JPH07269477A - Scroll gas compressor - Google Patents

Abstract

PURPOSE:To perform lubrication to two bearings with a simple means as well as to miniaturize a compressor by supporting a driving shaft at both sides of a motor. CONSTITUTION:In a vertical scroll gas compressor housed with an enclosed case 1 after setting up a compression zone in the lower part and a motor 3 in the upper part respectively, a bearing frame supporting a driving shaft 4 together with a body frame 5 is set up in an upper part of this motor 3, lubricating oil separated from compressed gas in an interspace between an upper end of the enclosed case 1 and the bearing frame 9 is to be collected in the upper part of an upper bearing 10 of the bearing frame 9, and thereby a central part of the bearing frame 9 is recessed at the side of the motor 3, and then this recessed bottom part and the upper bearing 10 are adjoined to each other.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to bearing oil supply for scroll gas compressors.

[0002]

2. Description of the Related Art A scroll compressor is provided with a suction chamber on the outer periphery and a discharge port provided in the center of a spirally-shaped compression chamber. The compression fluid flows in one direction and reciprocatingly compressed. It is generally known that it has basically low vibration and low noise characteristics based on the compression principle that load fluctuation during compression is extremely smaller than that of a compressor or a rotary compressor.

Further, in the compression chamber formed by both the fixed scroll member and the orbiting scroll member, the compression pressure when the fluid is compressed generates a force to separate the members in the axial direction, thereby sealing the compression chamber. Since it becomes incomplete, leakage of compressed fluid increases, and efficiency decreases, so there is also known a configuration in which the compressed fluid pressure is applied to the rear surface of the orbiting scroll to apply an axial pressing force to prevent both members from separating. FIG. 13 and FIG. 14 are examples thereof.

The drawing shows an orbiting scroll 1001 connected to a drive pin 1007a at the tip of a drive shaft 1007.
Of the fixed scroll 1002 is a mirror plate 1 of the fixed scroll 1002.
002a and the frame 1008 are supported by a minute gap, an intermediate pressure in the middle of compression is introduced to the back surface of the orbiting scroll 1001, and the back pressure is urged to the orbiting scroll 1001 to solve the above problems. When the compression load, the inertial force of the rotating member, or the like changes at the time of starting, stopping, or high-speed operation of the compressor, the orbiting scroll 1001 is prevented from tilting with respect to the main axis of the drive shaft 1007, and The compression chamber is sealed by maintaining a gap to improve the compression efficiency. Also, the orbiting scroll 10
01 tilts with respect to the main axis of the drive shaft 1007, compressive load, and the end plate 1001 of the orbiting scroll 1001.
The sliding resistance between a and the end plate 1002a of the fixed scroll 1002 depends on the drive pin 1 at the tip of the drive shaft 1007.
It acts on 007a and gives a bending moment to the drive shaft 1007. In order to prevent the bearing supporting the drive shaft 1007 from suffering a one-sided contact phenomenon and resulting in bearing damage due to this bending moment, there is a tendency to increase the distance between the bearings supporting the drive shaft 1007 (JP-A-55).
No. 142902).

Further, for example, a structure which is further improved with respect to the bearing portion contact phenomenon is disclosed in Japanese Patent Laid-Open No. 62-12628.
No. 5 is disclosed. That is, the scroll compression part is stored in the upper part of the closed container, the motor is stored in the lower part, the oil reservoir for bearing lubrication is arranged in the bottom part, and the bearings supporting the drive shaft connected to the motor are arranged on both sides of the motor. It is the configured configuration.

[0006]

However, in these structures in which the bearings are arranged on both sides of the motor, the space where the motor and the oil reservoir are located has a low pressure equal to the suction pressure, and the high pressure space having the discharge pressure is located above the compression section. Since it requires a wide high pressure space for separating the lubricating oil used for sealing the compression chamber gap and lubricating the sliding surface from the discharge gas, there is a problem that the height of the compressor becomes high. .

On the other hand, in order to reduce the size of the compressor and facilitate the supply of lubricating oil to the compression section, a construction in which a closed container in which the compression section and the motor are arranged has a high-pressure space is disclosed in Japanese Utility Model Laid-Open No. 57-69991. Has been done.

In this structure, the scroll compression unit is arranged in the lower part of the closed container, the motor is arranged in the upper part, the drive shaft connected to the motor is supported only on the compression unit side, and the discharge pipe is connected to the upper end of the closed container. However, since the structure is similar to that of the conventional rotary compressor, there remains a problem that the above-mentioned bearing piece contact phenomenon peculiar to the scroll compressor cannot be avoided.

As a matter of course, it is conceivable to arrange the bearing on the upper part of the motor, but it is necessary to solve the method of refueling the bearing.

[0010]

In order to solve the above problems, a scroll gas compressor according to the present invention has a bearing frame for supporting a drive shaft together with a main body frame of a compression unit disposed on an upper portion of a motor, and an upper end of a hermetically sealed case. The lubricating oil separated from the compressed gas in the space between the bearing frame and the bearing frame causes the central part of the bearing frame to be recessed toward the motor side in order to collect in the upper part of the upper bearing of the bearing frame. And are adjacent to each other.

[0011]

According to the present invention, the discharge gas sent from the compression section to the motor section after the motor cooling and oil separation has flowed into the space between the upper end of the closed case and the bearing frame.
The lubricating oil is separated again by colliding with the inner wall of the closed case.
This lubricating oil is collected and stored in the recessed portion at the center of the bearing frame and supplied to the bearing that supports the drive shaft.

[0012]

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

In FIGS. 1 to 12, reference numeral 1 denotes an iron-made hermetic case, the inside of which is a high-pressure atmosphere communicating with the discharge chamber 2, a motor 3 is arranged in the upper part, and a compression part is arranged in the lower part.
The interior of the hermetically sealed case 1 is partitioned into a motor chamber 6 and a discharge chamber 2 by a body frame 5 of a compression unit that supports a drive shaft 4 fixed to the rotor 3a.

The main body frame 5 is made of an aluminum alloy having excellent heat conduction characteristics mainly for weight reduction and heat dissipation of the bearing portion, and an iron liner 8 having excellent weldability is shrink-fitted and fixed to the outer peripheral portion thereof. The outer peripheral surface of the liner 8 is inscribed in the entire circumference of the closed case 1 and is partially welded and fixed.

The outer peripheral portions of both ends of the stator 3b of the motor 3 are supported and fixed by the bearing frame 9 and the main body frame 5 which are internally fixed to the hermetically sealed case 1. The drive shaft 4 includes an upper bearing 10 provided on the bearing frame 9, a lower bearing 11 provided on an upper end portion of the main body frame 5, a main bearing 12 provided on a central portion of the main body frame 5, an upper end surface of the main body frame 5. An eccentric bearing 14 which is supported by a thrust ball bearing 13 provided between the rotor 3a of the motor 3 and the lower end surface of the motor 3 and is eccentric from the main shaft of the drive shaft 4 is provided at the lower end thereof.

A fixed scroll 15 made of aluminum alloy is fixed to the lower end surface of the main body frame 5. The fixed scroll 15 is a spiral fixed scroll wrap 15a.
And an end plate 15b. A discharge port 16 that opens to the winding start portion of the fixed scroll wrap 15a is provided in the center of the end plate 15b so as to also open in the discharge chamber 2, and a suction chamber 17 is provided in the outer peripheral portion of the fixed scroll wrap 15a. .

A spiral orbiting scroll wrap 18 which meshes with the fixed scroll wrap 15a to form a compression chamber.
a and the swivel shaft 18 supported by the eccentric bearing 14 of the drive shaft 4.
The orbiting scroll 18 made of an aluminum alloy, which is composed of a lap support disc 18c which is upright with b, is arranged so as to be surrounded by the fixed scroll 15, the main body frame 5 and the drive shaft 4, and the outer peripheral portion of the orbiting shaft 18b. A sleeve 94 made of a high-strength steel material is shrink-fitted and fixed to the lap supporting disc 1
The surface of 8c is hardened.

A spacer 21 is provided between the thrust bearing 20 which is fixed to the split pin type parallel pin 19 fixed to the main body frame 5 and is movable only in the axial direction, and the end plate 15b of the fixed scroll 15. Therefore, the axial dimension of the spacer 21 is about 0.015 to less than the thickness of the lap support disk 18c in order to improve the sealing property of the sliding surface by the oil film.
It is set larger by 0.020 mm.

Thrust bearing 20 of lap support disk 18c
An annular groove 81 is provided in the outermost peripheral portion of the sliding surface with and, and an annular ring 82 made of a sintered alloy and having elasticity is mounted in the inside thereof with a minute gap, and the maximum axial gap is 0.025.
When the thickness is at least mm, it is possible to form an oil film. Further, the annular ring 82 is open in a free state as shown in FIG. 4 with a cut portion that is inclined and cut with respect to the circumferential direction, and the annular ring 82 is formed in the annular groove 81. When mounted, the outer surface of the annular ring 82 is set so as to be in close contact with the outer surface of the annular groove 81 by its elastic force and have a minute gap. The width of the annular groove 81 and the annular ring 82
The width is not the same across the entire circumference, and is configured such that the annular ring 82 cannot make one rotation within the annular groove 81.

The eccentric bearing space 36 between the bottom part of the eccentric bearing 14 of the drive shaft 4 and the shaft part of the orbiting shaft 18b of the orbiting scroll 18 and the outer peripheral space 37 of the lap supporting disk 18c are:
The swivel shaft 18b and the wrap support disk 18c communicate with each other through an oil hole A38a.

The thrust bearing 20 is made of a sintered alloy and is shown in FIG.
As shown in FIG. 6, the central portion has two parallel straight line portions,
It is formed by penetrating into a shape consisting of two arcuate curved portions 23 connected to it.

The rotation preventing member (hereinafter referred to as Oldham ring) 24 of the orbiting scroll 18 is made of a light alloy or a reinforced fiber composite resin material suitable for sintering molding, injection molding, etc., and also has oil impregnation characteristics. , A thin annular plate 24a whose both surfaces are parallel to each other, and a pair of parallel key portions 24b provided on one surface of the annular plate 24a. The outer contour of the annular plate 24a is two parallel linear portions 25 and two continuous linear portions 25. As shown in FIG. 6, the straight-line portion 25 is engaged with the straight-line portion 22 of the thrust bearing 20 with a small clearance and is slidable, and the side surface 24c of the parallel key portion 24b is a straight-line portion. 1 and 2 are orthogonal to each other in the central portion of 25 and engage with a pair of key grooves 71 provided in the lap support disk 18c of the orbiting scroll 18 with a minute gap, and are set to have a slidable shape. ing.

The inner contour of the annular plate 24a has a shape similar to the outer contour. Further, the dent portion 24d provided at the base of the parallel key portion 24b also serves as a passage for the lubricating oil. In addition, the dent portion 24 provided in the arc-shaped curved portion
Reference numeral 0e is a similar lubricating oil passage.

As shown in FIGS. 1 and 3, a release gap 27 of about 0.1 mm is provided between the main body frame 5 and the thrust bearing 20, and the main body frame 5 is also annularly opposed to the release gap 27. A groove 28 is provided and a rubber seal ring 70 surrounding the annular groove 28 is mounted between the main body frame 5 and the thrust bearing 20.

The upper portion of the motor chamber 6 and the discharge chamber 2 are connected to the bypass discharge pipe 29 penetrating the side wall of the sealed case 1.
The opening position of the bypass discharge pipe 29 to the motor chamber 6 faces the side surface of the upper coil end 30 of the stator 3b, and the upper open end of the bypass pipe 29 and the closed case 1 are communicated with each other.
The discharge pipe 31 connected to the upper end of the through hole 32 provided in the bearing frame 9 and the punching metal 33 having a large number of small holes arranged between the upper surface of the closed case 1 and the bearing frame 9. It is in communication.

The discharge chamber oil sump 34 provided in the lower portion of the motor chamber 6 communicates with the upper portion of the motor chamber 6 and a cooling passage 35 provided by cutting a part of the outer periphery of the stator 3b of the motor 3. . Further, the discharge chamber oil sump 34 communicates with the annular groove 28 via an oil hole B38b provided in the main body frame 5, and also in the back pressure chamber 39 of the orbiting scroll 18 in which the Oldham ring 24 is arranged, the main bearing 12 Of the oil groove A40, which is communicated with the sliding part of
It also communicates with the eccentric bearing space 36 via a.

Further, an oil hole B provided in the body frame 5
38b also communicates with the spiral oil groove 41 provided on the surface of the lower shaft portion 4a corresponding to the lower bearing 11 of the drive shaft 4, and the spiral oil groove 41 is wound in the normal direction of the drive shaft 4. It is provided so that a screw pump action utilizing the viscosity of the lubricating oil is generated when the lower bearing 4a is formed.

As shown in FIGS. 7 and 8, the fixed scroll 15
Is an arc-shaped suction passage 42 communicating both ends of the suction chamber 17.
Is provided, and a circular suction hole 43 orthogonal thereto is also provided in a direction perpendicular to the side surface of the fixed scroll wrap 15a, and the bottom portion of the suction hole 43 is a flat surface and reaches the side surface of the suction passage 42. .

Further, as shown in FIG. 9, the center of the suction hole 43 is displaced from the bottom surface 44 of the suction passage 42, and the opening size W45 to the suction passage 42 is smaller than the diameter size of the suction hole 43. There is. A suction pipe 47 of an accumulator 46 is connected to the suction hole 43, and the suction hole 43
Between the bottom surface 44 and the suction tube end surface 48, the inner diameter of the suction tube 47 and the suction hole depth dimension L499L between the suction tube end surface 48 and the bottom surface 44 are large, and are larger than the opening dimension W45. A check valve 50 of steel plate is arranged.

The surface of the check valve 50 has a poor oil wetting property and is coated with Teflon or rubber having a high elasticity.

The second compression chamber 51, which does not communicate with the suction chamber 17 or the discharge chamber 2, and the outer peripheral space, have a small diameter injection hole 52 formed in the second compression chamber 51 and provided in the end plate 15b. 15b and an insulating cover 53 made of resin, an injection groove 54 formed by an insulating cover 53 and an injection passage 55 formed by a stepped oil hole C38c opening in the outer peripheral space 37 are communicated to the large diameter portion 56 of the oil hole C38c. A check valve 58 made of a thin steel plate having a notch 57 in a part of its outer circumference as shown in FIG. 10 and a coil spring 59 are arranged.

The coil spring 59 has a heat insulating cover 53.
The check valve 58 is constantly urged by being pressed by. As shown in FIGS. 11 and 12, the opening position of the oil hole C38c to the outer peripheral space 37 reaches the vicinity of the end of the volume reduction process of the third compression chamber 60 communicating with the discharge port 16 and the orbiting scroll 1
The outer peripheral space 37 communicates with the oil hole C38c when 8 moves (see FIG. 11), and is provided at a position blocked by the lap support disc 18c at other times (see FIG. 12). .

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

1 to 12, when the drive shaft 4 is rotationally driven by the motor 3, the orbiting scroll 18 orbits, and the suction refrigerant gas containing lubricating oil from the refrigeration cycle connected to the compressor is accumulated in the accumulator 46. To the suction chamber 17 through the suction pipe 47, the suction hole 43, and the suction passage 42, and the first compression chambers 61a and 61b formed between the orbiting scroll 18 and the fixed scroll 15 into the compression chamber. The second that is confined and always becomes a closed space
It is sequentially transferred and compressed to the compression chambers 51a and 51b and the third compression chambers 60a and 60b, and discharged to the discharge chamber 2 via the discharge port 16 in the central portion.

The discharge refrigerant gas containing the lubricating oil returns to the motor chamber 6 in the compressor again via the bypass discharge pipe 29 that is piped to the outside of the compressor, and is then discharged from the discharge pipe 31 to the external refrigeration cycle. However, when flowing into the motor chamber 6,
It collides with the side surface of the upper coil end 30 of the motor 3 and adheres to the surface of the motor winding. As a result, a part of the lubricating oil is separated, and then, when passing through the hole 32 provided in the bearing frame 9, when changing the flow direction or when passing through the small hole of the punching metal 33, the inertia of the lubricating oil Lubricating oil is effectively separated by force or surface adhesion. A part of this lubricating oil is collected and stored in the recessed portion in the central portion of the bearing frame 9, is supplied to the upper bearing 10, and then passes through the cooling passage 35 together with the remaining lubricating oil to cool the motor 3 and the discharge chamber. Collected in the oil sump 34.

The drive shaft 4, which receives a bending moment from the orbiting shaft 18b of the orbiting scroll 18 and tends to incline within the sliding surface of the upper bearing 10 and the main bearing 12, is supported by an oil film generated on the sliding surface.

On the other hand, the lubricating oil in the discharge chamber oil sump 34 is supplied to the thrust ball bearing 13 by the viscous pumping action of the spiral oil groove 41 provided on the surface of the lower shaft portion 4a of the drive shaft 4, and the lower shaft. When the lubricating oil passes through the minute bearing gap at the end of the portion 4a, the oil film sealing action cuts off the discharge refrigerant gas atmosphere of the motor chamber 6 and the upstream space of the main bearing 12.

The lubricating oil containing the dissolved refrigerant gas in the discharge chamber oil sump 34 is reduced to an intermediate pressure between the discharge pressure and the suction pressure when passing through the minute gap of the main bearing 12, and flows into the back pressure chamber 39. To do. After that, the oil gradually flows through the oil groove A40a of the eccentric bearing 14, the eccentric bearing space 36, and the oil hole A38 passing through the orbiting scroll 18 into the outer peripheral space 37 while being gradually decompressed, and the oil groove C38c that is further intermittently opened and the injection groove 5 are provided.
4, through the injection holes 52a and 52b, and flows into the second compression chambers 51a and 51b, and lubricates each sliding surface in the middle of the passage.

The lubricating oil injected into the second compression chambers 51a and 51b merges with the lubricating oil that has flowed into the compression chamber together with the suction refrigerant gas from the refrigeration cycle outside the compressor, and forms an oil film in the minute gap between the adjacent compression chambers. The compressed refrigerant gas is leaked to the discharge chamber 2 again together with the compressed refrigerant gas while lubricating the sliding surface between the compression chambers.

Since the discharge chamber oil sump 34 also communicates with the annular groove 28 and the release gap 27, the thrust bearing 20
Is urged by its back pressure to come into contact with the spacer 21. Then, the lap support disk 18 of the orbiting scroll 18
c is the end plate 1 of the thrust bearing 20 and the fixed scroll 15.
A small gap is held between the end face of the fixed scroll wrap 15a and the lap support disc 18c, and a gap between the end face of the orbiting scroll wrap 18a and the end plate 15b is also small. Are held in place to reduce refrigerant leakage between adjacent compression chambers.

An annular ring 82 made of an elastic body that follows the orbiting scroll 18 and makes an orbiting motion scrapes the lubricating oil on the sliding surface of the thrust bearing 20 in contact with the lap support disk 18c to scrape off the annular groove 81. Collected in the periphery, the gap between the annular groove 81 and the annular ring 82 and the gap between the annular ring 82 and the thrust bearing 20 are oil-sealed. As a result, the back pressure chamber 39 is always filled with lubricating oil, the sliding surfaces of the main bearing 12 and the slewing bearing 14 are also filled with lubricating oil, the inclination of the drive shaft 4 in the bearing gap is prevented, and the upper portion is prevented. Drive shaft 4 in bearing 10
Assists the smooth sliding of.

As described above, according to the above-mentioned embodiment, the scroll compression mechanism is arranged in the lower part of the closed case 1, the motor 3 connected to the drive shaft 4 is arranged in the upper part thereof, and the discharge pipe 31 is connected to the closed case 1. After the compressed refrigerant discharged from the discharge port 16 passes through the discharge chamber 2 and the bypass discharge pipe 29 to cool the coil end 30 of the motor 3, the compressed pipe discharged from the discharge pipe 31 is closed.
In the configuration provided with the discharge refrigerant passage for discharging to the outside of the
A bearing frame 9 that supports the drive shaft 4 together with the main body frame 5 is arranged above the motor 3, and the lubricating oil separated from the refrigerant in the space between the upper end of the hermetic case 1 and the bearing frame 9 is the upper portion of the bearing frame 9. In order to collect in the upper part of the bearing 10, the central part of the bearing frame 9 is recessed on the motor 3 side, and the recessed bottom part and the upper bearing 10 are adjacent to each other.
Lubricating oil separated from the refrigerant in the space between the upper end of the sealed case 1 and the bearing frame 9 is collected and stored in the central recess of the bearing frame 9 to easily supply oil to the upper bearing 10 that supports the drive shaft 4. You can As a result, the drive shaft 4 which receives a bending moment from the orbiting scroll and tends to incline within the sliding surface of the upper bearing 10 and the main bearing 12 of the main body frame 5 is supported by the oil film generated on the sliding surface, and the bearing piece is supported. It rotates smoothly without hitting, and the original low vibration and low noise characteristics of the scroll compressor can be exhibited. Further, it is possible to reduce the input of the bearing sliding portion and improve the durability.

Further, by disposing the bearing frame 9, the diffusion of the refrigerant airflow generated by the rotation of the rotor 3a of the motor 3 does not propagate to the upper space of the sealed case 1, so that the upper end wall of the sealed case 1 and the bearing The oil separation efficiency with the frame 9 is also improved, and the amount of oil discharged to the outside of the compressor can be reduced.

Further, since the closed case 1 has a high-pressure space, it is possible to realize a vertical scroll refrigerant compressor which can be downsized without requiring a special space for separating lubricating oil from compressed refrigerant gas. You can

[0045]

As described above, according to the present invention, the scroll compression mechanism for rotating the orbiting scroll by engaging the rotation preventing member of the orbiting scroll between the main body frame supporting the drive shaft and the orbiting scroll is formed. The scroll compression mechanism is placed in the lower part of the sealed case, the motor connected to the drive shaft is placed in the upper part of the sealed case, and the discharge pipe is connected to the sealed case.The compressed gas discharged from the discharge port cools the motor and then the discharge pipe. In the configuration with a gas passage for discharging to the outside of the sealed case, a bearing frame that supports the drive shaft together with the main body frame is placed above the motor and separated from the compressed gas in the space between the upper end of the sealed case and the bearing frame. The collected lubricating oil collects on the upper part of the upper bearing of the bearing frame, so that the central part of the bearing frame is recessed toward the motor side, and the recessed bottom part and the upper bearing are By making contact with each other, the lubricating oil separated from the compressed gas in the space between the upper end of the sealed case and the bearing frame is collected and stored in the central recessed part of the bearing frame, and the lubricating oil to the upper bearing supporting the drive shaft is collected. Refueling is easy. As a result, the drive shaft, which receives a bending moment from the orbiting scroll and tends to incline within the sliding surface of the upper bearing and the bearing portion of the main body frame, is supported by the oil film generated on the sliding surface, resulting in bearing piece contact. It can rotate smoothly without any trouble and can exhibit the low vibration and low noise characteristics of the original scroll compressor. Further, it is possible to reduce the input of the bearing sliding portion and improve the durability.

Further, by disposing the bearing frame, the diffusion of the compressed air flow caused by the rotation of the rotor of the motor does not propagate to the upper space of the hermetically sealed case, so the space between the upper end wall of the hermetically sealed case and the bearing frame. The oil separation efficiency is improved, and the amount of oil discharged to the outside of the compressor can be reduced.

Further, since the inside of the closed case is a high pressure space,
It does not require a special space for separating the lubricating oil from the discharged gas, and can realize a vertical scroll gas compressor that can be miniaturized.

[Brief description of drawings]

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

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

FIG. 3 is a partial sectional view of a seal ring portion and a thrust bearing portion of the compressor.

FIG. 4 is an external view of a seal ring in the compressor.

FIG. 5 is an external view of an Oldham ring in the compressor.

FIG. 6 is an assembly external view of an Oldham mechanical section in the compressor.

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

FIG. 8 is an explanatory view of the position of the check valve in the suction pipe connecting portion of the compressor.

9 is a partial cross-sectional view taken along the line BB in FIG.

FIG. 10 is an external view of a check valve used in an oil supply passage of the compressor.

FIG. 11 is an explanatory diagram of movement of a compression chamber near a discharge port of the compressor.

FIG. 12 is an explanatory diagram of movement of a compression chamber near a discharge port of the compressor.

FIG. 13 is a vertical sectional view of a conventional scroll compressor.

FIG. 14 is a partially enlarged view of FIG.

[Explanation of symbols]

 1 Sealed Case 2 Discharge Chamber 3 Motor 3a Rotor 4 Drive Shaft 5 Body Frame 9 Upper Frame 10 Upper Bearing 12 Main Bearing 16 Discharge Port 18 Orbiting Scroll 29 Bypass Discharge Pipe 30 Coil End 31 Discharge Pipe

Claims (1)

[Claims] 1. A swirling fixed scroll wrap formed on one surface of an end plate that forms a part of a fixed scroll, and a swing scroll wrap on a wrap supporting disk that forms a part of the orbiting scroll is swingably rotatable. Engagement, forming a spiral compression space between both scrolls, a discharge port is provided at the center of the fixed scroll wrap or the orbiting scroll wrap, and a suction chamber is provided outside the fixed scroll wrap, The compression space is divided into a plurality of compression chambers that continuously move from the suction side toward the discharge side to compress the fluid, and between the main frame supporting the drive shaft and the orbiting scroll, the orbiting scroll A scroll compression mechanism that engages a rotation blocking member to orbit the orbiting scroll is formed, and the scroll compression mechanism is a closed case. A motor connected to the drive shaft is arranged in the lower part, and a discharge pipe is connected to the closed case, and compressed gas discharged from the discharge port cools the motor, and then the discharge pipe is connected to the closed case. In a configuration in which a gas passage for discharging to the outside is provided, a bearing frame that supports the drive shaft together with the main body frame is disposed above the motor, and a compressed gas is provided in a space between the upper end of the sealed case and the bearing frame. Lubricating oil separated from the above, the central portion of the bearing frame is recessed on the side of the motor in order to collect on the upper portion of the upper bearing of the bearing frame,
A scroll gas compressor in which the recessed bottom portion and the upper bearing are adjacent to each other.