JP2615527B2 - Scroll gas compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

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

[0002]

2. Description of the Related Art In a scroll compressor, a suction chamber is provided at an outer periphery of a spiral compression chamber in which a suction chamber is symmetrically arranged, and a discharge port forms a spiral compression chamber together with a revolving scroll.
It is provided at the center of the fixed scroll, and the flow of compressed fluid is unilateral, and the compression load fluctuation is extremely smaller than that of reciprocating compressors and rotary compressors. It is generally known to have.

Further, in a spiral compression chamber formed by both members of a fixed scroll and an orbiting scroll, a compressive pressure when a fluid is compressed generates a force for separating the two members in an axial direction, thereby causing a compression chamber. Sealing is incomplete, the leakage of the compressed fluid increases, and the compression efficiency is reduced. Therefore, the compressed fluid pressure is urged to the rear side of the orbiting scroll on the side opposite to the compression chamber to apply an axial pressing force, and the two members are separated from each other. 13 and 14 are examples.

FIG. 1 shows that the outer periphery of a wrap support disk 1001a of a revolving scroll 1001 connected to a revolving shaft 1007a at the end of a driving shaft 1007 is fixed.
The second end plate 1002a and the main body frame 1008 are supported by a small gap, and a fluid in the middle of compression (intermediate pressure between the discharge pressure and the suction pressure) and the like are introduced into the back of the orbiting scroll 1001 on the side opposite to the compression chamber, and When the compression load and the inertia of the rotating member change, such as when the compressor starts, stops, or operates at a high speed, the orbiting scroll 1001 rotates the drive shaft 101.
In order to reduce the inclination with respect to the main shaft of 07, to keep the compression chamber tight by maintaining a small gap in the compression chamber, a device for increasing the compression efficiency is devised.

The orbiting scroll 1001 is driven by the drive shaft 1
007, and the compression load and the sliding resistance between the lap support disk 1001a of the orbiting scroll 1001 and the end plate 1002a of the fixed scroll 1002 act on the orbiting shaft 1007a at the tip of the drive shaft 1007. To give a bending moment to the drive shaft 1007. In order to reduce the possibility that the bearing supporting the drive shaft 1007 causes a one-side contact phenomenon and damage the bearing due to the bending moment, the interval between the bearings supporting the drive shaft 1007 tends to be long (Japanese Patent Laid-Open No. 55-55). No. 142902).

Further, for example, a more improved arrangement against the bearing piece contact phenomenon is disclosed in Japanese Utility Model Laid-Open Publication No. 59-167.
No. 983 and JP-A-59-60092.

That is, the former accommodates a motor in an upper part in a sealed case, a scroll compression part in a lower part, an oil reservoir for lubricating a bearing in a bottom part, and a bearing for supporting a drive shaft connected to the motor. Are arranged on both sides of the motor, and have a simple configuration that depends only on adhesion of lubricating oil in an atomized state in which oil supplied to each bearing portion and sliding portion supporting the drive shaft is mixed with gas.

[0008] As shown in FIG. 15, the latter has a positive displacement pump device 1932 mounted on a bearing frame 1930 on the side opposite to the compression section.
The positive displacement pump device 1932 supplies the lubricating oil in the oil reservoir 1944 at the bottom of the motor 1909 to the drive shaft 19.
After the oil reservoir 19 is supplied to the bearing chambers for supporting the oil reservoir 19 and the storage chamber 1903 on the anti-compression chamber side of the orbiting scroll 1912.
This is a configuration having an oil supply passage for returning the oil to the oil supply passage 44.

[0009]

However, in the former configuration, the lubrication to each bearing portion supporting the drive shaft and the sliding portion on the compression portion side depends only on the adhesion of the lubricating oil in the atomized state in which the oil is mixed into the gas. Also, in the limited space in the upper part inside the sealed case, the separated lubricating oil is re-engaged in the gas flow, so the lubricating oil separation efficiency is low, and the lubrication efficiency to the bearing unit and the collection efficiency to the oil reservoir are poor. .

As a result, not only is there insufficient lubrication to the sliding surface of the bearing supporting the drive shaft, but also the orbital sliding resistance of the orbiting scroll is increased, so that the bending moment acting on the compression side end of the drive shaft is increased. The bearing load increases, resulting in the same bearing damage results as the bearing contact effect.

In the latter configuration, the lubrication of the bearings supporting the drive shaft 1906 and the back surface of the orbiting scroll 1912 on the side opposite to the compression chamber is sufficient.
12, the orbiting scroll 1912 is fixed at the fixed scroll 1921
, And the turning resistance increases. As a result, similarly to the former, the bending moment acting on the drive shaft 1906 is large, and the bearing load becomes excessive, resulting in the same bearing damage result as the bearing piece contact action.

In order to avoid applying an excessive back pressure to the orbiting scroll, a means for increasing the pressure on a part of the back surface of the orbiting scroll opposite to the compression chamber is disclosed in Japanese Patent Application Laid-Open No. Sho 60-190691 (US Pat. No. 4,522,575). Specification).

In this configuration, as shown in FIGS. 16 and 17, the central portion of the back surface of the orbiting scroll 1424 on the side opposite to the compression chamber is defined by a high-pressure space, and the outer periphery thereof is defined by an annular seal member 1449 so as to be a low-pressure space. In the high-pressure space inside the seal member 1449, lubricating oil at the bottom of the motor is supplied to the drive shaft 141.
The orbiting scroll 1424 is supplied by using a centrifugal pump action via a passage (not shown) provided in the inside 7, and presses the orbiting scroll 1424 against the fixed scroll 1426 with an appropriate force, while slidingly contacts the fixed scroll 1426. 1424
The lubricating oil at the bottom of the motor is supplied to the outer peripheral sliding contact portion through the thin tube 1447 at a differential pressure.

However, in this configuration, the liquid is compressed in the compression chamber, and an excessive thrust load is generated.
When it acts on 442, the lubrication of the thrust bearing portion that supports the orbiting scroll 1442 on the back surface on the side opposite to the compression chamber becomes insufficient, and the sliding portion of the orbiting scroll 1442 is damaged. Further, since the thin tube 1447 is provided as a means for supplying the lubricating oil to the outer peripheral sliding contact portion of the orbiting scroll 1442, there is a problem that the configuration becomes complicated.

Japanese Patent Application Laid-Open No. 61-169686 proposes a configuration in which the rear surface of the orbiting scroll on the side opposite to the compression chamber is divided into an inner side and an outer side by an annular seal member.

However, this annular sealing member is
This is to prevent the leakage of compressed gas and has the function of preventing the lubrication of sliding parts including the thrust bearing, as described above.Especially, there is no lubricating oil flow on the thrust bearing surface and insufficient lubrication There was a problem of inviting.

Accordingly, the present invention provides a simple and stable method for the orbiting scroll sliding portion which can improve the efficiency of oil separation from the discharged gas and the efficiency of recovery into the oil sump, and reduce the phenomenon of the bearing portion supporting the drive shaft contacting the bearing piece. The main purpose is to provide a refueling passage.

[0018]

In order to solve the above problems, a scroll gas compressor according to the present invention comprises an oil separation space (9).
The lubricating oil separated from the compressed gas in 8) is returned to the discharge chamber oil sump (34) arranged below the motor (3) through an oil return hole (32a) provided in the bearing frame (9). The oil return hole (32a) is arranged on the opposite side of the drain hole (32) serving as an introduction passage to the oil separation space (98), and the sealed case (1) connects the motor (3) to the outside of the compressor.
The oil return hole (32a) also serves as a through hole for the connection line (99) between the electric connection terminal (100) and the motor (3) arranged at the end of the discharge pipe (31).

Further, the present invention provides an orbiting scroll (18).
Can form an oil film between the thrust bearing (20) provided on the body frame (5) supporting the drive shaft (4) and the end plate (15b) of the fixed scroll (15). An annular ring (82) having a cut portion (82a) on the inner side of the thrust bearing (20) and between the thrust bearing (20) and the lap support disk (18c), which is arranged with a minute gap. The body frame (5) including the thrust bearing (20) and the lap support disk (18c) are arranged in an annular recessed portion (81) provided on one of the lap support discs (18c) in a loose state, and the inside of the annular ring (82) Space is the main bearing (1
In order to reduce the thrust load acting on the thrust bearing (20), the back pressure chamber (39) of the orbiting scroll (18) is constituted by communicating with 2) and the orbit bearing (14).
Discharge chamber oil sump (34) disposed below motor chamber (6) communicating with discharge port (16) and containing motor (3)
Is supplied to the back pressure chamber (39), and thereafter the lubricating oil of the back pressure chamber (39) is disposed between the end plate (15b) and the main body frame (5) by the wrap supporting disk (18c). In a configuration in which an outer peripheral space (37) disposed outside the wrap support disk (18c) and an oil supply passage for sequentially supplying one of the suction chamber (17) and the compression chamber are provided, the back pressure chamber (3
9) Oil from the outer peripheral space (37) to the outer peripheral space (37) is partially leaked from the seal portion including the cutout portion (82a) of the annular ring (82) to lubricate the thrust bearing (20) while the outer peripheral space is externally provided. (37) and a wrap support disk (1) provided in the wrap support disk (18c).
8c) and a throttle oil supply passage via an oil hole A (38a) having a throttle function from the center to the outer periphery.

[0020]

According to the present invention, the lubricating oil separated from the compressed gas in the oil separation space (98) is less likely to be diffused into the flow of the gas flowing into the oil separation space (98). . Further, since the lubricating oil passes through the oil return hole (32a) while flowing down the surface of the connection line (99) and the like, and is collected in the discharge chamber oil reservoir (34) along the winding of the motor (3), The recovery rate of the lubricating oil separated from the compressed gas is improved.

Further, according to the present invention, the lubricating oil pressure in the back pressure chamber is offset with the compression chamber pressure to reduce the thrust force acting toward the anti-compression chamber side of the orbiting scroll, and the annular ring is provided on the thrust bearing surface. Between the lap support disc and the head plate while receiving two systems of stable lubrication by lubrication oil leaking from the inside and lubrication oil from outside through the oil hole A in the lap support disc. In the state where the contact force of the thrust bearing is reduced, the same amount of lubricating oil as the thrust bearing is supplied. A simple turning motion is realized. Further, the bending moment force acting on the drive shaft is small, and the phenomenon of one-side contact of the bearing portion supporting the drive shaft can be reduced.

[0022]

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

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

The main body frame 5 is made of an aluminum alloy having excellent heat conduction properties mainly for the purpose of weight reduction and heat dissipation of the bearing portion, and an iron liner 8 having excellent weldability is shrink-fitted around its outer peripheral portion. The outer peripheral surface of the liner 8 is inscribed in the entire periphery of the closed case 1 and partially fixed by welding.

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

A fixed scroll 15 made of an 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 the end plate 15b. At the center of the end plate 15b, a discharge port 16 that opens at the beginning of winding of the fixed scroll wrap 15a is also provided to the discharge chamber 2, and a suction chamber 17 is provided at the outer periphery of the fixed scroll wrap 15a. I have.

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

A spacer 21 is provided between a thrust bearing 20 which is restricted by a split pin type parallel pin 19 fixed to the main body frame 5 and can move only in the axial direction, and a head plate 15b of the fixed scroll 15. The axial dimension of the spacer 21 is such that the lap support disc 18c is effectively formed with an oil film between the end plate 15b and the thrust bearing 20 and smoothly comes into sliding contact with the lap support disc 18c without being inclined.
The thickness is set to be approximately 0.015 to 0.020 mm larger than the thickness of 8c.

Thrust bearing 20 of lap support disk 18c
An annular groove (hereinafter, referred to as an annular recessed portion) 81 is provided on the sliding surface with which an annular ring 82 made of a sintered alloy and having elasticity is mounted with a small gap. The axial gap is 0.025 mm or more, which is such that an oil film can be formed. In addition, the annular ring 82 is open in a free state as shown in FIG. 4 with a cutout 82a that is cut inclining with respect to the circumferential direction thereof.
When the annular ring 82 is attached to the annular recessed portion (annular groove) 81, the outer surface of the annular ring 82 is formed by the pressure difference between the inside and the outside of the annular ring 82 and the elastic force of the annular ring 82. It is set so as to have a minute gap in a state of being in close contact with the outer surface of the concave portion (annular groove) 81. The minute gap is such that the annular ring can absorb the thermal expansion allowance, and is set so that the outer surface of the annular ring 82 is always in close contact with the outer surface of the annular concave portion (annular groove) 81. In addition, the width of the annular recessed portion (annular groove) 81 and the width of the annular ring 82 are not the same over the entire circumference. It is configured so that it cannot rotate.

The orbiting bearing space 3 between the bottom of the orbiting bearing 14 of the drive shaft 4 and the end of the orbiting shaft 18b of the orbiting scroll 18
6 and the outer peripheral space 37 of the lap support disc 18c are communicated with each other by an oil hole A38a having a throttle function provided in the turning shaft 18b and the lap support disc 18c.

The thrust bearing 20 is made of a sintered alloy.
As shown in FIG. 6, the center portion is composed of two parallel straight portions,
It is penetrated and formed into a shape composed of two arc-shaped curved portions 23 connected thereto.

The anti-rotation member (hereinafter referred to as Oldham ring) 24 of the orbiting scroll 18 is made of a light specific gravity material such as a light alloy or a reinforced fiber composite resin material suitable for sintering or injection molding, and has an oil-impregnating property. As shown in FIG. 5, the annular plate 24a includes a thin annular plate 24a having two parallel surfaces, and a pair of parallel key portions 24b provided on one surface of the thin annular plate 24a. The linear portion 25 is engaged with the linear portion 22 of the thrust bearing 20 with a small gap, is slidable, and has a side surface of the parallel key portion 24b, as shown in FIG. Reference numeral 24c is orthogonal to the center of the linear portion 25, and the wrap support disk 18c of the orbiting scroll 18 as shown in FIGS.
Are engaged with a pair of key grooves 71 provided at a small gap, and have a slidable shape.

The inner contour of the annular plate 24a has a shape similar to the outer contour. The dent portion 24d provided at the base of the parallel key portion 24b also serves as a passage for lubricating oil. In addition, the dent portion 24 provided in the arc-shaped curved portion is provided.
Reference numeral 0e denotes 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 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 part of the motor chamber 6 and the discharge chamber 2 are connected to a bypass discharge pipe 29 connected through the side wall of the closed case 1.
The opening position of the bypass discharge pipe 29 to the motor chamber 6 is opposed to the side surface of the upper coil end 30 of the stator 3b, and is connected to the upper open end of the bypass discharge pipe 29 and the upper end of the sealed case 1. The discharge pipe 31 communicates with the discharge pipe 31 through a hole 32 provided in the bearing frame 9 and an oil separation space 98 between the upper surface of the sealed case 1 and the bearing frame 9. A shielding member 33 having a number of small holes is disposed between the shielding member 33 and the shielding member 33.

An electric connection terminal 100 is disposed at the center of the upper end of the sealed case 1, and a connection wire 99 between the electric connection terminal 100 and the motor 3 is provided on the opposite side of the hole 32. The bearing frame 9 penetrates through the return hole 32a.

The discharge chamber oil reservoir 34 provided in the lower part of the motor chamber 6 is communicated with the upper part of the motor chamber 6 by a cooling passage 35 cut and provided in a part of the outer periphery of the stator 3b of the motor 3. . The discharge chamber oil reservoir 34 communicates with the annular groove 28 via an oil hole B38b provided in the main body frame 5 and also has a main bearing 12 in the back pressure chamber 39 of the orbiting scroll 18 in which the Oldham ring 24 is disposed. Oil groove A40a which is provided through the sliding portion passage of
Through the swivel bearing space 36.

An oil hole B provided in the body frame 5
Reference numeral 38b also communicates with a 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 winding direction of the spiral oil groove 41 is such that the drive shaft 4 rotates forward. The lower end of the lower bearing 4a is formed halfway in the lower bearing 4a.

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.
A circular suction hole 43 perpendicular to the suction hole 43 is also provided in a direction perpendicular to the side surface of the fixed scroll wrap 15a. The bottom of the suction hole 43 is flat and reaches the side surface of the suction passage 42. .

As shown in FIG. 9, the center of the suction hole 43 is offset from the bottom surface 44 of the suction passage 42, and the opening W45 to the suction passage 42 is smaller than the diameter of the suction hole 43. I have. A suction pipe 47 of an accumulator 46 is connected to the suction hole 43.
Between the bottom surface 44 and the suction pipe end face 48, the inner diameter of the suction pipe 47 and the depth L499L of the suction hole between the suction pipe end face 48 and the bottom face 44 are also large, and the circular shape is larger than the opening dimension W45. A check valve 50 of steel plate is arranged.

The surface of the check valve 50 is coated with Teflon or rubber which has poor oil wetting characteristics and is highly elastic.

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

The coil spring 59 includes a heat insulating cover 53
The check valve 58 is constantly urged. As shown in FIGS. 11 and 12, the opening position of the oil hole C38c in the outer peripheral space 37 is set to a value close to the end of the volume reduction stroke of the third compression chamber 60 communicating with the discharge port 16.
8 is moved (see FIG. 11), the outer peripheral space 37 communicates with the oil hole C38c, and at other times (see FIG. 12), it is provided at a position where it is shut off by the lap support disk 18c. .

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

In FIG. 1 to FIG. 12, when the drive shaft 4 is driven to rotate by the motor 3, the orbiting scroll 18 orbits, and the suction refrigerant gas containing lubricating oil is supplied from the refrigerating cycle connected to the compressor to the accumulator 46. Flows into the suction chamber 17 sequentially through the suction pipe 47, the suction hole 43, and the suction passage 42 connected to the suction chamber 47, and enters the compression chamber through the first compression chambers 61a and 61b formed between the orbiting scroll 18 and the fixed scroll 15. The second that is confined and always becomes a closed space
The liquid is sequentially transferred and compressed to the compression chambers 51a and 51b and the third compression chambers 60a and 60b, and is discharged to the discharge chamber 2 through the discharge port 16 at the center.

The discharged refrigerant gas containing the lubricating oil returns to the motor chamber 6 in the compressor again through the bypass discharge pipe 29 bypassed to the outside of the compressor, and is 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 thereafter, when passing through the hole 32 provided in the bearing frame 9, the flow direction is changed, the collision with the shielding member 33 or a part of the refrigerant gas is carried out. When passing through the shield member 33 and bypassing the shielding member 33, the lubricating oil is effectively separated by the inertial force and the surface adhesion of the lubricating oil. A part of the lubricating oil is collected and stored in a concave portion in the center of the bearing frame 9 and supplied to the oil passage of the upper bearing 10, while the remaining lubricating oil flows down along the connection line 99 while flowing down. Return hole 32a
After flowing into the motor chamber 6 through the motor chamber 6 and passing through the space between the motor winding bundles and the cooling passage 35, the discharge chamber oil reservoir 34 while cooling the motor 3
Will be collected.

The drive shaft 4 which receives a bending moment from the orbiting shaft 18b of the orbiting scroll 18 and tries to tilt in 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 reservoir 34 is supplied to the thrust ball bearing 13 by the viscous pump 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 is When the lubricating oil passes through the minute bearing gap at the end of the portion 4a, the oil film sealing action shuts off the refrigerant gas atmosphere discharged from the motor chamber 6 and the space on the upstream side of the main bearing 12.

The lubricating oil containing the dissolved refrigerant gas in the discharge chamber oil reservoir 34 is reduced to an intermediate pressure between the discharge pressure and the suction pressure when passing through the bearing gap of the main bearing 12, and flows into the back pressure chamber 39. I do. Thereafter, the outer peripheral space 37 is gradually reduced in pressure through the oil groove A40a of the slewing bearing 14, the slewing bearing space 36, and the oil hole A38 having a throttle function in the lap support disk 18c.
Flows into. On the other hand, the lubricating oil from the back pressure chamber 39 leaked from the minute gap at the cutout portion 82 a of the annular ring 82 is reduced in pressure and flows into the outer peripheral space 37 while lubricating the sliding surface of the thrust bearing 20. The lubricating oil passing through the two pressure reducing paths from the back pressure chamber 39 joins in the outer peripheral space 37 to lubricate the thrust bearing 20 and the end plate 15b.

The lap support disk 18c is mounted on the thrust bearing 2
0 and the end plate 15b (0.015 to 0.0
(20 mm). Also,
The lap support disk 18c urged toward the compression chamber by the lubricating oil pressure in the back pressure chamber 39 and the lubricating oil pressure in the outer peripheral space 37
Are offset by the thrust force from the compression chamber side, the contact force with the end plate 15b is reduced, and a smooth turning motion is achieved.

A part of the lubricating oil in the outer peripheral space 37 flows into the suction chamber 17 through the sliding surface between the lap supporting disk 18c and the end plate (15b), and the remaining lubricating oil is intermittently opened. Through the hole C38c, the injection groove 54, and the injection holes 52a, 52b, the second compression chamber 51a,
51b.

The lubricating oil injected into the second compression chambers 51a and 51b merges with the lubricating oil flowing into the compression chamber together with the suctioned refrigerant gas from the refrigeration cycle outside the compressor, and forms a small gap between the adjacent compression chambers with an oil film. To prevent leakage of the compressed refrigerant gas and to be discharged again to the discharge chamber 2 together with the compressed refrigerant gas while lubricating the sliding surfaces between the compression chambers.

Since the discharge chamber oil reservoir 34 communicates with the annular groove 28 and the release gap 27, the thrust bearing 20
Is biased by the back pressure to come into contact with the spacer 21. The wrap 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 gap 5b.

Also, the clearance between the end surface of the fixed scroll wrap 15a and the wrap support disk 18c and the clearance between the end surface of the orbiting scroll wrap 18a and the end plate 15b are kept very small. Reduce.

An annular ring 82 made of an elastic material which makes a revolving motion following the orbiting scroll 18 scrapes the lubricating oil on the sliding surface of the thrust bearing 20 in contact with the lap support disk 18c to form an annular recess. Around the part (annular groove) 81,
Excessive leakage through the gap between the annular recessed portion (annular groove) 81 and the annular ring 82 and the sliding contact surface between the annular ring 82 and the thrust bearing 20 and the minute gap at the cutout portion 82a of the annular ring 82 To block. As a result, the back pressure chamber 39
The lubricating oil pressure is maintained, the back pressure chamber 39 is always filled with the lubricating oil, the effective lubricating oil film is formed on the sliding surfaces of the main bearing 12 and the slewing bearing 14, and the drive shaft in the bearing clearance is formed. 4 is also prevented, and assists the smooth sliding of the drive shaft 4 in the upper bearing 10.

As described above, according to the above-described embodiment, the oil return hole (32a) provided in the bearing frame (9) is removed by the removal hole (3).
The oil return hole (32a) is disposed on the opposite side of 2), and the return passage for lubricating oil separated from the compressed gas in the oil separation space (98) to the discharge chamber oil reservoir (34) and the electrical connection terminal (100) The lubricating oil separated from the compressed gas in the oil separation space (98) is used for the flow of the gas flowing into the oil separation space (98). While the lubricating oil is also trapped on the surface of the connection line (99), and flows down the surface of the connection line (99) together with the lubricating oil separated in other regions to form the oil return hole (32a). Through the discharge chamber oil sump (3) along the winding of the motor (3).
Since it is collected in 4), the recovery rate of the lubricating oil separated from the compressed gas can be improved.

Further, in the configuration in which the scroll compression mechanism is arranged at the lower part and the motor (3) is arranged at the upper part, the central part of the bearing frame (9) and the periphery thereof are recessed on the side of the motor (3), and the electric connection is made. By arranging the terminal (100) at a position opposing the recess, the compressor can be downsized.

Further, by disposing the shielding member (33) between the vent hole (32) and the discharge pipe (31), the gas flowing through the vent hole (32) directly flows into the discharge pipe (31). And prevents a large amount of lubricating oil contained in the gas from flowing out of the compressor, thereby avoiding abrasion of the sliding portion due to insufficient lubricating oil.
In particular, when the liquid refrigerant mixed in the lubricating oil foams and moves together with the lubricating oil toward the bearing frame (9), such as at the beginning of a cold start of the compressor, together with the bearing frame (9), In many cases, the shielding member (33) contributes to preventing a large amount of lubricating oil from flowing out of the compressor.

The outer space (3) extends from the back pressure chamber (39).
7) is supplied to the cut portion (82) of the annular ring (82).
A leakage oil supply passage which partially leaks from the seal portion including a) and flows into the outer peripheral space (37) while lubricating the thrust bearing (20), and is provided in the lap support disk (18c). The wrap support disk (18c) is configured with a throttle oil supply passage passing through an oil hole A (38a) having a throttle function extending from the center to the outer periphery of the wrap support disk (18c). The thrust force acting toward the anti-compression chamber side of the orbiting scroll is offset and the thrust bearing surface is lubricated from the inside by the lubricating oil leaking from the annular ring on the thrust bearing surface, and the oil hole A in the lap support disk is provided. Receiving the same amount of lubricating oil as the thrust bearing, while receiving the two systems of stable lubrication by lubricating oil from outside through the lubricating oil, while also reducing the contact force between the lap support disc and the end plate , Light inside small gap Tilting and sliding frictional resistance of the lap supporting disc to slide load is reduced, a smooth orbiting motion of the orbiting scroll is realized. Further, the bending moment force acting on the drive shaft is small, and the phenomenon of one-side contact of the bearing portion supporting the drive shaft can be reduced.

Further, the cut portion (8) of the annular ring (82)
By making the minute gap 2a) the main passage of the leakage oil supply passage, adjustment and stabilization of the leakage oil supply amount can be achieved.

In order to prevent the outer peripheral surface of the annular ring (82) from being in close contact with the outer surface of the annular recess at the time of thermal expansion, and to make it the main passage of the leakage oil supply passage, the annular passage during assembly is used. By setting the gap at the cut portion (82a) of the ring (82), it is possible to reduce the amount of oil that leaks from the entire annular ring (82).

The space (3) from the back pressure chamber (39) to the outer peripheral space (3)
As the upstream passage of the throttle oil supply passage up to 7), the throttle oil supply passage can be provided long by passing through the inside of the turning shaft (18b), the dispersion of the passage resistance is reduced, and the differential pressure oil supply amount is reduced. Stabilization can be achieved.

The end plate (1) of the fixed scroll (15)
5b) and the thrust bearing (20) of the main body frame (5), the lap support disk (18c) is arranged at an assembly gap of about 0.020 mm, and when the compressor is running, about 0.015 m
The coefficient of thermal expansion and the axial dimension of the main frame (5) and the lap support disk (18c) are set so that a lubricating oil film is formed on both sides of the lap support disk (18c) within the gap of m. Accordingly, the sliding gap of the lap support disk (18c) does not increase, so that the inclination of the orbiting scroll (18) with respect to the drive shaft (4) is restricted, and the bending moment acting on the drive shaft (4) can be reduced.

Further, the lubricating oil in the discharge chamber oil reservoir (34) is led to the main bearing (12) through an oil hole B (38b) provided in the main body frame (5), and passes through the bearing gap of the main bearing (12). Lubricating oil reduced to an intermediate pressure between the discharge pressure and the suction pressure flows into the back pressure chamber (39).
Oil hole A (38a) provided in lap support disk (18c)
The differential pressure oil supply passage for supplying the pressure to the outer peripheral space (37) is provided after the pressure is reduced through the oil supply passage. Can be reduced.

In the above embodiment, the back pressure chamber 39 is set to the intermediate pressure. However, since the oil level of the discharge chamber oil reservoir 34 is higher than the main bearing 12 and the slewing bearing 14, the structure is adopted. Since the lubricating oil in the discharge chamber oil reservoir 34 can be easily led to the back pressure chamber 39 without reducing the pressure, depending on the load conditions of the compressor, the above-mentioned conventional example of Japanese Patent Application Laid-Open No. 60-190691 (US Pat. No. 4,522,575) may be used. As described in the specification, while the area of the back pressure chamber 39 is narrowed, it can be set to be equivalent to the discharge pressure.

In the above-described embodiment, the compressor is arranged vertically. However, in the configuration in which the back pressure chamber 39 is set to the intermediate pressure as in the above embodiment, the differential pressure from the discharge chamber oil reservoir 34 to the back pressure chamber 39 is increased. Since refueling can be performed, a horizontal configuration in which the accumulator 46 side is the bottom of the compressor in the embodiment of FIG. 1 can also be employed. The configuration of the passage of the separated lubricating oil in this case will be apparent from the above description. As a matter of course, by adjusting the passage resistance from the back pressure chamber 39 to the outer peripheral space 37, the back pressure chamber 39 can be set to the discharge pressure.

[0067]

As is apparent from the above embodiment, the invention according to the first aspect is characterized in that a bearing frame provided with an upper bearing for supporting a drive shaft together with a main body frame is disposed on the side opposite to the compression chamber of the motor, and the discharge port is provided. After the compressed gas discharged from the motor cools the motor, it flows into the oil separation space between the bearing frame and the sealed case via the hole provided in the bearing frame, and then the discharge pipe provided at the end of the sealed case. In the configuration provided with a gas passage for discharging from the compressor to the outside, the lubricating oil separated from the compressed gas in the oil separation space is supplied to the discharge chamber oil sump disposed at the lower part of the motor through the oil return hole provided in the bearing frame. To return the oil, return the oil return hole to the opposite side of the hole as the gas inflow passage, and install an electrical connection terminal at the end of the closed case discharge pipe side to connect the motor and the outside of the compressor. The oil return hole is electric According to this configuration, the lubricating oil separated from the compressed gas in the oil separation space flows in one direction and the flow of gas flowing into the oil separation space A motor that is less likely to diffuse, but also catches lubricating oil on the surface of the connection line and, together with the lubricating oil separated elsewhere, passes through the oil return hole while flowing down the surface of the connection line and connects to the connection line Since the oil is collected in the discharge chamber oil sump without being subjected to the diffusion effect due to the gas passage flow through the wire bundle gap of the winding, the recovery rate of the lubricating oil separated from the compressed gas can be improved. As a result, durability can be improved by effectively supplying this lubricating oil to each sliding portion. Further, since the oil separation efficiency in the sealed case is high, the size of the compressor can be reduced.

According to a second aspect of the present invention, in the configuration in which the scroll compression mechanism is arranged at the lower part and the motor is arranged at the upper part,
The central portion of the bearing frame and its periphery are recessed on the motor side, and the electric connection terminals are disposed at positions opposing the recessed portions. According to this configuration, the final gas passage in the closed case is provided. Since the oil separation space is enlarged, the efficiency of oil separation from gas is improved, lubricating oil is easily collected at the center of the recess, and lubrication to the upper bearing can be facilitated. Also, there is an effect that the compressor can be downsized.

According to the third aspect of the present invention, a shielding member is disposed between the hole and the discharge pipe. According to this configuration, the gas that has passed through the hole and directly flows into the discharge pipe is prevented. In addition, it is possible to prevent a large amount of lubricating oil mixed into the discharge gas from flowing out of the compressor, and to avoid abrasion of the sliding portion due to insufficient lubricating oil.

According to a fourth aspect of the present invention, the hole and the discharge pipe are arranged at the upper part, the oil return hole is arranged at the lower part, and the electric connection terminal is arranged at the upper part of the oil return hole to form a horizontal arrangement. According to the above, since the lubricating oil separated in the oil separation space easily flows down, the efficiency of oil recovery in the discharge chamber oil sump is further improved, and the compressor is further downsized by saving the space of the oil separation space. This has the effect that it can be performed.

According to a fifth aspect of the present invention, the orbiting scroll lap support disk is disposed between the thrust bearing provided on the main body frame and the end plate of the fixed scroll with a minute gap capable of forming an oil film. On the inner side, and
An annular ring having a cut portion between the thrust bearing and the lap support disk is loosely arranged in an annular recess provided on one of the main frame including the thrust bearing and the lap support disk, and The inner space of the ring communicates with the main bearing and the orbiting bearing to constitute the back pressure chamber of the orbiting scroll, and in order to reduce the thrust load acting on the thrust bearing, the lower part of the motor chamber that communicates with the discharge port and houses the motor. The lubricating oil in the discharge chamber oil sump disposed in the back pressure chamber is supplied to the back pressure chamber, and then the lubricating oil in the back pressure chamber is supplied to the lap supporting disc to dispose the lap supporting disc between the end plate and the main body frame. In a configuration in which an outer peripheral space disposed outside and an oil supply passage for sequentially supplying one of the suction chamber and the compression chamber are provided, the oil supply from the back pressure chamber to the outer peripheral space includes a cut portion of the annular ring. One from the seal A leakage oil supply passage that leaks and flows into the outer peripheral space while lubricating the thrust bearing, and an oil hole A provided in the lap support disk and having a throttle function from the center to the outer periphery of the lap support disk. According to this configuration, the lubricating oil pressure in the back pressure chamber cancels out the compression chamber pressure and reduces the thrust force acting toward the anti-compression chamber side of the orbiting scroll. At the same time, stable lubrication can be achieved by two systems: lubrication from the inside by the lubricating oil leaking from the annular ring on the thrust bearing surface, and lubrication from the outside by the lubricating oil through the oil hole A in the lap support disk. . In particular, since there is no dust clogging in the oil supply passage leaking from the annular ring having the sliding surface, even if dust clogging occurs in the oil hole A, oil can be supplied to the thrust bearing surface. Conversely, stable oiling can be achieved by forming oiling passages that interpolate with each other, such as making up for the oiling amount leaked from the unstable annular ring with the oiling amount via oil hole A. In addition, since the same amount of lubricating oil as the thrust bearing is supplied with the contact force between the lap support disc and the end plate reduced, the inclination and sliding of the lap support disc that slides within the minute gap with a light load are also achieved. The dynamic frictional resistance is reduced, and a smooth orbiting movement of the orbiting scroll is realized. In addition, the bending moment force acting on the drive shaft is small, and an effect of reducing the one-side contact phenomenon of the bearing portion supporting the drive shaft can be obtained.

According to the sixth aspect of the present invention, the cut portion of the annular ring is a main passage of the leakage oil supply passage. According to this configuration, the amount of oil leakage can be stabilized. In addition, by changing the gap of the cut portion, there is an effect that the amount of leaked lubrication can be adjusted.

According to a seventh aspect of the present invention, the gap at the cut portion is set so that the amount of oil to be leaked from the cut portion of the annular ring is equal to or less than the amount of oil supplied through the oil hole A. For example, it is possible to reduce the amount of unstable leakage oil supply and stabilize the total oil supply amount to the suction chamber and the compression chamber.

According to an eighth aspect of the present invention, the swivel shaft protruding from the lap support disk to the side opposite to the compression chamber is slidably engaged with a swivel bearing provided at the end of the drive shaft on the compression chamber side. In the slewing bearing configuration, as the upstream side passage of the throttle oil supply passage from the back pressure chamber to the outer peripheral space, the inside of the slewing shaft,
According to this configuration, the throttle oil supply passage can be provided long, the variation in the passage resistance can be reduced, and the effect of stabilizing the differential pressure oil supply amount can be achieved.

According to a ninth aspect of the present invention, a lap support disk is disposed between the end plate of the fixed scroll and the thrust bearing of the main body frame at an assembly gap of about 0.020 mm,
In order to form a lubricating oil film on both sides of the lap support disk within a gap of about 0.015 mm during the operation of the compressor, the thermal expansion coefficient and the axial dimension of the main frame and the lap support disk are set. According to this configuration, since the sliding gap of the lap support disk does not increase so much, the inclination of the orbiting scroll with respect to the drive shaft is regulated, and the effect of reducing the bending moment acting on the drive shaft can be obtained.

According to a tenth aspect of the present invention, the lubricating oil in the discharge chamber oil sump is guided to the main bearing through an oil hole B provided in the main body frame, and passes between the discharge pressure and the suction pressure through the bearing gap of the main bearing. A differential pressure oil supply passage is provided in which lubricating oil reduced to pressure flows into the back pressure chamber, and is further reduced in pressure sequentially through an oil hole A provided in the slewing bearing and the lap support disk, and then supplied to the outer peripheral space. According to this configuration, there is an effect that the oil supply passage through which the bearing portion passes is made a single system, the amount of oil supply to the compression chamber can be reduced, and the compression input based on oil compression can be reduced.

[Brief description of the drawings]

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

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

FIG. 3 is a partial sectional view of a seal ring portion and a thrust bearing portion in 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 external view of an assembly of an Oldham mechanism in the compressor.

FIG. 7 is a transverse sectional view taken along line AA in FIG. 1;

FIG. 8 is an explanatory view showing a position of a check valve at a suction pipe connection portion of the compressor.

FIG. 9 is a partial cross-sectional view along the line BB in FIG. 8;

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

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

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

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

FIG. 14 is a partially enlarged view of FIG.

FIG. 15 is a longitudinal sectional view of another conventional scroll compressor.

FIG. 16 is a longitudinal sectional view of still another conventional scroll compressor.

FIG. 17 is a transverse sectional view taken along line 3-3 in FIG. 16;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Sealing case 3 Motor 4 Drive shaft 5 Main frame 9 Bearing frame 10 Upper bearing 15 Fixed scroll 15a Fixed scroll wrap 15b End plate 16 Discharge port 17 Suction chamber 18 Rotating scroll 18a Rotating scroll wrap 18c Lap support disk 24 Rotation preventing member 31 Discharge Pipe 32 Drainage hole 32a Oil return hole 33 Shielding member 34 Discharge chamber oil reservoir 38a Oil hole A 81 Annular recessed portion 82 Annular ring 82a Cutout portion 98 Oil separation space 99 Connection line 100 Electrical connection terminal

Claims (10)

(57) [Claims] An orbiting scroll (1) is provided on a spiral fixed scroll wrap (15a) formed on one surface of an end plate (15b) forming a part of the fixed scroll (15).
Wrap support disk forming part of 8) (18c) on the orbiting scroll wrap (18a) meshing freely oscillating rotation, to form a compression space of the spiral between both scrolls, before
A discharge port (16) is provided at the center of the fixed scroll wrap (15a), and the fixed scroll wrap (15a ) is provided.
A suction chamber (17) is provided outside of (a), and the compression space is divided into a plurality of compression chambers which continuously shift from the suction side to the discharge side, and the drive shaft (4) is arranged to compress the fluid. Frame (5) supporting the orbiting scroll (1)
8), the rotation preventing member (24) of the orbiting scroll (18) is engaged with the orbiting scroll (18).
A motor (3) connected to the drive shaft (4) and the scroll compression mechanism are housed in a closed case (1), and the motor (3) is located on a side opposite to the compression chamber of the motor (3). A bearing frame (9) provided with an upper bearing (10) for supporting the drive shaft (4) together with the body frame (5) is provided, and compressed gas discharged from the discharge port (16) is supplied to the motor (3). ) Is cooled, the oil flows into the oil separation space (98) between the bearing frame (9) and the closed case (1) via a hole (32) provided in the bearing frame (9). Thereafter, in a configuration in which a gas passage is provided for discharging the gas to the outside of the compressor from a discharge pipe (31) provided at the end of the closed case (1), the lubricating oil separated from the compressed gas in the oil separation space (98) is provided. ,
The oil return hole (32a) is drained so as to return to the discharge chamber oil reservoir (34) disposed below the motor (3) via an oil return hole (32a) provided in the bearing frame (9). An electric connection terminal (1) is disposed on the side opposite to the discharge pipe (31) of the sealed case (1) so as to connect the motor (3) to the outside of the compressor.
00), and the oil return hole (32a) is provided with a connection line (9) between the electric connection terminal (100) and the motor (3).
9) A scroll gas compressor that also serves as a through hole. 2. A motor having a scroll compression mechanism provided at a lower portion thereof.
In the configuration in which (3) is arranged at the upper part, the bearing frame
The center of (9) and its periphery are recessed on the side of the motor (3)
And the electrical connection terminal (100) was opposed to the recessed portion.
The scroll gas compressor according to claim 1, which is disposed at a position. 3. Between a hole (32) and a discharge pipe (31).
The shielding member (33) was arranged and passed through the hole (32).
It is configured to prevent the gas from flowing directly into the discharge pipe (31).
The scroll gas compressor according to claim 1. 4. The drain hole (32) and the discharge pipe (31) are located at the top.
The oil return hole (32a) at the bottom, and the electrical connection terminal (10
0) is disposed above the oil return hole (32a) and placed horizontally.
The scroll gas compressor according to claim 1, wherein the scroll gas compressor is formed in a shape. 5. A head plate forming part of a fixed scroll (15).
(15b) Spiral fixed scroll formed on one surface
One of the orbiting scrolls (18) with respect to the wrap (15a)
Orbiting scroll on lap support disk (18c) forming part
The wrap (18a) is rotatably engaged with the wrap (18a).
A spiral compression space is formed between the rolls, and the fixed scroll
Discharge port (16) at the center of the loop wrap (15a)
Provided outside the fixed scroll wrap (15a).
Is provided with a suction chamber (17), and the compression space is discharged from the suction side.
It is divided into a plurality of compression chambers that move continuously toward the outlet side.
The main bearing (1) supporting the drive shaft (4) to compress the fluid
Body frame (5) with 2) in the center and swivel wheel
Between the orbiting scroll (18) and the
The rotation preventing member (24) is engaged, and
The rotating disk (18c) and the drive shaft (4)
4) orbiting the orbiting scroll (18)
Forming a scroll compression mechanism for moving the drive shaft;
A motor (3) connected to (4) and the scroll compressor;
The wrap support circle is stored in the closed case (1).
A thrust provided with a plate (18c) on the body frame (5)
Oil film between the bearing (20) and the end plate (15b)
And the thrust bearing
The inner side of (20) and the thrust bearing (20)
Between the lap support disc (18c) and the lap support disc (18c).
An annular ring (82) having 2a)
The body frame (5) including the (20) and the wrap support
An annular recess provided on one of the holding disks (18c)
(81) Placing said annular ring (82)
The inner space of the main bearing (12) and the slewing bearing (1).
4) to communicate with the back pressure chamber of the orbiting scroll (18).
(39), the thrust bearing (2)
0) to reduce the thrust load acting on the discharge port.
A motor that communicates with the motor (16) and houses the motor (3).
Of the discharge chamber oil sump (34) arranged at the lower part of the heat chamber (6).
Lubricating oil is supplied to the back pressure chamber (39), and thereafter,
The lubricating oil of the pressure chamber (39) is supplied to the end plate (15b) and the main body.
The wrap supporting disk (18c) between the frame and the frame (5)
Is arranged outside the wrap support disk (18c) to arrange the
The outer peripheral space (37) provided, the suction chamber (17) and the
An oil supply passage is provided to sequentially supply one of the compression chambers
In the configuration, the back pressure chamber (39) is connected to the outer peripheral space.
(37) is supplied with oil by turning off the annular ring (82).
Part of the seal including the port (82a)
Said outer periphery while lubricating said thrust bearing (20)
A leakage oil supply passage flowing into the internal space (37);
Said wrap support disk provided in a support disk (18c)
(18c) has a diaphragm function from the center to the outer periphery
And a throttle oil supply passage via oil hole A (38a).
Scroll gas compressor. 6. A cut portion (82a) of an annular ring (82).
6. The disk according to claim 5, wherein the main passage is a leakage oil supply passage.
Roll gas compressor. 7. A cut portion (82a) of an annular ring (82).
Is the amount of oil that leaks through the oil hole A (38a)
The gap of the cutout (82a) is set as follows.
The scroll gas compressor according to claim 5, wherein 8. The wrap support disk (18c) on the side opposite to the compression chamber.
The protruding turning shaft (18b) is connected to the drive shaft (4).
Sliding engagement with a swivel bearing (14) provided at the end on the compression chamber side
In the slewing bearing configuration, the back pressure chamber (39) is
As the upstream passage of the throttle oil supply passage up to interval (37)
6. The scroll according to claim 5, wherein the rotary shaft passes through the turning shaft.
Roll gas compressor. 9. The end plate (15b) of the fixed scroll (15).
Between the thrust bearing (20) of the body frame (5) and
Set the lap support disk (18c) to about 0.020mm
Approximately 0.015mm when the compressor is running
Sliding on both sides of the lap support disk (18c) in the front and rear gaps
In order to form a lubricating oil film on the contact surface, the body Frame (5)
And the coefficient of thermal expansion and axis of the lap support disk (18c)
The scroll gas compression according to claim 5, wherein a direction dimension is set.
Machine. 10. Lubricating oil in the discharge chamber oil sump (34)
Main bearing through an oil hole B (38b) provided in the arm (5)
(12) through the bearing clearance of the main bearing (12).
Lubricating oil reduced to an intermediate pressure between the discharge pressure and the suction pressure
Flow into the back pressure chamber (39), and
4), an oil hole A (3) provided in the lap support disc (18c).
8a), the pressure is sequentially reduced, and then the outer peripheral space (37)
6. The scroll according to claim 5, wherein a differential pressure oil supply passage is provided.
Gas compressor.