JPS618487A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To make the alignment of a bearing in an enclosed scroll compressor ever so easy as well as to simplify its manufacturing and assembling work, by setting up a main bearing between the upper end of a motor and the scroll compressor and also setting up an auxiliary bearing, capable of positional fine adjustment, at the lower end of the motor. CONSTITUTION:At the upper part of an enclosed scroll compressor, there is provided with a compression mechanism 15, and a motor 16 is installed in the lower part. A frame, supporting the compression mechanism, is installed in position between the compression mechanism 15 and the motor 16, and a main bearing 51 is installed in this frame. On the other hand, an auxiliary bearing body 75 is attached to the lower end of the motor via a bearing support member 74. A bolt insertion hole being larger in diameter than that of a bolt 82 is bored in a flange part 81 of the auxiliary bearing body whereby the position of the auxiliary bearing body is constituted so as to make it minutely adjustable.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to an improvement of a scroll-type compression device in which a scroll-type compression mechanism is housed in a closed case.

[Technical Background of the Invention and Problems Therewith] A scroll type compression device has been known as a low-pressure compression device. This compression device has a compression mechanism constructed by combining a pair of scroll blades in the axial direction, and has advantages such as small size, high efficiency, and low vibration.

By the way, such a scroll-type compression device generally has a frame fixed to a position slightly above the closed case in a form that vertically partitions the inside of the closed case, and a scroll-type compression mechanism is installed above the frame. A motor for providing driving power to the scroll-type compression mechanism is disposed below the frame, and lubricating oil is stored in the bottom of the sealed case. A scroll-type compression mechanism usually consists of a fixed element and a movable element arranged below the fixed element. A bearing hole is provided in the frame so as to pass through the frame in the vertical direction, and the aforementioned motor rotating shaft is rotatably supported by the bearing hole.

Further, an eccentric coupling mechanism and an Oldham mechanism are provided between the upper end of the rotating shaft and the movable element, and the eccentric coupling mechanism and Oldham mechanism cause the movable element to perform a rotational movement without rotation.

However, the conventional scroll type compression device configured as described above has the following problems. That is, the rotating shaft of the motor is passed through a bearing hole provided in the frame, and the bearing hole supports the radial load and thrust load applied to the rotating shaft. In this way, when the means for supporting the rotating shaft is a so-called cantilever support structure, a bending moment is likely to act on the rotating shaft, and this force causes stress to concentrate on the bearing surface, which causes seizure and
There was a strong possibility that this would occur. Such a phenomenon occurs particularly during high-speed operation, and even a small imbalance acts on the bearing surface as a large force during high-speed operation. Therefore, a structure is usually adopted in which the length of the bearing is increased to receive the above-mentioned force over as large an area as possible. In order to realize this method, generally, the overall length in the axial direction is increased, or a hollow part is provided in a part of the motor, and a part of the bearing is inserted into this hollow part. Although a structure in which the length in the axial direction is suppressed has been adopted, the efficiency of the motor is low in such a structure, and therefore there is a problem in that high-speed rotation cannot be achieved.

Therefore, in order to eliminate this problem, a so-called sub-bearing that supports the lower end of the rotating shaft is placed in the lower part of the sealed case, and the two bearings, this sub-bearing and the bearing hole provided in the frame, are installed. However, with this configuration, it is necessary to align both bearings with high precision, and the problem is how to facilitate this alignment.

[Object of the Invention] The present invention has been made in view of the above circumstances, and its object is to provide a frame that divides the inside of the sealed case into two halves, and to connect one end of the rotating shaft of the drive motor. The supporting main bearing and the sub-bearing supporting the other end of the rotating shaft can be easily and precisely aligned, thereby realizing high-speed rotation and facilitating manufacturing and assembly. An object of the present invention is to provide a scroll-type compression device that can be used in a variety of ways.

[Summary of the Invention] The present invention provides fixed elements each having a shape that forms a compression chamber between them by joining them in the axial direction, and each having scroll blades that engage with each other within the compression chamber. A scroll type compression mechanism consisting of a movable element is disposed in a closed case containing lubricating oil at the bottom, and the movable element is caused to undergo a rotational movement without rotation by the power of a motor provided in the closed case. In the scroll type compression device, the scroll type compression device compresses gas by supporting a portion of a rotating shaft that transmits the power of the motor to the scroll type compression mechanism, and is located between the rotor of the motor and the scroll type compression mechanism. a main bearing that supports the rotor, and a sub-bearing that supports an end of the rotating shaft located on the opposite side of the scroll-type compression mechanism, and the sub-bearing is provided on the inner surface of the case. It is characterized by comprising a fixed bearing support member and a sub-bearing main body that is finely adjustable and fixed to the bearing support member and supports the end portion of the rotating shaft.

[Effects of the Invention] With the above configuration, since the sub-bearing is composed of two elements: the bearing support member and the sub-bearing body fixed to the support member in a finely adjustable manner, when assembling the sub-bearing, the bearing support member is first After fixing the material to the sealed case, if the sub-bearing body is fixed to the bearing supporting material while adjusting the position, the main bearing and the sub-bearing main body can be easily aligned with high precision. Therefore, by supporting the rotating shaft of the motor with two bearings, not only can high speed rotation be realized, but also the secondary bearing Not only can manufacturing be facilitated, but also assembly can be facilitated.

[Embodiments of the invention] Embodiments of the present invention will be described below with reference to the drawings.

In FIG. 1, reference numeral 11 indicates a vertically long sealed case, and this sealed case 11 is a cylindrical intermediate case 1.
2, and closing cases 13a and 13b welded to close both ends of the intermediate case 12. A frame 14 is fixed at an upper position inside the sealed case 11 in a form that partitions the inside of the sealed case 11 in the vertical direction. A scroll type compression mechanism 15 is disposed above the frame 14, a motor 16 for providing driving power to the scroll type compression mechanism 15 is disposed below the frame 14, and the bottom of the sealed case 11 is lubricated. Oil 17 is contained.

The scroll-type compression mechanism 15 is composed of a fixed element 21 and a movable element 22 disposed below the fixed element 21, as is well known.

The fixing element 21 includes a disk-shaped mirror plate 23, an annular wall 24 protruding from the peripheral edge of one surface of the mirror plate 23, and a portion surrounded by the annular wall 24 having a height approximately equal to that of the annular wall 24. It is composed of a scroll blade 25 projecting from the side, and a discharge port 26 provided approximately at the center of the end plate 23. The inner edge of the annular wall 24 is formed into a notched surface 27, such as a curved surface with an appropriate curvature or a tapered surface as shown in FIGS. 2(a) and 2(b). The fixing element 21 configured as described above includes an annular wall 24 and a scroll blade 2.
The peripheral edge of the annular wall 24 is airtightly fixed to the peripheral edge of the upper surface of the frame 14 with bolts 28, with the protruding direction of the annular wall 24 facing downward. Note that a cap 29 is applied to the upper surface of the fixing element 21 during fixation, and this cap 29 is also fixed integrally with the bolt 28. The two caps are sized to form a gap 30 of a predetermined thickness between them and the upper surface of the end plate 23, and a hole 31 is formed in a part of the wall forming this gap 30. Further, a hole 32 for guiding lubricating oil, which will be described later, is formed in a part of the side wall. On the other hand, the movable element 22 includes a mirror plate 33 having an outer diameter slightly larger than the inner diameter of the annular wall 24, and a scroll 134 protruding from one surface of the mirror plate 33 at a height approximately equal to the island of the scroll blade 25. , and a cylindrical portion 35 protruding from the other central portion of the end plate 33.

The peripheral edge of the mirror plate 33 on the side from which the scroll blades 34 protrude is formed into a notched surface 36 such as a tapered surface, as shown in FIGS. 3(a) and 3(b). and,
The movable element 22 configured as described above is arranged such that the scroll blade 34 and the scroll! 25, and the peripheral portion of the mirror plate 33, the end face of the annular wall 24, the end face of the scroll blade 34, the mirror plate 23, the end face of the scroll blade 25, and the mirror plate 3.
3 are mounted so as to be in sliding contact with each other, and this mounted state is maintained by an Oldham mechanism 40 provided between the end plate 33 and the frame 14.

The Oldham TA structure 40 includes key grooves 41a and 41b provided at two locations on the same line drawn through the center of the end plate 33 at the lower peripheral edge of the end plate 33, and the key groove 41a,
41b, and on a line perpendicular to the arrangement direction of frame 14.
A key groove 42a provided on the top surface of the key as shown in FIG.
42b and the keyway 4 on one side as shown in FIG.
The ring 45 has keys 43a and 43b that fit into the key grooves 18 and 41b, and keys 44a and 44b that fit into the key grooves 42a and 42b on the other side. On both sides of the ring 45, for example, mesh-like oil grooves 46 are actually formed to reduce sliding resistance, as shown in FIG. Further, on the inner surface of each of the keyways 42a, 42b, 418.
As represented by the keyway 42b in the figure, an enlarged step 47 is formed to reduce the sliding area with the key.

A bearing hole 51 eccentric to the axis of the cylindrical portion 35 of the movable element 22 is provided through the frame 14 in the vertical direction, and the bearing hole 51 is located on the cylindrical portion 35 side of the bearing hole 51. The part is formed to have a large diameter. The frame structure on the larger diameter side is specifically constructed as shown in FIG. That is, the outermost part has an outer diameter that is approximately equal to the inner diameter of the sealed case 11, and the inner diameter is the same as that of the annular wall 2.
An annular wall 52 is formed which is larger in inner diameter than the inner diameter of the annular wall 24 and to which the annular wall 24 is tightened and fixed with a bolt 28,
The annular receiver that receives the ring 45 on the inside is formed with a surface 55 lowered one step, and the annular receiver that is further lowered one step on the inside and receives the thrust force reduction mechanism 59 described later is formed with the surface 5.
6 is formed. The surface of the banake is divided into a plurality of parts in the circumferential direction by grooves 57 provided radially, and at least one of the grooves 57 communicates with a hole 58 provided in the wall of the frame 14 that directly communicates the inside and outside. ing. Note that the key grooves 42a and 42b are formed on a receiving surface 55.

Specifically, the thrust force reduction mechanism 59 is shown in FIG.
As shown in a), (b), and (c), the annular receiver includes an annular body 60 fitted and supported by the surface 56, an annular groove 61 carved on the upper surface of this annular body 60, and an annular groove formed on the upper surface. Annular grooves 62.63 shallower and narrower than the annular groove 61 formed on the inside and outside of the annular groove 61, respectively, and these annular grooves 62.63.
Each part is attached to the inside so that it protrudes outward,
For example, it is composed of seal rings 64° and 65° made of tetrafluoroethylene. A tapered surface 66 is formed at the lower end of the outer peripheral surface of the seal ring 64, as shown in FIG. ing. Further, bottomed holes 67 are formed at four positions in the circumferential direction of the annular groove 61 to have the same depth as the annular groove 61 and communicate the annular groove 61 with the annular grooves 62 and 63. The interior of the end plate 33 is surrounded by an annular body 60, seal rings 64, 65, and the lower surface of the end plate 33 when the thrust force reducing device 159 is in the 8@ state as shown in FIG. Hole 6 that always communicates the space between the medium pressure ports s and s' of the compression chamber P
8.69 is formed.

A rotating shaft 70 of the motor 16 is rotatably supported in the bearing hole 51 of the frame 14 .

The rotating shaft 70 has a large diameter portion 71 formed in a portion located in the large diameter portion of the bearing hole 51, and a small shaft 72 that fits into the aforementioned cylindrical portion 35 is protruded from this large diameter portion 71. There is. The rotating shaft 70 has a length such that its lower end penetrates into the oil 17, and the lower end is supported by a sub-bearing 73 fixed to the inner surface of the sealed case 11.

The sub-bearing 73 is broadly divided into a bearing support member 74 and a sub-bearing main body 75 fixed to the bearing support member 74 so as to be finely adjustable. The bearing support member 74 is formed, for example, by press working a disc-shaped member or is formed by casting, and the outer diameter of the bearing support member 74 is the same as the inner diameter of the intermediate case 12 of the sealed case 11 at its peripheral edge. approximately equal,
A peripheral wall 76 having a height greater than the thickness of the member is formed, a relatively large diameter hole 77 is formed in the center, and a peripheral wall 76 is formed between the hole 77 and the peripheral wall 76. A plurality of holes 78 are formed in the direction.

The bearing support member 74 formed as described above is fitted into the lower end of the intermediate case 12 at a position where it is immersed in the lubricating oil 17 with the projecting direction of the projecting peripheral wall 76 facing upward, and in this state, the cylindrical portion 76 is fixed to the intermediate case 12 by spot welding.

On the other hand, the secondary bearing body 75 includes a cylindrical portion 79 that supports the radial load at the lower end of the rotating shaft 70, and a cylindrical portion 79 that protrudes inward from the lower end of the cylindrical portion 79 to support the thrust load applied to the rotating ring 70. It is composed of an annular part 80 that supports the parts, and a flange part 81 that projects from the outer periphery of this annular part 80. and,
The sub-bearing main body 75 configured as described above has seven cylindrical parts connected to the rotating shaft 70 through a hole 77 provided in the bearing support member 74.
In this state, the flange 81 is fitted onto the lower end of the bolt 82.
The tightening is fixed with respect to the bearing support member 74. The bolt insertion hole provided in the collar 81 for mounting the bolt 82 is formed to be slightly wider than the outer diameter of the bolt 82, so that the mounting position of the sub-bearing body 75 can be finely adjusted. It has become.

Inside the rotating shaft 70, there is a hole 9 through which the lubricating oil 17 is pumped up to the bearing surface and the fitting part between the small shaft 72 and the cylindrical part 35 by a centrifugal pump action.
0 is formed. The shape of the entrance portion of this hole 90, that is, the portion located at the lower end of the rotating shaft 70, includes a portion 91 extending upward from the center of the lower end surface of the rotating shaft 70, and a portion 91 extending radially from the cylindrical portion. It is a combination of a portion 92 extending to the inner surface of the rotating shaft 79 and a portion 93 extending vertically at the peripheral edge position within the rotating shaft 70 so as to intersect this portion 92 at right angles.

The motor 16 has a rotor 100 inside and a stator 10 inside.
1 is placed on the outside, and a stator 101 is fixed to the inner surface of an intermediate case 12.

On the other hand, a ratchet type reversal prevention mechanism 103 is provided between the balance weight 102 protruding from the upper end of the rotor 100 of the motor 16 and the frame 14, and this reversal prevention mechanism 103 has a specific The system is constructed as shown in FIG. That is, balance weight 1
02 is provided with a bottomed hole 105 facing in the direction of the axis center line, and a stopper rod 106 is provided in this bottomed hole 105.
a spring 1 that slidably houses the rod 106 and applies a force between the rod 106 and the inner surface of the bottom wall of the bottomed hole 105 in a direction that causes the rod 106 to protrude from the bottomed hole 105;
07, and a claw-shaped notch 108 is provided on the outer surface of the frame 14, on which the tip of the rod 106 roughly slides.

Roughly speaking, a portion of the side wall of the intermediate case 12 of the sealed case 11 located between the scroll type compression mechanism 15 and the motor 16 is connected to the space 110 between the scroll type compression mechanism 15 and the motor 16. The suction pipe 11 is connected to the
1 is connected to the wall of the closed case 13a, and a discharge pipe 113 is connected to the wall of the closed case 13a so as to communicate with a space 112 formed between this wall and the fixed length l#21.

In addition, 114 in FIG. 1 is an annular wall 24 for returning the lubricating oil pushed out into the space 112 downward from the frame 14.
115 indicates a balance weight, 116 indicates a connection mechanism for power supply to the motor 16, and 117 indicates a hole through which lubricating oil passes.

Next, the operation of the compression device configured as described above will be explained.

First, when power is supplied to the motor 16, the rotating shaft 70 starts rotating. This rotation is smoothly maintained by both the bearing hole 51 and the sub-bearing body 75.

The rotational force of the rotating shaft 70 is then transmitted to the movable element 22. At this time, when the motor 16 starts rotating, the rod 106 of the reversal prevention mechanism 103 comes into sliding contact with the outer circumferential surface of the frame 14 at the initial stage, but when the number of rotations increases beyond a certain speed, the spring 107 is rotated by centrifugal force. Retracts against the force and maintains a completely non-contact state. Furthermore, the cylindrical portion 35 of the movable element 22 is fitted with a small shaft 72 provided eccentrically with respect to the rotating shaft 70, and since the cylindrical portion 35 is also supported by the Oldham mechanism 40, the movable element 22 is supported by the Oldham mechanism 40. At the same time, the scroll blades 34 provided on the movable element 22 also perform a whirling movement. Along with this whirling movement, there is a gap between the scroll blades 25 and the scroll blades 34. The volume of the formed compression chamber P decreases periodically, and the compressed gas is thereby discharged to the discharge port 2.
It is discharged from 6. The discharged high pressure gas is stored in the cap 29.
It is sent out from the discharge pipe 113 through the gap 30 formed by the hole 31 provided in the cap 29 and the space 112. On the other hand, when the movable element 22 rotates as described above, the notch surface 3 is formed between the upper surface peripheral edge of the end plate 33 of the movable element 22 and the inner edge of the annular mold 24 of the fixed element 21.
6.27 is formed, so that the peripheral edge of the compression chamber P is formed on the frame 14.
It is always in communication with the space above. The above space is provided through holes 58 through grooves 57 etc. provided radially in the frame 14.
Also, since this hole 58 communicates with the suction pipe 111 via the space 110, the low-pressure gas eventually passes through the suction pipe 111, the space 110, the hole 58, and the space on the surface 55. The compressed air is sucked into the low-pressure boat in the compression chamber P, where it functions as a compression device. In addition,
In this case, even if a liquid such as a refrigerant is mixed in the low-pressure gas that has flowed in through the suction pipe 111, this liquid will be mixed into the space 11.
0, it falls downward and attempts to migrate to the bottom where the lubricating oil 17 is stored. Since the motor 16 generates heat by itself, the fallen liquid is gasified by the heat, mixes with the flow of the already gasified liquid, and flows into the compression chamber P.
move inward.

Therefore, the space 110 has exactly the same function as a gas-liquid separator.

On the other hand, when the motor 16 rotates as described above, the lubricating oil 1
7 is pumped upward into the hole 90 by the centrifugal pumping action associated with the shape of the hole 90. This pumped up lubricating oil lubricates the inner circumferential surface of the bearing hole 51, then lubricates the fitting part between the small shaft 72 and the cylindrical part 35, and then
The part where the Oldham mechanism 40 is installed is lubricated through the hole 58, and then part of it flows down from the hole 58, and the rest enters the compression chamber P and lubricates the sliding part in the compression chamber P. Lubricate. The lubricating oil that has entered the compression chamber P is finally discharged from the discharge 026, and then flows downward through the hole 32 and hole 114 provided in the cap 29. Therefore, high pressure gas containing no lubricating oil is discharged from the discharge pipe 113.

Further, as described above, when the movable element 22 performs a rotational motion and a compression operation is performed, the pressure inside the compression chamber P becomes high, so the movable element 22 receives a downward thrust force, and this force is transferred to the Oldham mechanism. 40. The support of the frame 14 touches the surface 55, etc., and there is a possibility that a seizure phenomenon may occur in these elements. However, in the case of this embodiment, the thrust force reduction mechanism 5
No. 9 prevents the occurrence of the burn-in phenomenon as follows.

That is, the annular space surrounded by the annular body 60° seal ring 64, 65 of the thrust force reduction mechanism 59 and the end plate 33 is always connected to the so-called intermediate pressure ports s, s' of the compression chamber P via the holes 68, 69. is familiar with Therefore, the end plate 33 receives an upward force due to the gas pressure in the annular space, and the presence of this force reduces the downward thrust force that the end plate 33 receives. This reduction prevents the occurrence of the burn-in phenomenon. Note that the movable element 22
The downward thrust force applied to the compressed space pulsates as the position of the compressed space changes. For this reason, the thrust force reduction mechanism 5
However, in this embodiment, as shown in FIG. 7, the annular groove 61 and the annular groove 62, 63 in which the seal ring 64, 65 is installed are connected. Since the bottomed holes 67 are provided, the seal rings 64 and 65 always receive a force as shown by the solid arrow in FIG. act. Therefore, this pressing prevents high pressure gas from leaking.

Furthermore, when the motor 16 is stopped, there is a possibility that the movable element 22 will rotate backwards due to the pressure difference between the empty WJ 112 and the space 110, and the high pressure gas will flow into the low pressure side. However, in the case of this embodiment, since a ratchet-type reversal prevention mechanism 103 is provided, the rod 106 of this mechanism 103 engages with the pawl 108 at the same time as it stops, and as a result, the occurrence of reverse rotation is reliably prevented. High pressure gas leakage is prevented.

In this way, the upper end of the rotating shaft 70 is supported by the bearing hole 51 provided in the frame 14, and the lower end is supported by the auxiliary bearing 73. Therefore, the support of the rotating shaft 70 can be stabilized, and high-speed rotation can be realized. In particular, the sub-bearing 73 is composed of a bearing support 74 fixed to the inner surface of the sealed case 11, and a sub-bearing main body 75 fixed to the bearing support 74 in a finely adjustable manner. Therefore, during assembly, the bearing hole 51 serving as the main bearing and the sub-bearing body 75 can be easily and reliably aligned by only finely adjusting the position of the sub-bearing body 75. Furthermore, since the secondary bearing 73 is formed into a two-piece structure consisting of the bearing support member 74 and the secondary bearing body 75, the secondary bearing body 75 is the only part that requires relatively high precision machining. Unlike a one-piece structure, manufacturing can be facilitated, and as a result, the above-mentioned effects can be obtained.

Furthermore, as shown in the embodiment, if the secondary bearing main body 75 is configured to support part of the thrust load, the support of the thrust load at the shoulder of the bearing hole 51 can be reduced, so that even higher speed rotation can be achieved. It is possible to aim for That is, although the portion of the bearing hole 51 is lubricated with lubricating oil supplied through the hole 90, it is structurally difficult to supply sufficient oil to this portion.

On the other hand, so that the secondary bearing body 75 is immersed in the lubricating oil 17,
In other words, it is easy to provide sufficient lubrication. Therefore, if part or most of the thrust load is shared by the auxiliary bearing body 75 which is sufficiently lubricated, the load on the bearing hole 51 side can be reduced, so that higher speed rotation can be realized. Further, as shown in the embodiment, if the sub-bearing main body 75 is fixed to the bearing support member 74 so that the cylindrical portion 79 of the sub-bearing main body 75 projects upward from the bearing support member 74, the rotating shaft The length of 70 can be minimized, and as a result, the lift distance of the lubricating oil Ω can be shortened, so a large amount of lubricating oil can be pumped up and refilled, which is advantageous for high-speed rotation. Become. Furthermore, if the projecting peripheral wall 76 is provided at the peripheral edge of the bearing support member 74 as in the embodiment, this projecting peripheral wall 7
6 can be used to achieve welding or press-fitting to the sealed case, which is extremely convenient.

Note that the present invention is not limited to the embodiments described above. That is, in the embodiment, one end of the portion 92 of the hole 90 for pumping up lubricating oil is opened on the circumferential surface of the rotating shaft 70, and the other end of the portion 93 is opened on the lower end surface of the rotating shaft 70. The section may be closed. When closed in this way, a groove 131 for guiding lubricating oil is provided on the inner surface of the cylindrical portion 79 of the sub-bearing body 75, as shown in FIG. A guide groove may also be provided. Further, in the embodiment, the scroll type compression mechanism is placed above and the motor is placed below, but the present invention is not limited to this. Of course, it can also be applied to those placed in the same direction or those installed with the axis line horizontal.

[Brief explanation of drawings]

FIG. 1 is a longitudinal cross-sectional view of a scroll type compression device according to an embodiment of the present invention, FIG. 2 (a) is a bottom view of a fixing element in the same device, and FIG. Figure 3 (a) is a sectional view under installation conditions when cut along the line and viewed in the direction of the arrow.
> is a top view of the movable element in the same device, and (b) is (
Fig. 4 is a partially cutaway exploded perspective view showing only the upper part of the frame in the same device; Fig. 5 is a plan view of the main parts of the Oldham mechanism in the same device; Figure 6 is a diagram for explaining the shape of the keyway of the Oldham mechanism, Figure 7 (a) is a top view of the thrust force reduction mechanism incorporated in the same device, and Figure 7 (b) is the C in (a).
- A view taken along the line C, FIG. FIG. 3 is a perspective view showing a modified example of the sub-bearing main body with part 9 cut away. 11... Sealed case, 14... Frame, 15...
・Scroll type compression mechanism, 16...Mori, 17...
- Lubricating oil, 21...fixed element, 22...movable element,
25, 34...Scroll blade, 2G...Discharge port, 4
0... Oldham mechanism, 51... Bearing hole as main bearing, 70... Rotating shaft, 73... Sub bearing, 74...
Bearing support material, 75... Sub-bearing body, 90... Hole for centrifugal pump, 100... Rotor, 101... Stator, 103... Reversal prevention mechanism, 110.112... Space, 111...Suction pipe, 1-13...Discharge pipe. Applicant's agent Patent attorney Takehiko Suzue Figure 1 17 /j Figure 2 (a) (a) Figure 3 Figure 4 Figure 5 43b Figure 6 Figure 7

Claims (6)

[Claims] (1) A scroll consisting of a fixed element and a movable element, each of which is joined in the axial direction to form a compression chamber between them, and each of which has scroll blades that engage with each other within the compression chamber. The mold compression mechanism is placed in a sealed case containing lubricating oil at the bottom, and the movable element is rotated without rotation by the power of a motor installed in the sealed case, thereby compressing the gas. In the scroll type compression device, a main bearing supports a portion of a rotating shaft that transmits the power of the motor to the scroll type compression mechanism, and is located between the rotor of the motor and the scroll type compression mechanism; a bearing support member comprising: a sub-bearing that supports an end of a rotating shaft located on the opposite side of the scroll-type compression mechanism with the rotor as a boundary; the sub-bearing is fixed to an inner surface of the sealed case; and a sub-bearing body that is finely adjustable fixed to the bearing support member and supports the end portion of the rotating shaft. (2) The scroll type compression device according to claim 1, wherein the sub-bearing main body has a radial bearing surface and a thrust bearing surface. (3) The scroll type compression device according to claim 1, wherein the sub-bearing main body has a lubricating oil guide groove formed in the bearing surface. (4) The first aspect of the present invention is characterized in that the sub-bearing body is disposed so as to be submerged in the lubricating oil.
Scroll-type compression device as described in Section 1. (5) The scroll type compression device according to claim 1, wherein the bearing support member has a cylindrical projecting peripheral wall in a portion inscribed in the sealed case. (6) The scroll type compression device according to claim 5, wherein the bearing support member has a portion of the projecting peripheral wall fixed to the sealed case by welding or press fitting.