.
A differential pressure oil supply passage is provided for supplying pressure to the compression chamber after branching and depressurizing from two to support the anti-compression chamber side of the orbiting scroll 318 and supply oil to the thrust bearing 220 arranged in the main body frame 305. Further, according to this configuration, the oil supply head loss of the trochoid pump device 106 is reduced, and the pump input is reduced.

Further, it is possible to sufficiently supply the thrust bearing 220 supporting the orbiting scroll 318 even during the low speed operation of the compressor, and it is possible to continue the low speed operation of the compressor and realize energy saving.

In the fifth embodiment, the orbiting scroll 318 is made of a high silicon aluminum alloy having a higher thermal conductivity and a larger thermal expansion coefficient than the trochoid pump device 106 and the drive shaft 304. According to this configuration, the trochoid pump device 1 associated with the high speed operation of the compressor
Even when the temperature rises at 06, it is possible to avoid an abnormal decrease in the gap between the trochoid pump device 106 and the housing portion in which the trochoid pump device 106 is disposed, and prevent an increase in pump input due to maintaining a proper gap.

In the sixth embodiment, the trochoid pump device 106 is provided with the lap support disk 31 of the orbiting scroll 318.
It is arranged in 8c. According to this configuration, the center of gravity of the orbiting body member including the orbiting scroll 318 can be brought closer to the compression chamber, the orbiting motion of the orbiting scroll 318 can be stabilized, and the vibration of the compressor can be reduced.

In the seventh embodiment, the oil surface of the discharge chamber oil sump 34 is arranged at a position higher than that of the trochoid pump device 106. According to this configuration, the trochoid pump device 106 can be easily sucked, the amount of oil supply can be increased during low-speed operation of the compressor, and the durability of the sliding portion can be improved.

(Embodiment 2) FIG. 16 is a longitudinal cross-sectional view of the main part around the oil supply pump device at the tip of the drive shaft in the scroll refrigerant compressor according to the second embodiment of the present invention.
In the stepped hole portion of the main bearing 412 of No. 5 on the side of the orbiting scroll 418, the suction notch 11 as shown in the external view of FIG.
The side plate 114 having 4a and the side plate case 118 having the groove 119 are fixed to the device with a space therebetween, and are composed of a ring-shaped piston 115, a partition vane 117, and a coil spring 116 between the side plate 114 and the side plate case 118. The components of the rolling piston pump device 120 are arranged.

As shown in the external view of FIG. 17, a slewing bearing 418b having a small-diameter outer peripheral portion 418f is press-fitted and fixed to the slewing boss portion 418e of the slewing scroll 418, and the inner peripheral surface thereof serves as the crankshaft 414 of the drive shaft 404. The small-diameter outer peripheral portion 418f is disposed so as to engage and slide with the inner peripheral surface of the piston 115.

Oil hole A4 provided in the main body frame 405
Oil chamber A478a communicating with the discharge chamber oil sump 34 via 38a
Is the side plate case 118 press-fitted into the body frame 405.
And, it is isolated from the back pressure chamber 439 of the orbiting scroll 418 by the annular ring 94 attached to the end of the orbiting boss 418e.

The side plate 114 is in contact with the end surface 404a of the stepped portion of the drive shaft 404 to block the oil hole A438a side from the discharge side of the rolling piston type pump device 120.

The oil chamber A487a includes a rolling piston type oil supply pump device 120, a spiral oil groove 441b provided on the outer peripheral surface of the crankshaft 414, an oil chamber B478b provided at the end of the crankshaft 414, and a drive shaft 404. Axial oil hole 112a provided in the shaft core and spiral oil groove 441
a, it communicates with the back pressure chamber 439 through an oil hole B438b provided in the main body frame 405, and the open end of the oil hole B438b is interrupted intermittently by the reciprocating motion of the Oldham ring 24.

Other configurations are the same as in the case of FIG.
The operation of the scroll refrigerant compressor configured as described above will be described.

When the drive shaft 404 is rotated at the same time when the compressor is started, the crank shaft 414 makes an eccentric rotation motion, and the rotation preventing mechanism of the Oldham ring 24 allowed only the reciprocating motion causes the orbiting scroll 418 to rotate without rotating. It makes an orbital motion around the main axis of 404.

Following the orbiting movement of the orbiting bearing 418b fixed to the orbiting scroll 418, the piston 115 engaging and sliding on the orbiting bearing 418b is orbiting while rotating.
A suction / discharge action of a known oil supply pump in which the tip of the partition vane 117 is biased by the coil spring 116 and slidably contacts the piston 115 is performed.

The lubricating oil in the oil reservoir 34 of the discharge chamber is guided to the suction notch 114a via the oil hole A438a provided in the main body frame 405, and is discharged to the groove 119 of the side plate case 118 via the pump chamber. After that, the oil chamber B478b and the axial oil holes provided in the drive shaft 404 while lubricating the sliding surface of the slewing bearing 414 by using the screw pump action (viscous pump action) of the spiral oil groove 441b from the oil chamber A478a. 112a, and lubricates the sliding surface of the main bearing 412.

The lubricating oil sucked into the spiral oil groove 441a by the rolling piston type oil supply pump is delivered to the main bearing 412 by the screw pump action, and is joined with the lubricating oil discharged from the axial oil hole 112. , 22nd
As in the case of the figure, the oil is discharged to the oil sump 72 (not shown), the upper bearing (not shown), and the thrust bearing (not shown), and is supplied to the back pressure chamber 439 while being depressurized through the oil hole A438a. Then, the sliding parts are lubricated at the initial stage of compressor startup.

The opening end of the oil hole B438b to the back pressure chamber 439 is intermittently opened and closed by the reciprocating motion of the Oldham ring 24, and the continuous opening time is shortened as the rotation speed of the drive shaft 404 increases. Therefore, the inflow resistance into the back pressure chamber 439 increases. As a result, the amount of lubricating oil flowing into the back pressure chamber 439 is reduced.

After the pressure of the discharge refrigerant gas acting on the discharge chamber oil sump 34 rises with the lapse of time after the compressor is started, the lubricating oil in the discharge chamber oil sump 34 is also changed by the pressure difference with the back pressure chamber 439. After being supplied to the oil chamber A478a, the spiral oil groove 441
It is supplied to each sliding portion by the screw pump action of a and 441b.

Due to the pump oil supply which uses the differential pressure oil supply, the rolling piston type oil supply pump device 120, and the screw pump function together, when some gas is trapped in the lubricating oil or the oil supply capacity of the screw pump function is high. Continues to lubricate the sliding parts even when the operating area is reduced.

The other operations are the same as in the case of FIG. Further, according to this embodiment, the rolling piston type oil supply pump device 120 as the pump oil supply means for the bearing sliding portion is arranged in the oil chamber A478a on the upstream side of the bearing sliding portion, so that the compressor is operated at low speed. However, efficient pumping can be performed in a state in which the decrease in viscosity due to the temperature rise of the lubricating oil is small. Also, the oil chamber A4
Refrigerant gas mixed in the lubricating oil of 78a has a spiral oil groove 44.
1a, the oil hole B438b, and the back pressure chamber 439 to be sucked into the first compression chambers 61a and 61b, the refrigerant gas in the lubricating oil in the oil chamber A478a is reduced, and the cavitation phenomenon of the rolling piston type oil supply pump device 120 may occur. Does not occur,
In particular, since the refueling capacity during low speed operation is increased, the rolling piston refueling pump device 120 can be reduced in capacity and input.

(Embodiment 3) FIG. 19 is a vertical cross-sectional view of the main part around the oil supply pump device at the tip of the drive shaft in the scroll refrigerant compressor of the third embodiment of the present invention, similar to the case of FIG. In the stepped hole portion of the main bearing 512 of the main body frame 505 on the side of the orbiting scroll 518, a side plate 114b and a side plate case 118a having a crescent-shaped suction hole 114c and a protrusion 114d as shown in the external view of FIG. And are fixedly mounted with a space therebetween, and are composed of a ring-shaped piston 115a having a protrusion 115b and a groove 115c between a side plate 114b and a side plate case 118a, and, for example, Japanese Patent Publication No. 61-5.
Arranged are components of a swirling cylindrical piston type pump device 115 similar to the swirling cylindrical piston type pump device as described in 7935.

As shown in the external view of FIG. 21, the orbiting bearing 518b having the small-diameter outer peripheral portion 518f is press-fitted and fixed to the orbiting boss portion 518e of the orbiting scroll 518. The portion 518f is intermittently formed on the inner peripheral surface 115 of the piston 115a.
When the piston 115a abuts against d, the piston 115a swings and swings to act as a pump.

The projection 115b of the piston 115a is
Is a cutout groove 121 provided in the main body frame 505.
To prevent the piston 115a from rotating.

The side plate 114b comes into contact with the end surface 504a of the stepped portion of the drive shaft 504 and contacts the side of the oil hole A538a and the piston 1.
It is cut off from the circumferential surface side of 15a.

Oil hole A5 provided in the main body frame 505
Oil chamber A578a communicating with the discharge chamber oil sump 34 via 38a
Is a side plate 114b press-fitted into the main body frame 505 and an annular ring 94 attached to the ends of the turning boss 518e.
Is blocked from the back pressure chamber 539 of the orbiting scroll 518.

The oil chamber 578a is an orbiting cylindrical piston type oil supply pump device, a spiral oil groove 541b provided on the outer peripheral surface of the crankshaft 514, an oil chamber B578b provided at the end of the crankshaft 514, and a drive shaft 504. Is communicated with the back pressure chamber 539 through the axial oil hole 112b provided in the shaft core, the spiral oil groove 541a, and the oil hole B538b provided in the main body frame 504, and the opening end of the oil hole B538b is The Oldham ring 24 is intermittently shut off by the reciprocating motion.

Other configurations are the same as in the case of FIG.
The operation of the scroll refrigerant compressor configured as described above will be described.

The piston 115a in which the protruding portion 115b is movably locked in the cutout groove 121 of the main body frame 505 is
When the orbiting bearing 518b of the orbiting scroll 518 orbits, the orbiting bearing 518b performs an orbiting motion, and suction and discharge actions are performed. Since a gap is provided between the inner surface of the piston 115a and the small diameter outer peripheral portion 518f of the slewing bearing 518b,
The amount of movement of the piston 115a is smaller than twice the amount of eccentricity of the crankshaft 514. The discharge amount of the swirling cylindrical piston type oil supply pump is influenced by the size of this gap. In this embodiment, the amount of movement of the piston 115a is set to correspond to the amount of eccentricity of the crankshaft 514, and in particular, pump input is reduced by excessive oil supply during high speed operation.

Simultaneously with the activation of the compressor, the lubricating oil in the oil reservoir 34 of the discharge chamber is sucked into the suction hole 114c of the side plate 114b through the oil hole A538a, and then discharged from the groove 115c of the piston 115a to be discharged from the oil chamber. It is sent to A578a.

The lubricating oil in the oil chamber A578a is supplied in the spiral oil groove 5
Oil is supplied to the orbiting bearing 518b and the main bearing 512 by the screw pump action of 41b, and is used for lubrication of each sliding surface.

The description of the operation thereafter is the same as that of the above-mentioned example, and the description thereof is omitted. And according to this embodiment,
As the positive displacement pump device, one outer peripheral portion of the orbiting bearing 518b of the sliding coupling portion between the drive shaft 504 and the orbiting scroll 518 and an inner surface of an annular piston 115a which is rotationally locked and arranged in the cylinder are provided. A swirling cylindrical piston type pump in which the piston 114a is slidably contacted with each other in a loosely engaged state and the swinging motion of the piston 114a follows the swiveling motion of the swiveling scroll 518 to pump between the inner wall of the cylinder and the outer peripheral surface of the annular piston 115a. Since the device 115 is used, the piston 115a of the orbiting cylindrical piston type pump device 115 is provided.
However, a swinging motion less than the orbiting diameter of the orbiting scroll 518 can be applied from the inside of the piston 115a to perform a pumping action with a small input.

(Embodiment 4) FIG. 22 is a vertical cross-sectional view of the main part around the oil supply pump device at the tip of the drive shaft in the scroll refrigerant compressor according to the fourth embodiment of the present invention. The side plate case 11 having a crescent-shaped suction hole 118c as shown in the external view of FIG. 23 in the stepped hole portion of the main bearing 612 of the main body frame 605 on the side of the orbiting scroll 618.
8b and the side plate case 118a are mounted and fixed with a space therebetween, two vane grooves 124 and two discharge holes 125 are provided between the side plate cases 118a and 118b, and the drive shaft 604 is provided.
The so-called slide vane type oil supply pump device 126a, which is composed of a rotor 122 fixed to the vane groove and two vanes 123 mounted in each vane groove 124 and reciprocating in the vane groove 124, is arranged.

Oil hole A6 provided in the body frame 605
Oil chamber A678a communicating with the discharge chamber oil sump 34 via 38a
Is a side plate case 118 press-fitted into the body frame 605.
The back pressure chamber 639 of the orbiting scroll 618 is shut off by an annular ring 94 attached to the end of the orbiting boss 618e.

The oil chamber A678a is a slide vane type oil supply pump device, a spiral oil groove 641b provided on the outer peripheral surface of the crankshaft 614, an oil chamber B678b provided at the end of the crankshaft 614, and a shaft of the drive shaft 604. It communicates with the back pressure chamber 639 via the axial oil hole 112c provided in the core, the spiral oil groove 641a, and the oil hole B638b provided in the main body frame 604, and the open end of the oil hole B638b is the Oldham ring. It is intermittently shut off by the reciprocating movement of 24.

Other configurations are the same as in the case of FIG.
The operation of the scroll refrigerant compressor configured as described above will be described.

Simultaneously with the startup of the compressor, the rotor 122 fixed to the drive shaft 604 rotates, and the vane 123 slidably mounted on the rotor 122 receives its own centrifugal force and moves to the outer peripheral side of the rotor 123. As a result, the pump chamber is partitioned, and well-known suction / discharge operations are performed.

The lubricating oil in the oil reservoir 34 of the discharge chamber is the oil hole A638.
It is sucked from the suction hole 118c of the side plate case 118b via a and discharged to the oil chamber A638a via the discharge hole 125.

When the drive shaft 604 rotates at a high speed and the pump chamber pressure rises above the set pressure, the lubricating oil force acting on the tip of the vane 123 from the pump chamber side becomes larger than the centrifugal force of the vane 123. As a result, the vane 123 retracts, widens the gap of the pump chamber, and controls the pump oil supply capacity.

Further, at the time of extremely low speed operation, the centrifugal force of the vanes 123 is small, so that the compartment formation of the pump chamber becomes insufficient and the pump oil supply action is suppressed. As a result, the liquid refrigerant staying at the bottom of the discharge chamber oil sump 34 is not supplied to the bearing sliding portion at the initial stage of the cold start of the compressor.

The liquid refrigerant staying in the discharge chamber oil sump 34 with the lapse of time after the compressor is started is separated from the lubricating oil while firing, and moves to the upper part of the motor chamber 6, whereupon the normal operating speed range of the compressor. In this case, the oil supply pump action is sufficiently exerted, and the lubricating oil containing no refrigerant is supplied to each sliding portion.

The other operations are the same as those in the above-mentioned case, and therefore their explanations are omitted. Further, according to this embodiment, as a positive displacement pump device, a vane 123 for advancing / retracting the rotor 122 coaxially rotating with the drive shaft 604 and the vane groove 124 provided in the rotor 122 to partition and seal the pump chamber. The slide vane type oil supply pump device 126a consisting of the above and the urging force of the vane 123 on the cylinder wall is made to depend only on the centrifugal force based on the own weight of the vane 123. Since the contact force at the tip of is small, the pump input can be made small.

Although the refrigerant compressor has been described in the above embodiment, similar effects can be expected in the case of other gas compressors such as oxygen, nitrogen and helium which use lubricating oil.

Further, in the above-mentioned embodiment, the structure of the vertical compressor is shown and the effect thereof is explained. However, the same effect can be expected in the structure of the horizontal compressor.

[0159]

As is apparent from the above embodiment, claim 1
In the invention described above, a positive displacement pump device driven and driven by the drive shaft is arranged in either the inside of the main body frame supporting the drive shaft or the inside of the orbiting scroll, and the positive displacement pump device is arranged in the sealed case by the positive displacement pump device. A bearing oil supply passage that sucks in and discharges lubricating oil from the oil sump and returns it to the oil sump is formed.In the middle of the bearing oil supply passage, a main bearing and a drive shaft that support the drive shaft and are close to the compression chamber are provided. The sliding portion of the orbiting bearing that engages with the orbiting scroll is arranged, the oil passage on the suction side and the oil passage on the discharge side of the positive displacement pump device are provided in the main body frame, and the oil passage on the suction side serves as an oil reservoir. It is a communication. With this configuration, the oil passages on the suction side and the discharge side of the positive displacement pump device can be shortened, and the rising of oil supply to the sliding portion at the early stage of low speed compressor startup can be accelerated and the sliding at the initial stage of compressor startup can be accelerated. The part durability can be improved.

Further, since the lubricating oil is supplied to the bearing sliding portion without deteriorating the lubrication characteristic due to the heating of the motor, it is possible to effectively exert the required lubricating action and reduce the compressor input. .

According to a second aspect of the present invention, the positive displacement pump device is a rotary pump device, and in order to prevent the discharge side lubricating oil of the rotary pump device from flowing back to the suction side, either of the suction / discharge passages is provided. A partition plate that also has one of the functions is arranged on the side surface side of the pump chamber of the rotary pump device. According to this configuration, the oil supply efficiency of the rotary pump device is improved, and the oil supply amount during the low speed operation of the compressor is secured,
It is possible to realize energy-saving operation by continuing low-speed operation.

Further, it is possible to form an oil passage at a desired position, and it is possible to reduce the size of the compressor by saving the space around the rotary pump device.

According to the third aspect of the present invention, the drive shaft is driven by the drive shaft between the end of the crankshaft provided at the tip of the drive shaft so that the drive shaft engages with the orbiting scroll and the bottom of the orbiting bearing. A positive displacement rotary pump device is arranged, the suction side of the positive displacement rotary pump device communicates with the oil reservoir in the sealed case via at least the crankshaft, and the discharge side of the positive displacement rotary pump device is connected to the drive shaft. A bearing oil supply passage communicating with an oil reservoir via at least the main bearing through an axial oil hole provided therein is provided. According to this structure, the positive displacement rotary pump device can be arranged with a simple structure, and the cost can be reduced.

Further, it becomes possible to dispose the slewing bearing and the main bearing on the suction side and the discharge side of the positive displacement rotary pump device.
By providing equal amount of oil to both bearings, it is possible to avoid excessive and insufficient oil supply, and to prevent bearing seizure during low speed operation.

According to the fourth aspect of the present invention, the oil sump is used as the discharge chamber oil sump on which the discharge pressure acts, and the lubricating oil in the discharge chamber oil sump is branched and depressurized from the discharge side of the positive displacement pump device to prevent the orbiting scroll from rotating. A differential pressure oil supply passage that supplies oil to a compression bearing or a suction chamber after oil is supplied to a thrust bearing that supports the compression chamber side and is arranged in the main body frame is provided. According to this configuration, the oil supply head loss of the positive displacement pump device is reduced, and the pump input can be reduced.

Further, it is possible to sufficiently supply the sliding portion supporting the orbiting scroll with oil even when the compressor is operating at a low speed, thereby reducing the compressor input and improving the compression efficiency by supplying oil to the compression chamber. Produce an effect.

According to a fifth aspect of the present invention, the orbiting scroll is made of a material having a higher thermal conductivity and a larger thermal expansion coefficient than those of the positive displacement rotary pump device and the drive shaft. According to this configuration, even when the temperature of the positive displacement rotary pump device is increased due to high-speed operation of the compressor, the gap between the housing portion in which the positive displacement rotary pump device is disposed and the positive displacement rotary pump device is abnormally reduced. It is possible to avoid the above and prevent an excessive input increase of the positive displacement rotary pump device.

According to a sixth aspect of the present invention, the positive displacement rotary pump device is arranged in the lap support disk of the orbiting scroll. With this configuration, the center of gravity of the orbiting body member including the orbiting scroll is brought closer to the compression chamber, the orbiting motion of the orbiting scroll is stabilized, and the compressor vibration can be reduced.

According to a seventh aspect of the invention, the oil surface of the oil sump is arranged at a position higher than that of the positive displacement pump device. According to this configuration, the positive displacement pump device can be easily sucked, the amount of oil supply can be increased during low-speed operation of the compressor, and the compressor input can be reduced and the durability can be improved by sufficient oil supply to the bearing sliding portion. The effect that it can be achieved is produced.

[Brief description of drawings]

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

[Fig. 2] Exploded view of main parts of the compressor

FIG. 3 is a partial cross-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.

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 of the compressor.

FIG. 8 is a partial sectional view of a main bearing portion of the compressor.

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

FIG. 10 is a perspective view of a partition plate as a side plate of the trochoid pump device in the compressor.

FIG. 11 is a partial sectional view of a thrust bearing portion of the compressor.

FIG. 12 is a partial sectional view of the thrust bearing portion.

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

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

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

FIG. 16 is a partial vertical sectional view of a main bearing portion of a scroll refrigerant compressor according to a second embodiment of the present invention.

FIG. 17 is a perspective view of the bearing component shown in FIG.

FIG. 18 is an exploded perspective view of components of the oil supply pump device in the compressor.

FIG. 19 is a partial vertical cross-sectional view of the main bearing portion of the scroll refrigerant compressor according to the second embodiment of the present invention.

FIG. 20 is an exploded perspective view of components of the oil supply pump device in the compressor.

21 is a perspective view of the bearing component shown in FIG.

FIG. 22 is a partial vertical cross-sectional view of the main bearing portion of the scroll refrigerant compressor according to the third embodiment of the present invention.

FIG. 23 is an exploded perspective view of components of the oil supply pump device in the compressor.

FIG. 24 is a vertical sectional view of a conventional scroll compressor.

FIG. 25 is a vertical cross-sectional view of another conventional scroll compressor.

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

FIG. 27 is a detailed vertical sectional view of the pump device in FIG.

28 is a cross-sectional view taken along the line AA in FIG.

FIG. 29 is a vertical sectional view of a conventional scroll compressor.

30 is a partial cross-sectional view around the pump device in FIG. 29.

31 is a cross-sectional view taken along the line AA in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Sealed case 3 Motor 15 Fixed scroll 15a Fixed scroll wrap 15b End plate 16 Discharge port 17 Suction chamber 24 Rotation prevention member 34 Discharge chamber oil sump 106 Trochoid pump device 110 Partition plate 112 Oil hole 114, 114b Side plate 115 Swiveling cylindrical piston type pump device 118a, 118b Side plate case 120 Rolling piston type oil supply pump device 126a Slide vane type oil supply pump device 220 Thrust bearing 304 Drive shaft 305 Main body frame 312 Main bearing 314 Crankshaft 318 Orbiting scroll 318a Orbiting scroll wrap 318b Orbiting bearing 318c Wrap support disk

Continuation of the front page (51) Int.Cl. ⁶ Identification number Office reference number FI technical display location F04C 29/02 311 F04C 29/02 311C

Claims (7)

[Claims] 1. An orbiting scroll wrap on a lap support disk forming a part of an orbiting scroll is oscillatably and rotatably meshed with a spiral fixed scroll wrap formed on one surface of an end plate forming a part of the fixed scroll. , A spiral compression space is formed between both scrolls, a discharge port is provided at the center of the fixed scroll wrap, and a suction chamber is provided outside the fixed scroll wrap, and the compression space is discharged from the suction side to the discharge side. The lap support disk supports the end plate, the drive shaft, and the main bearing at least near the compression chamber and the lap support in order to compress the fluid by being divided into a plurality of compression chambers that continuously move toward It is arranged between the disc and a main body frame having a thrust bearing supporting the side opposite to the compression chamber, and the swivel swath is provided between the lap support disc and the main body frame. The rotation preventing member of the roll is engaged,
In a configuration in which a scroll compression mechanism that orbits the orbiting scroll through a orbiting bearing that engages the drive shaft and the lap support disk and a motor that is connected to the drive shaft are housed in a sealed case, the inside of the main body frame And a positive displacement pump device driven and operated by the drive shaft is disposed in one of the inside of the orbiting scroll, and the positive displacement pump device sucks in the lubricating oil in the oil reservoir arranged at the bottom of the motor. A bearing oil supply passage that discharges and returns to the oil reservoir is formed, and a sliding portion of the main bearing and the orbiting bearing is arranged in the middle of the bearing oil supply passage, and oil on the suction side of the positive displacement pump device is disposed. A scroll gas compressor in which a passage and an oil passage on the discharge side are provided in the main body frame, and the oil passage on the suction side communicates with the oil reservoir. 2. A positive displacement pump device is used as a rotary pump device, and also has a function of one of a suction passage and a discharge passage in order to prevent the discharge side lubricating oil of the rotary pump device from flowing back to the suction side. The scroll gas compressor according to claim 1, wherein the partition plate is disposed on a side surface side of a pump chamber of the rotary pump device. 3. A positive displacement rotation driven by rotation of the drive shaft between an end of a crankshaft provided at a tip of the drive shaft and a bottom of an orbiting bearing so that the drive shaft engages with the orbiting scroll. Type pump device is disposed, the suction side of the positive displacement rotary pump device and the oil reservoir in the closed case are communicated with each other via at least the clans shaft, and the discharge side of the positive displacement rotary pump device is driven by the drive device. The scroll gas compressor according to claim 1 or 2, further comprising a bearing oil supply passage that communicates with the oil reservoir via at least a main bearing via an axial oil hole provided in the shaft. 4. An oil sump is used as a discharge chamber oil sump to which a discharge pressure acts, and lubricating oil in the discharge chamber oil sump is branched and depressurized from the discharge side of a positive displacement pump device to supply oil to a thrust bearing and then to a compression chamber. The scroll gas compressor according to claim 1, further comprising a differential pressure oil supply passage for supplying to either one of the suction chambers. 5. The scroll gas compressor according to claim 3, wherein the orbiting scroll is made of a material having a higher thermal conductivity and a larger thermal expansion coefficient than those of the positive displacement pump device and the drive shaft. 6. The scroll gas compressor according to claim 5, wherein the positive displacement pump device is arranged in the lap supporting disk. 7. The scroll gas compressor according to claim 1, wherein the oil level of the oil sump is arranged at a position higher than that of the positive displacement pump device.