JPH02227579A - Fluid machine with scroll - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed Description of the Invention] [Objective of the Invention 1 (Industrial Application Field) This invention aims to rotate a crescent-shaped space formed by combining a main rotor blade and a slave rotor blade with their centers of rotation shifted. The present invention relates to a scroll fluid machine that changes by rotating the device.

(Prior art) A scroll fluid machine includes a main rotor blade that is rotationally driven,
There is a combination of a main rotor and a slave rotor that rotates synchronously.

In such a scroll fluid machine, the rotation centers of the main rotor blade and the slave rotor blade, which are formed by protruding spiral wraps (wings) on the plate surface of the end plate (end plate), are shifted, so that the wraps are staggered. The wraps fit together to form a crescent-shaped compressed space between the wraps.

Then, the main rotor and the slave rotor are connected using an Oldham joint. Also, the main rotor blade and the slave rotor blade are housed in the suction chamber. Furthermore, the main rotor blade is connected to a motor and driven to rotate, and the volume of the crescent-shaped space can be increased from the outer periphery of the blade part by each wrap of the main rotor blade and the slave rotor blade, which rotate at different rotation centers. It is gradually changed toward the center so that the outermost side of the wrap facing the suction chamber is on the suction side and the discharge hole formed on the center side of the wrap is on the discharge side.

By the way, such a scroll fluid machine has a main rotor,
The back side of the slave rotor blade is rotatably supported, but since the clearance of the sliding part faces the suction chamber, there is a problem that leakage occurs due to communication between the suction chamber and the outside air.

Therefore, conventional scroll fluid machines are bearing using a sealed structure. This includes the structure shown in FIG.
There is a structure as shown in the figure.

That is, in FIG. 14, a sliding bearing f for rotatably supporting the main rotor a is provided on the wall e on the main rotor a side of the suction chamber d that houses the main rotor ia and the slave rotor gb together with the Oldham coupling C. , a ball or roller bearing that does not require oil lubrication is provided on the wall g on the side of the slave rotation gb. Further, an oil reservoir J for storing lubricating oil i is provided above the wall e, and the structure is such that oil is supplied to the slide bearing f while sealing the shaft portion t to be bearing.

Further, in FIG. 15, an oil reservoir k is also formed in the suction chamber d, and the end on the slave rotation gb side is supported by a sliding bearing m so as to be immersed in the oil reservoir k.

Note that q is a motor qS that drives the main rotor a, r is a suction port, and S is a discharge port.

(Issue 1m to be solved by the invention) However, the structure in which the bearing is sealed with oil tends to increase the size of the scroll fluid machine. Furthermore, although the oil-sealed structure is good when the maximum differential pressure is small, leaks occur when the maximum differential pressure is large. Specifically, the maximum differential pressure between suction gas and discharge gas is 1 ksr/c-
However, it has not been possible to support anything other than fluid machines such as vacuum pumps, which require small loads and bearing structures.

Moreover, when such a scroll fluid machine constitutes a closed cycle such as a refrigeration cycle, the lubricating oil i in the oil sump j discharged together with the discharged gas circulates through the closed cycle and returns to the suction chamber d. Since the oil tends to accumulate in the suction chamber d, there is a problem that the amount of oil decreases only in the oil sump part i, which may lead to poor lubrication depending on the case. In addition, especially in the latter lubrication structure having the two oil reservoirs j and k, it is necessary to take measures to prevent the two oils from mixing.

In addition, since the oil reservoir j is required, it is quite difficult to cool the motor q with suction gas and discharge gas, or to cool it with a well. It is necessary to provide an external cooling means such as a cooling fan U to cool the motor q in the atmosphere. Therefore, there was a problem in that the cooling structure of the motor q was also complicated.

This invention was made with attention to these circumstances,
The purpose of this is to be able to lubricate the main rotor and slave rotors without lubrication failure or leakage, regardless of the maximum differential pressure between the suction gas and the discharge gas, and to Another object of the present invention is to provide a small scroll fluid machine that can be cooled using lubricating oil as it is.

[Structure of the Invention] (Means for Solving the Problems) In order to achieve the above object, a scroll fluid machine according to claim 1 includes a closed case in which an oil reservoir for storing lubricating oil is formed in the inner bottom. 4y4-A main rotor blade and a slave rotor blade are provided on one side of the sealed case and are combined with each other so that the blade portions are inserted into each other alternately. , a discharge hole provided in the center of the end plate of the main rotor or the slave rotor; an Oldham joint that transmits the rotation of the main rotor to the slave rotor; and the main rotor and the slave rotor. a sliding bearing means rotatably supporting the rear side of the end plate of the rotor; a rotor provided on the other side of the closed case and connected to the main rotary platform i; and a pair of the rotor.

a stator that is supported in a sealed case and constitutes a motor section together with a rotor; a main rotor blade in the sealed case;
a suction chamber provided to surround the periphery of the slave rotor and the Oldham joint; a suction pipe connected to the sealed case and communicating with the suction chamber either directly or through the inside of the sealed case; and a suction pipe connected to the sealed case and connected to the suction chamber. A discharge pipe that corresponds to the pipe and communicates directly with the discharge hole through the inside of the sealed case, and an inlet side provided in the sealed case is connected to the oil reservoir portion and an outlet side is connected to the sliding bearing means. The oil passage includes an oil passage that opens to the surface, and a pump that is provided in the sealed case and that delivers lubricating oil from the oil reservoir from the entrance of the oil passage.

Further, the scroll fluid machine according to the second aspect of the present invention includes a cooler provided in the sealed case for the purpose of suppressing overheating of the gas caused by the rotation of the main rotor blade and the slave rotor blade.

(Operation) In the scroll fluid machine according to the first aspect, when the electric motor section is operated, the main rotor blade and the slave rotor blade in the suction chamber are rotationally driven. As a result, the gas led to the suction chamber directly from the suction pipe (or through the inside of the sealed case) passes through the space formed between the blades, and then passes through the discharge hole through the inside of the sealed case to the discharge pipe ( or directly). This process in a sealed case prevents gas from leaking to the outside air, regardless of the maximum differential pressure between the suction gas and the discharge gas. In other words, the conventional oil reservoir for sealing is not required, and the scroll fluid machine can be made smaller accordingly.

Moreover, the electric motor section is cooled by directly utilizing the discharged gas (or suctioned gas) discharged into the sealed case.
The simple structure also allows cooling of the motor part.

Further, the lubricating oil at the inner bottom of the sealed case is sucked up by a pump, and is supplied to the sliding surfaces of the sliding bearing means supporting the main rotor blade and the slave rotor blade through the oil passage. This means that even when the maximum differential pressure between the suction gas and the discharge gas is large (heavy load), a sufficient amount of oil can be secured, and lubrication failure will not occur. A portion of the lubricating oil discharged from this sliding surface after lubrication of the sliding bearing means is discharged to the rotor and stator of the motor section, thereby cooling the motor section. Thereby, the electric motor section can be effectively cooled together with the discharged gas (or suctioned gas). Moreover, even if the lubricating oil is discharged from the discharge pipe into a closed cycle,
Since the lubricating oil enters the sealed case again and accumulates at the inner bottom of the sealed case, the amount of lubricating oil will not be inadvertently reduced.

According to the scroll fluid machine according to the second aspect, the lubricating oil in the sealed case and further the components in the sealed case are cooled by the cooler. The gas is then cooled through this heat transfer.

This will suppress overheating of the gas, increase efficiency, and improve the performance of scroll fluid machines.

(Example) The present invention will be described below based on a first example shown in FIGS. 1 to 8. FIG. 1 shows, for example, a hermetic compressor to which a double-rotation scroll fluid machine is applied, and 1 is a hermetic case constituted by a vertical case. An oil reservoir 2 for storing lubricating oil 2a is provided at the inner bottom of the sealed case 1.
is formed. Also, on the upper side of the sealed case 1,
A motor section 5 composed of a stator 3 and a rotor 4 is provided. Furthermore, a compressor section 6 is provided on the lower side inside the sealed case 1.

Regarding the compressor section 6, 7 is a main rotor blade, and 8 is a sub rotor blade. The main rotor 7 has a spiral wrap 11 (corresponding to one part) formed by an arc of an involute curve, for example, integrally provided on the plate surface of a disk-shaped mirror plate 10 (corresponding to an end plate). In addition, a hollow shaft portion 12 is integrally provided at the axial center portion of the mirror plate 10 on the side opposite to the wrap 11. Similarly, for the slave rotation W18, a spiral wrap 14 (corresponding to a wing portion) having the same external shape as the wrap 11 is integrally provided on the plate surface of a disc-shaped end plate 13 (corresponding to an end plate), and a wrap It has a structure in which a solid shaft portion 15 is integrally provided at the axial center portion of the end plate 10 opposite to the shaft portion 14. The main rotor blade 7 and the slave rotor blade 8 are arranged so that the rotation center A of the main rotor blade 7 and the rotation center B of the slave rotor blade 8 are shifted by a distance fie as shown in FIG. 14 are combined so that they enter alternately. Specifically, at the position of distance e, the phase of both wraps 11.14 is r18
The two wraps 11 and 14 are combined so that they are offset by 0'J and are in contact with each other. As a result, crescent-shaped sealed spaces 16 to 20 (formed by being surrounded by both wrap portions and both mirror plate portions) are formed between the wraps 11 and 14 as compressed spaces.

The combined main rotor blade 7 and slave rotor blade 8 consist of a concave main fixed frame 21 fixed to the inner surface of the sealed case 1 and a sub fixed frame 22 fixed so as to close the opening of the main fixed frame 21. It is accommodated in a suction chamber 23 formed by. The shaft portion 12 of the main rotor blade 7 is connected to the rotor 3.
The main bearing part 2 is connected to a hollow shaft part 25 connected to
4 (corresponding to sliding bearing means). Further, the shaft portion 15 of the slave rotor blade 8 which is shifted by a distance e is connected to a subsidiary bearing portion 26 formed of a sliding bearing provided on the subsidiary fixed frame 22.
(equivalent to sliding bearing means) is rotatably supported.

These main rotor blades 7 and slave rotor blades 8 are connected by an Oldham joint, and the rotation manually applied to the main rotor blades 7 is transmitted to the slave rotor blades 81;

The structure of this Oldham joint is shown in FIG. To explain the structure of the Oldham joint, 27a and 27b.
is a part of the outer periphery of the wrap 11 of the main rotor blade 7 that is not in sliding contact with the wrap 14 of the slave rotor g8, for example, the part of the wrap 11 that protrudes to the outermost periphery and the wrap 14
This is a wide thick part formed in two places: the part immediately after it is exposed. In this embodiment, both thick portions 27a are used.

Both 27b are formed only on the outer periphery of the protruding side of the wrap 11, but they may of course be formed on the entire outer periphery of the wrap. 1 of the slave rotor blade 8 in the thick wall portion 27a. Facing Kari 13. At the protruding end, a linear keyway 28a (guide path) with two parallel sides forms an angle α, for example, 45″ with respect to a diametrical line X passing through the center of rotation A. It is formed.

Similarly, at the protruding end of the thick interior 27b, a linear keyway 28b (guide path) with two parallel sides is formed at an angle β, for example r, with respect to a diametrical line Y passing through the center of rotation A.
It is formed to form an angle of 45"J. The plate portion of the head plate 13 of the slave rotor blade 8 that comes into sliding contact with these thick-walled portions 27a, 27b (the portion that faces the thick-walled portions 27a, 27b)
, a linear keyway 29a with two parallel sides.

A guide path 29b (guide path) is provided so as to be orthogonal to the key grooves 28a, 28b. Between the overlapping portions of the keyway 28a and the keyway 29a and between the overlapping portions of the key 28b and the keyway 29b, parallel columnar keys 30a and 3 having the same cross-sectional shape as the area of the mold portion are provided.
0b (transmission rod) is slidably inserted. This allows the movement of the key 30a with respect to the orthogonal keyway 28a and the keyway 29a, and the movement of the key 30a with respect to the orthogonal keyway 28b and the keyway 29a.
By using the movement of the key 30b relative to the rotation center 9b, the slave rotary blade 8 can be rotated around a rotation center B that is shifted from the rotation center A.

In other words, in the Oldham joint, the parts of the Oldham joint are the head plate 1
The rotation of the main rotor blade 7 can be transmitted to the slave rotor blade 8 without protruding outside the 0.13 mm.

The suction pipe 32 penetrates the side of the sealed case 1 and is connected to the suction chamber 23, and the discharge pipe 31 is connected to the upper part of the sealed case 1, and the compressed gas is transferred from the suction pipe 32 to the main rotor blade 7. A discharge hole 33 provided in the center of the mirror plate 10. Shaft part 12
The gas can be discharged to the outside from a discharge pipe 31 through the interior of the shaft portion 25, the check valve 34 (for preventing reverse rotation due to expansion of the compressed gas), and the interior of the sealed case 1.

And between this discharge pipe 31 and suction pipe 32,
For example, as shown in FIG. 7, a condenser 9a.

The expansion valve 9b (pressure reducing device 5F) and the evaporator 9C are connected in this order to constitute the refrigeration cycle 9.

On the other hand, the shaft portion 15 of the hammered device 8 is immersed in the lubricating oil 2a.
For example, an internal tooth type tocolloid gear pump 35 is provided. The discharge portion of this trochoid gear pump 35 is located within the peripheral wall of the sub-bearing portion 26, within the sub-fixing frame 22.
It communicates with an oil supply passage 36 (corresponding to an oil passage) formed within the plate portion of the main stationary frame 21, within the peripheral wall of the main stationary frame 21, and within the end wall of the main stationary frame 21. The end of this oil supply path 36 faces the shaft portion of the shaft portion 25 which is supported by the main bearing portion 24 and has a spiral groove 25a on the outer periphery, and mainly carries the lubricating oil 2a sucked up by the trochoid gear pump 35. Bearing part 24
and the shaft portion 25.

Further, the discharge part of the trochoid gear pump 36 is connected to the secondary bearing part 2.
6, a spiral groove 15a (corresponding to the oil passage)
It also faces the shaft portion of the shaft portion 15 which has on its outer periphery. In other words, the lubricating oil 2a sucked up by the trochoid gear pump 35 can also be supplied to the sliding surface between the sub-bearing part 26 and the shaft part 15.

On the other hand, 40 indicates the inner bottom surface of the sealed case 1 and the sub-fixing frame 2.
This is a cooling pipe disposed in a dead annular space (ura reservoir part 2) between the two. The cooling pipe 40 is formed into a coil shape. Further, both ends of the cooling pipe 40 penetrate the side of the sealed case 11 and protrude to the outside to form an inlet portion 40a.
and an outlet section 40b. This entrance part 40a
As shown in FIG. 7, a heat radiation pipe 41 installed outside the sealed case 1 is connected to the outlet portion 40b. (not shown) is enclosed to constitute an oil cooler 42 (corresponding to a cooler). In other words,
By using the evaporation and condensation effects of the enclosed refrigerant, the lubricating oil 2a in the closed case 1, particularly in the pond portion 2, can be cooled. That is, the lubricating oil 2a is used to cool the gas inside the compressor section 6 through each component and section of the compressor section 6.

In addition, 43 is a collision plate for removing the gas contained in the compressed gas discharged from the shaft part 25, and 44 is the main fixed frame 2.
1 and a mirror plate 10.13 provided on the sub-fixing frame 22.
45 is a terminal box.

Next, the operation of the hermetic compressor configured as described above will be explained.

The electric motor section 5 is excited through the terminal box 45.

As a result, the rotor 4 rotates, and the generated rotational force is transmitted to the main rotor blade 7 via the shaft portion 25, and the wrap 11
is rotated around rotation center A. The rotation of the main rotor blade 7 is then transmitted to the slave rotor g8 through the pair of keys 30a and 30b.

That is, the keys 30a, 30b have the keys 30a, 30b.
Power is transmitted by contact between the side surface of b and the keyways 28a and 29a, which rotate with the rotation of the main rotor blade 7. Further, the power input to the keys 30a, 30b is transmitted to the side surfaces of the keys 30a, 30b and the keyway 28a at the tip.

It is transmitted to the hammered device 8 by contact with the parallel surfaces of the keyways 28b and 29b in the direction orthogonal to the keyway 29a.

Here, since the keys 30a and 30b are slidable in two orthogonal directions, the rotation center A of the main rotor blade 7 and the hammered device 8 is
, B (distance e) is allowed by sliding according to the amount of deviation. In other words, the keys 30a and 30b are shifted by the amount of deviation (distance, I).
IIe), while sliding on the orthogonal keyways 28a, 29a and 28b, 29b, the rotation of the main rotor 7 is transmitted to the slave rotation g8.

As a result, the main rotation W7 rotates around the rotation center A,
Following this, the hammer device 8 rotates around the rotation center B at the same angular velocity as the main rotation W7.

Then, the wrap 11 of the main rotor blade 7 with the sum of r180'J
and the wrap 14 of the hammered device 8.
As seen in FIGS. 3 to 6, as the rotation progresses, the refrigerant ( compresses the suction gas).

Since this compression process is carried out inside the closed case 1,
No matter what the maximum differential pressure between the suction gas and the discharge gas is, the gas inside the compressor section will not leak to the outside air. This eliminates the need for a conventional sealing structure using oil that requires a large volume, and the entire device can be made smaller accordingly.

On the other hand, the refrigerant that has completed the final compression is discharged from the discharge hole 33. Inside the shaft section 12, inside the shaft section 25, check valve 34. The refrigerant is discharged into the sealed case 1 through the collision plate 43, and the discharged refrigerant is further discharged into the discharge pipe 3.
1 to the outside of the sealed case 1. In other words,
The inside of the sealed case 1 will be filled with discharged gas. As a result, the entire motor section 5, which generates a large amount of heat, is cooled in the atmosphere of the discharged gas. Note that the lubricating oil 2a separated from the gas by the collision with the collision plate 43 falls to the inner bottom of the sealed case 1.

Then, this discharged gas is sequentially transferred to the condenser 9a, the expansion valve 9b,
The refrigerant circulates through the evaporator 9C, forming a cooling cycle (cooling cycle).After evaporation, the refrigerant is sucked in from the suction pipe 32 again.

On the other hand, the trochoid gear pump 35 is driven by the rotation of the slave rotor 8 and sucks up the lubricating oil 2a from the oil reservoir 2. The sucked up lubricating oil 2a is branched into the main fixed frame 21 side and the sub fixed frame 22 side (and
The branched lubricating oil 2a on the main fixed frame 21 side passes through the oil supply path 36 to the main bearing portion 24 and the thrust bearing portion 44.
etc. are supplied to each sliding surface. Further, the lubricating oil 2a branched to the side of the sub-fixed frame 22 is supplied to each sliding surface such as the sub-bearing part 26 and the thrust bearing part 44.

However, by actively feeding each impulse surface, it is possible to secure a sufficient amount of oil necessary for lubrication.
Even in a fluid machine with a large load such as the compressor of this embodiment, stable operation without poor lubrication can be guaranteed.

Furthermore, the lubricating oil 2a after lubricating the sliding surface between the main bearing part 24 and the shaft part 25 is directed from the end of the main bearing part 24 toward the electric motor part 5 side as shown by the arrow in FIG. In other words, the rotor 4 and stator 5 are also cooled by oil.

This means that the motor section 5 can be cooled using the discharged gas and the lubricating oil 2a as they are, and the motor section 5 can be effectively cooled without requiring a complicated structure. Note that the lubricant/rt12a released to the electric motor section 5,
The lubricating oil 2 a after lubricating the sub-bearing part 26 and the thrust bearing part 44 returns to the oil reservoir part 2 .

Next, the lubricating oil 2a branched to the side of the auxiliary fixed frame 22 lubricates the sliding surfaces of the auxiliary bearing section 26 and the thrust bearing section 44, and then returns to the oil reservoir section 2a. In other words,
A predetermined amount of oil is always maintained in the sealed case 1. Therefore, there is no shortage of oil, resulting in a fluid machine with excellent lubrication performance.

On the other hand, during the above-described compression operation, the refrigerant sealed in the oil cooler 42 is evaporated by receiving heat from the lubricating oil 2a. Here, the evaporated refrigerant is guided to a heat radiation pipe 41 installed in the outside air where the temperature is low.

Then, this refrigerant radiates heat in the heat radiation pipe 40, condenses, and returns to the cooling pipe 40 again. The lubricating oil 2a is cooled by repeating such evaporation and condensation of the refrigerant.

Then, this cooled lubricating oil 2a is supplied to each sliding surface as described above, and the lubricating oil 2a cools the head plate 10.13 and wrap 11.14 of the main rotor g7 and the slave rotor 8. . As a result, suction gas, gas in the middle of compression,
It directly cools the discharged gas.

However, overheating (temperature rise) of the gas in each compression process can be suppressed, and the amount of work due to overpressure in the compression process and the amount of work in the discharge process can be reduced accordingly. According to experiments, as shown in the rP-V diagram in Figure 8, cooling with the oil cooler shown in the solid line reduces the amount of work in the compression process and the amount of work in the discharge process, compared to the oil cooler shown in the broken line without cooling. "
It was possible to reduce this by approximately 4%. Moreover, cooling not only reduces this amount of work, but also prevents the suction gas from overheating, increasing suction efficiency, and reducing bearing loads due to gas pressure, greatly improving the efficiency of fluid machinery. It brings benefits that can be achieved. In addition,
If the cooling pipe 40 is fixed by touching the sub-fixing frame 22 instead of floating on the oil sump 2, cooling can also be performed using the sub-fixing frame 22, so that the negative layer effect becomes larger.

In addition, in this embodiment, since the compressor section 6 is disposed below so as to be immersed in the lubricating oil 2a, the propagation of noise and vibrations emitted from the compressor section 6 can be attenuated.

Although the first embodiment uses an air-cooled oil cooler 42, the present invention is not limited to this, and other types of oil coolers 42 may be used. For example, as shown in FIG.
0 and the condenser 9a may be connected via a branch path 50, and the liquid refrigerant may be circulated through the cooling pipe 40. Of course, although not shown, the piping portion on the outlet side of the condenser 9a may be connected to the refrigerant piping 40. Of course, a cooler other than the oil cooler may be used.

Further, in the first embodiment, a hermetic compressor was shown in which the electric motor part 5 was provided in the upper part of the hermetic case 1, and the compressor part 6 was provided in the lower part, but the second embodiment shown in FIG. As in the embodiment, the present invention is applied to a hermetic compressor in which the compressor part 6 is provided in the upper side of the hermetic case 1, the electric motor part 5 is provided in the lower part, and the inside of the hermetic case 1 is filled with discharged gas. The same effect can be achieved. However, in FIG. 10, 36a is a guide path connected to a feeding path 36 formed inside the solid shaft portion 25. Of course, the present invention may be applied not only to a case high pressure type in which the inside of the sealed case 1 is filled with discharge gas pressure but also to a case low pressure type in which the sealed case 1 is filled with suction gas pressure. A third embodiment shown in FIG. 11 shows a case low-pressure hermetic compressor in which a compressor section 6 is provided on the upper side of a hermetic case 1, and an electric motor section 5 is provided on the lower side. . This differs from the second embodiment in that the discharge pipe 31 directly communicates with the discharge hole 33 via the discharge chamber 32a, and the suction pipe 32 communicates with the suction chamber 23 through a closed case high pressure type. ing.

However, in FIG. 10 and FIG. 11, the same components as in FIG. 1 are given the same reference numerals and their explanations are omitted.

In addition, although the internal tooth type trochoid gear pump 35 was used in the above-described embodiment, it is not limited to this pump, and other pumps,
For example, an external gear pump, a pump 60 using vanes 60a as shown in FIG. 12, a pump 61 using an eccentric boat 61 as shown in FIG. 13, etc. may be used. Furthermore, in each of the embodiments described above, the oil supply passage 36 was provided inside the main fixed frame 21 and the sub fixed frame 22, but the structure is not limited to this.
It is also possible to provide the oil supply path 36 by disposing the oil supply path 36 inside. Furthermore, it goes without saying that Oldham joints of other structures may also be used.

Further, although the present invention has been applied to a compressor in all of the above-described embodiments, it goes without saying that it may also be applied to other fluid machines such as expanders, pumps, blowers, etc.

[Effect of the invention] As explained above, according to the invention stated in claim 1,
Since the fluid machine operates within a sealed case, leakage to the outside air can be prevented regardless of the maximum differential pressure between the suction gas and the discharge gas.

Therefore, the conventional sealing structure is no longer necessary,
Accordingly, the scroll fluid machine can be made smaller.

Furthermore, the electric motor section (rotor, stator) can be cooled with a simple structure that uses the discharge gas or suction gas that is filled in the sealed case as it is.

In addition, since the structure uses a pump to suck up lubricating oil from the inner bottom of the sealed case and supply it to the sliding surface of the sliding shaft means, it is possible to secure a stable and sufficient amount of oil necessary for lubrication, making it possible to handle large loads. Even in the case of fluid machinery, lubrication failure does not occur and the reliability is excellent. Moreover,
After lubricating the sliding surfaces, a portion of the lubricating oil is discharged from the sliding surfaces and falls on the rotor and stator, so together with the previously discharged gas and suction gas, it efficiently cools the motor section. can bring benefits. Furthermore, even if a closed cycle is configured and lubricating oil is discharged from the discharge pipe in the closed cycle, it will enter the sealed case again and accumulate in the oil reservoir of the sealed case, so the lubricating oil accumulated in the oil reservoir will The oil amount will not decrease inadvertently.

Further, according to the invention described in claim 2, it is possible to prevent overheating of the gas in the sealed case, reduce the amount of work caused by overpressure, and further improve the efficiency of the scroll fluid machine by increasing the suction efficiency. can be done. Moreover, it is possible to reduce the bearing load due to gas pressure.
This also makes it possible to improve the efficiency of the scroll fluid machine.

[Brief explanation of the drawing]

1 to 8 show a first embodiment of the invention,
Fig. 1 is a side sectional view showing a hermetic compressor to which the present invention is applied, Fig. 2 is a plan sectional view taken along line A-A in Fig. 1, and Fig.
Figures 6 through 6 are plan sectional views showing the progression of the compression process performed by synchronous rotation of the main rotor and slave rotor, and Figure 7 is a configuration diagram showing a refrigeration cycle configured using a hermetic compressor. , Figure 8 shows that the amount of work is reduced by preventing overheating of the gas by cooling the cooler.p-v1! Figure, No. 9
The figure is a block diagram showing the structure of a different cooler together with a refrigeration cycle, and Fig. 10 shows a second embodiment of the present invention in which a compressor section is disposed in the upper side and an electric motor section is disposed in the lower side inside the sealed case. Side sectional view showing a high-pressure hermetic compressor in a case, Part 1
Fig. 1 is a side sectional view showing a low-pressure hermetic compressor in a case according to a third embodiment of the present invention, Figs. 12 and 13 are sectional views showing different pump structures, and Fig. 14 is a conventional one. FIG. 15 is a side sectional view showing a scroll fluid machine in which both rotating devices rotate, and FIG. 15 is a side sectional view showing a different scroll fluid machine. DESCRIPTION OF SYMBOLS 1... Airtight case, 2... Oil reservoir part, 3... Stator, 4... Rotor, 5... Electric motor part, 6... Compressor part, 7... Main rotation Wings, 8...Sub rotary wings, 10...
・End plate (end plate), 11... Wrap (wing part) 13・
... Mirror plate (end plate), 14... Wrap (end plate), 15.
... Groove ... (oil passage), 21 ... Main fixed frame,
22... Sub fixed frame, 24... Main bearing part (sliding bearing means), 26... Sub bearing part (sliding bearing means),
28a, 28b...Keyway (Oldham joint), 29
a, 29b...Keyway (Oldham joint 'f), -30
a, 30b...Key (Oldham joint), -41...
・Discharge pipe, 32...Suction pipe, 33...Discharge hole, 35
... Trochoid gear pump (pump), 36... Oil supply path (oil passage), A... Center of rotation, B... Center of rotation. Figure 2 Applicant's agent Patent attorney Takehiko Suzue Figure C

Claims (2)

[Claims] 1. An airtight case with an oil reservoir formed on the inner bottom for storing lubricating oil, and a spiral wing protruding from one side, which are combined so that the wings enter alternately into the airtight case. A main rotor and a slave rotor provided on one side, a discharge hole provided in the center of the end plate of the main rotor or the slave rotor, and an Oldham joint that transmits the rotation of the main rotor to the slave rotor. a sliding bearing means for rotatably supporting the rear side of the end plates of the main rotor blade and the slave rotor blade; a rotor provided on the other side of the sealed case and connected to the main rotor blade; a stator that is supported in a sealed case and constitutes a motor section together with a rotor; a suction chamber provided in the sealed case so as to surround the main rotor, the slave rotor, and the Oldham joint; A suction pipe connected to the sealed case and communicating with the suction chamber directly or through the inside of the sealed case, and a suction pipe connected to the sealed case and connected to the discharge hole corresponding to the suction pipe through the inside of the sealed case or directly. A communicating discharge pipe, an oil passage provided in the sealed case whose inlet side connects to the oil reservoir and whose outlet side opens to the sliding surface of the sliding bearing means, and an inlet of the oil passage provided in the sealed case. 1. A scroll fluid machine comprising: a pump for discharging lubricating oil from an oil reservoir. 2. 2. The scroll fluid machine according to claim 1, further comprising a cooler provided within the sealed case.