JPH1047268A - Hermetic scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce an oil rising quantity of a compressor by arranging plural passage parts to connect upper and lower spaces in a stator part outside edge part of an electric motor, forming a single passage among them as a passage of oil flowing in the downward direction, and forming the other passages as passages of compressed gas being a downward flow or a rising flow. SOLUTION: In a hermetic scroll compressor in which an electric motor chamber upper space is communicated with an electric motor chamber lower space through passages 25 (25a to 25d) between an electric motor stator and a casing inner wall surface 2m of a sealed vessel, a core cut part 3n is arranged in a stator outer peripheral part of an electric motor, and an outer peripheral part of a stator is vertically cut by four places, and a space part is formed. Among the spaces 25a to 25d, the whole area of the space 25a is made to function as a passage to flow oil in the downward direction, and the space 25b is made to function as a passage to flow compressed gas in the downward direction, and the spaces 25c and 25d are made to function as passages to flow compressed gas being a rising flow, respectively. Therefore, an oil separating function of the compressor is improved, and the cooling action on the electric motor is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a hermetic scroll compressor.

[0002]

2. Description of the Related Art Conventional scroll compressors are disclosed in JP-A-63-106386 (JP-B-6-70434, hereinafter referred to as Reference 1) and JP-A-5-141201 (hereinafter referred to as Reference 2). Call)
As disclosed in the official gazette, the oil that has lubricated the bearings and the like through the inside of the main shaft accumulates in the space of the balancer chamber that accommodates the balance weight, and further, through an oil drain hole or an external oil pipe. Thus, there is a structural example showing an oil discharge path to be discharged to a motor chamber or a bottom oil reservoir.

[0003]

In FIG. 4 of Reference 1 of the prior art, the oil lubricating the bearing and the like is supplied to the balancer chamber 104.
, And is further discharged to the lower space of the motor chamber through the oil discharge hole 29. However, since the oil that has flowed out of the oil drain hole 29 is exposed to the flow of the surrounding low-pressure refrigerant gas, the oil easily mixes again into the flow of the low-pressure refrigerant gas, and the mixed oil is combined with the refrigerant gas and There is a problem that the so-called oil rising phenomenon of the compressor increases, that is, the oil is directed toward the direction and further guided to both scroll portions, and eventually the oil flows out of the compressor. Further, the structure of the oil drain hole 29 is not disclosed in detail, and it is questioned whether the function as the oil drain hole is fulfilled.

In FIGS. 1 and 2 of the cited reference 2, the oil path lubricating the bearing and the like is discharged to the lower space of the motor chamber through the oil return hole 81 and the oil return pipe 82. Is shown. However, since the oil that has flowed out of the oil return pipe 82 is exposed to the flow of the surrounding low-pressure refrigerant gas, as in the case of the cited example 1, the oil easily flows into the flow of the low-pressure refrigerant gas again. Together, the oil droplets are sprayed from the state of the oil, and are further guided to both scroll portions, and eventually the oil flows out of the compressor. There is a problem of increasing. The structure of the oil return pipe 82 using the external piping has a complicated structure, which is difficult to mass-produce in terms of assemblability, and increases the manufacturing cost.

SUMMARY OF THE INVENTION It is an object of the present invention to reduce the amount of oil rising in a compressor and to effectively cool an electric motor. An object of the present invention is to improve the reliability of a compressor by preventing running parts from running out of oil and seizure.

[0006]

According to the present invention, a plurality of passages are provided at the outer periphery of the stator portion of the motor to connect the upper and lower spaces, and the passage means for connecting one of the passages to the oil reservoir at the bottom of the sealed container is provided. Provided in a closed container, the passage is a passage that mainly flows oil flowing downward, and the other passage is a passage that mainly flows compressed gas that becomes a downward flow or an upward flow. The structure of a hermetic scroll compressor characterized by the following.

Further, oil drainage passage means for guiding oil discharged from a main bearing portion or a swivel bearing portion which supports a main shaft at a center portion of the frame to an inner wall surface of a casing portion of a closed vessel is provided in the frame, and connects upper and lower spaces of an electric motor. A passage is provided in the outer peripheral portion of the stator, and a first oil discharge passage means for connecting an oil discharge port peripheral portion of the oil discharge passage means in the frame and a passage in the outer peripheral portion of the stator is provided in the casing portion of the sealed container. Features. Next, a plurality of passage portions are provided on the outer edge portion of the stator portion of the electric motor, and the one passage is a passage through which oil flows mainly downward, and the other passage is mainly a downward flow or an upward flow. It is characterized in that the passage is such that the compressed gas flows. Further, in the hermetic scroll compressor, a first oil discharge passage means for connecting a peripheral portion of an oil discharge port of the oil discharge passage means in the frame and a passage of the outer peripheral portion of the stator is provided in a casing portion of the closed container. It is characterized in that the area of the intake port for the discharged oil of the first oil discharge passage means is set to be larger than the passage area of the outer peripheral portion. Furthermore, the height of the oil intake of the first oil drain passage means is located above the position of the upper end face of the balance weight provided in the upper space of the motor chamber below the main bearing. I do.

As an example of a method in which the first and second oil discharge passage means are provided in a casing portion of a closed container, a case is shown in which a passage is set along an inner wall surface 2m of a casing 2a as shown in FIG. I have. That is, the oil discharged from the bearing portion is guided to the inner wall surface of the casing by oil discharge passage means provided on the frame, and the discharged oil is separated from the flow of the compressed gas in the upper space of the electric motor chamber by the oil discharge passage means, and the outer periphery of the motor stator is removed. It constitutes a first oil drainage path directly leading to a core cut portion serving as a passage of the portion. In addition, the oil drain guided to the core cut portion, which is a passage of the outer periphery of the motor stator, is directly guided to the oil reservoir of the bottom chamber by oil drain passage means isolated from the flow of the compressed gas in the lower space of the motor chamber. Of the oil drain path. Specifically, as shown in FIG. 1, the oil discharged after lubricating the bearing portions 32 and 40 reaches the hydraulic chamber 41, and is further discharged to the inner wall surface 2 m of the casing 2 a through the oil discharge hole 37. Is done. Next, the discharged oil is used as the partition plate 31.
a and a first oil drain passage 31 formed by the casing inner wall surface 2m and directly leading to the space 25a of the core cut portion 3n which is a passage of the outer edge of the stator 3a of the electric motor 3. . The oil discharge path is configured to be isolated from the flow of the compressed gas in the upper space 1b, which is the upper space of the motor room, so that the oil discharged from the bearing portion and the like can be reliably prevented from directly mixing into the compressed gas. Can be The oil guided to the space 25a of the core cut portion 3n serving as a passage of the outer edge portion falls along the casing inner wall surface 2m as it is. Further, in order to avoid mixing of the compressed gas and the discharged oil in the lower space 1c of the motor room, which has been a problem in the cited examples 1 and 2 of the related art, the partition plate 32a and the casing inner wall surface 2
m and the second oil drain passage means 32 formed by the electric motor 3
An outer edge 47e of the lower frame 47 is formed from the lower end of the core cut portion 3n which becomes a passage in the outer edge of the stator 3a. The oil flowing down from the lower end of the core cut portion 3n is directly transferred to the oil reservoir 2 of the bottom chamber by the second oil discharge passage means.
Lead to 2. As shown in FIG. 4, four core cut portions 3
n and a space 25a formed by the casing inner wall surface 2m,
At 25b, 25c, 25d, the space 25a is connected to the first oil discharge passage means, and the entire region of the space 25a has a function as a passage mainly through which oil flows downward. On the other hand, the space 25b is a flow of compressed gas mainly in the downward direction, though containing a small amount of oil, and 25c, 25d.
The two spaces are mainly passages through which the compressed gas flows so as to flow the compressed gas which becomes the upward flow, and a cooling effect of the motor, particularly a cooling effect to the lower portion of the motor, which is difficult to cool, can be obtained. As described above, the present invention is characterized in that the space of the core cut portion 3n in the outer peripheral portion of the stator is divided into a function mainly as a passage through which the compressed gas flows and a function mainly through the passage through which the discharged oil flows. Then, the oil return path by setting the first and second oil discharge passage means 31 and 32 along the inner wall surface of the casing and the flow path of mainly the compressed gas in the upper space 1b and the lower space 1c of the motor chamber are isolated. With this configuration, the oil discharged from the bearing portion or the like directly mixed into the compressed gas as seen in the cited example, and the oil rising phenomenon due to the blowing action by the refrigerant gas flow can be reliably prevented. This makes it possible to effectively obtain the oil separating function of the sealed container itself. With this configuration, the amount of oil rise in the compressor can be significantly reduced, and the cooling effect of the entire electric motor can be greatly improved. Further, in FIG. 9, a first balance weight 9a for canceling the centrifugal force caused by the turning motion.
Is fixed to the main shaft 14 on the side of the electric motor chamber 1b below the frame 11, the oil intake port 3 of the oil drain passage 31
The height of 1 m is set above the position of the upper end surface 9c of the balance weight 9a provided below the main bearing portion 41 so that the oil discharged from the discharge pipe 39 is balanced by the balance weight. 9A, the agitation loss due to the rotation of the balance weight 9a due to the fact that the space is not an atmosphere filled with oil can be significantly reduced, in combination with the fact that the space is a refrigerant gas region,
The motor input is greatly reduced, and an effect of improving performance is obtained. Since the oil discharge passage means 31 and 32 can be easily constituted by the partition plate and the inner wall surface of the closed container, a wide oil discharge passage having a small flow resistance and a small flow resistance can be easily produced, mass productivity can be improved in terms of assemblability, and the production cost can be reduced. Becomes

[0009]

1 to 13 show an embodiment of the present invention.
Shown over. In the drawings, solid arrows indicate the flow direction of the refrigerant gas, and broken arrows indicate the flow direction of the oil.

FIGS. 1 and 2 are longitudinal sectional views showing the overall structure of a hermetic scroll compressor. FIG. 1 shows an oil drainage path discharged from a bearing portion, etc., while FIG. The compressed gas flow mainly containing oil was shown. In addition, FIG.
FIG. 2 is a sectional view taken along line DD of FIG. 4, while FIG.
It is E sectional drawing. As shown in FIG. 1 and FIG.
The compressor unit 100 is accommodated in the upper part, and the electric motor part 3 is accommodated in the lower part. The inside of the closed container 2 is partitioned into an upper chamber 1a (discharge chamber) and electric motor chambers 1b and 1c, and a space 1d is provided below a lower frame 47 supporting the lower bearing portion 44.
There is. The compressor section 100 forms the compression chamber 8 by meshing the fixed scroll 5 and the orbiting scroll 6 with each other. The fixed scroll 5 is composed of a disk-shaped end plate 5a and a wrap 5b standing upright on the end plate 5a and having an involute curve or a curve approximating to the end plate 5a. 16C. As shown in FIGS. 10 and 11, the frame 11 has a main bearing portion 40 formed at the center thereof, the rotating shaft 14 is supported by the bearing portion 40, and the eccentric shaft 14 a at the tip of the rotating shaft is connected to the boss portion of the orbiting scroll 6. 6c is inserted so that a relative rotational movement is possible. The fixed scroll 5 is fixed to the frame 11 by a plurality of bolts, and the orbiting scroll 6 is supported on the frame 11 by an Oldham ring 38. The orbiting scroll 6 orbits with respect to the fixed scroll 5 without rotating. It is formed as follows. In FIG. 2, a motor shaft 14 b fixed to the rotor 3 b is integrally provided below the rotary shaft 14, and the motor unit 3 is directly connected. A vertical suction pipe 17 is connected to the suction port 16 of the fixed scroll 5 through the closed container 2, and the upper chamber 1 a in which the discharge port 10 is open is a passage 18 (18 a, 18 b).
Through the upper motor room 1b. From the passage 18, the compressed gas is passed through the gas guide passage means 2
Reaches 3. One embodiment of the entire structure of the gas guide passage means 23 is shown in FIGS. As shown in FIG. 3, the gas guide passage means 23 includes a U-shaped frame 23a and a collision plate 23b using the inner wall surface 2m of the casing. Discharge chamber 1
The compressed gas in which the oil is mixed is guided to the opening 29a of the U-shaped frame 23a, flows in the horizontal direction toward the winding portion 3c of the electric motor 3, and flows vertically through the opening 29b of the collision plate 23b. Core cut part 3n on the outer periphery of the stator of the motor 3 in the direction
And diverted into

The upper space 1b of the motor room communicates with the lower space 1c of the motor room via a passage 25 (25a, 25b, 25c, 25d) between the motor stator 3a and the inner wall surface 2m of the casing of the closed casing 2. I have. The upper motor chamber 1b communicates with a discharge pipe 20 penetrating through the closed casing 2. Reference numeral 22 denotes an oil reservoir at the bottom of the closed container. The lubricating oil 22 a is stored as an oil sump 22 in the lower part of the closed container 2. In addition, 15 is a check valve part. The upper end of the rotary shaft 14 has an eccentric shaft portion (crank pin) 14a, and the eccentric shaft portion 14a is a scroll compression element portion orbiting scroll 6 via a turning bearing 32 in a boss portion 6c of the end plate 6a of the orbiting scroll 6. Is engaged. The rotary shaft 14 has an eccentric vertical hole 13b for refueling each bearing.
4 is formed from the lower end to the upper end surface. The eccentric vertical hole 13b is connected to the center hole 13a of the oil pumping tube 27. 27
Is an oil-lifting pipe that connects the lower end of the rotating shaft 14 and the bottom oil sump 22. A main bearing (slide bearing type) 40 is provided below the eccentric shaft portion 14a, and the outer peripheral portion thereof seals a back pressure chamber 36 on the back surface of the end plate of the orbiting scroll and a high-pressure hydraulic chamber 41 around the main shaft side. A sealing means 34 is provided on the frame end face 11c. The first balance weight 9a for canceling the centrifugal force accompanying the orbiting movement of the orbiting scroll 6
Is fixedly arranged on the main shaft 14 on the side of the electric motor room 1 b below the frame 11. A first balance weight 9a for offsetting a centrifugal force caused by the orbiting movement of the orbiting scroll 6 is disposed on the main shaft 14 on the side of the motor room 1b below the frame 11.
The height of the oil intake 31 m of the oil drain passage 31 is determined by the upper end surface 9 of the balance weight 9 a provided below the main bearing portion 41.
It is located above the position of c. With such a vertical relationship, there is no danger that the discharged oil is agitated by the balance weight 9a. Stirring loss due to rotation of 9a can be greatly reduced.

In FIG. 2, the flow in the vertical direction into the space 25b of the core cut portion 3n on the outer periphery of the stator of the electric motor 3 is changed in the horizontal direction by the lower frame 47 to cool the lower part of the electric motor. Further, the compressed gas flows upward through the spaces 25c and 25d of the core cut portion 3n on the outer peripheral portion of the stator, reaches the upper motor chamber 1b again, and then flows out of the machine through the discharge pipe. In addition, as shown in FIG. 1 and below, as an example of a method provided in the casing portion of the closed container as the first and second oil discharge passage means 31 and 32, a passage along the inner wall surface 2m of the casing 2a as shown in FIG. This shows the case where it is set.

FIG. 4 is a sectional view taken along the line AA of FIG. FIG.
As shown in (2), the compressed gas containing the oil converted in the vertical direction by the flow dividing plate 23b directly collides with the winding part 3c of the electric motor 3, and the oil is separated from the compressed gas. further,
The compressed gas having a low oil content goes around the space between the upper winding portion 3c of the motor and the inner wall surface 2m of the casing of the closed container. The compressed gas exerts a cooling action on the winding portion, and the compressed gas by the centrifugal separation function. This promotes the action of separating the oil mixed with the gas from the gas, and then reaches the discharge pipe 20 in the opposite direction to the gas guide passage means 23. FIG. 5 is a partial perspective view showing the flow of oil around the oil outlet of the oil drain hole 37. In FIG.
A groove 11z having a wide opening facing the casing 2a is provided at an outer edge of the frame serving as an oil outlet. By forming the groove 11z having a wide frontage, the outflow speed of the discharged oil is reduced, and scattering of the oil adhering to the inner wall surface 2m of the casing is prevented.

FIG. 6 shows an oil discharge passage means 3 which is a dedicated oil passage between the partition plates 31a, 32a and the inner wall surface 2m of the casing.
It is the perspective view which comprised 1 and 32. FIG. 7 is a sectional view of FIG.
It is a cross-sectional view in B section. 47c is a hole connecting the spaces 1c and 1d.
The gap between the a and the rotor portion 3b is adjusted, and four positions are set at radial positions where the centering gap gauge can be inserted. Numerals 80 (80a to 80d) are tack welds for fixing the sita frame 47 to the casing 2a. FIG.
Is a cross-sectional view taken along the line CC of FIG.
25a, 25b, 25c, 25d of the communication passage 18 and the core cut portion 3n of the outer peripheral portion of the stator, and the discharge pipe 20
This shows the positional relationship with.

The core cut portion 3n of the outer peripheral portion of the stator shown in FIG.
This shows that a fan-shaped space is formed by cutting a portion. 3m is a cut surface of the core cut portion 3n. The spaces 25a, 25b, 25c, and 25d formed by the core cut portion 3n and the inner wall surface 2m of the casing have a function as a passage mainly through which the entire region of the space 25a flows downward and mainly serves as an oil passage. , And the two spaces 25c and 25d are the flows of the compressed gas that become the upward flow. As described above, in the present invention, the space of the core cut portion 3n in the outer peripheral portion of the stator is mainly used as a passage through which the compressed gas flows or a passage dedicated to the compressed gas.
On the other hand, the feature is that the function is divided as a passage through which the discharged oil flows or a passage dedicated to oil. This effectively achieves both effects of improving the oil separating function of the compressor and improving the cooling effect on the electric motor.

Here, the lubricating oil 22a inside the compressor is
An outline of the flow will be described. In FIG. 1, the lower end of the oil pump 27 immersed in the oil reservoir 22 of the lubricating oil 22a receives a high discharge pressure Pd. The lubricating oil 22 a in the oil reservoir 22 at the bottom of the container rises in the eccentric vertical hole 13 (13 b) by the action of the centrifugal pump in the eccentric vertical hole 13. 13d is a vent hole for venting the gas mixed in the oil, and discharges the gas into the space 1c. Around the slewing bearing 32 and the main bearing (slide bearing 40), the back pressure chamber 36 in the state of the intermediate pressure Pm, which is the pressure during compression, is sealed by the sealing means 34 by the small holes 6d provided in the slewing head plate 6a. Because it is isolated, it is in an atmosphere of approximately discharge pressure. The lubricating oil 22a that has risen in the eccentric vertical hole 13 is supplied to the main bearing 40 through the horizontal oil supply hole 13c, and to the swing bearing 3 through the main shaft upper end chamber 77.
2 is refueled. The oil supplied to the bearing portions 32 and 40 is discharged at one end to the hydraulic chamber 41, and most of the oil passes through the oil drain hole 37 and passes through the casing 2 as described above.
It is discharged to the inner wall surface 2m of a. Further, a small amount of oil in the hydraulic chamber 41 passes through the sealing means 34 and passes through the back pressure chamber 36.
Flows into. The oil flowing into the back pressure chamber 36 is as shown in FIG.
As shown in FIG. 11, the fluid flows into the Oldham chamber 51 through the communication passage groove 11m, and lubricates the periphery of the Oldham ring portion. Further, a part of the trace amount of oil leaks from the outer peripheral portion of the revolving head plate to the suction chamber 5f through the head plate sliding surface 5k and mixes with the suction refrigerant gas. On the other hand, the oil inside the back pressure chamber 36 is
Through d, it also flows out to the compression chamber 8. The oil reaching the compression chamber 8 is pressurized together with the refrigerant gas while sealing the gap between the scroll wraps and preventing leakage between the compression chambers,
Discharge chamber 1a above fixed scroll 5 via discharge port 10
Is further moved to the motor room 1b. The compressed gas mixed with the oil entering the compression chamber is supplied to the discharge chamber 1a and the motor chamber 1
In the course of the gas flow in b and 1c, the refrigerant gas and the oil are mainly separated, and the separated oil is transferred to the lower frame 4 of the lower portion of the closed vessel 2.
7, falls into the oil reservoir 22 through the hole 47c, and is again supplied to each sliding portion. With such an oil flow, lubrication in each part of the compressor is reliably performed. In addition, a deep groove ball bearing is applied to the lower bearing portion 44 to provide a bearing structure that is resistant to oil film breakage. On the upper end surface of the inner ring portion 44a of the deep groove ball bearing, the main shaft 14, the balance weight portions 9a and 9b, and the rotor portion 3
It has a thrust force support structure that can bear the load of its own weight such as b. With this configuration, the sliding bearing portion of the main bearing 41 does not require a special thrust bearing structure, and the main bearing 41 does not bear an extra load. Therefore, the main bearing 41 can be configured as a sliding bearing type bearing structure. Reliability around the bearing is improved.

FIG. 9 is a longitudinal sectional view of the hermetic scroll compressor showing the entire structure of the present invention. FIG.
FIG. 9 is a perspective view in which an oil discharge passage means 33 is configured by a partition plate portion 33a provided with a wide intake port for the discharged oil and an inner wall surface of a casing 2b. That is, the oil discharged from the bearing portion is guided to the inner wall surface of the casing by the oil discharge passage means provided in the frame, and the discharged oil is guided to the space of the core cut portion of the outer peripheral portion of the stator of the electric motor. This is an embodiment in which an oil discharge passage means provided with a wide oil intake is formed by a partition plate portion and an inner wall surface of a casing. As shown in FIGS. 9 to 12, the oil drain hole 37 is connected to the oil drain pipe 39, and the oil in the hydraulic chamber 41 is guided to the vicinity of the inner wall surface 2m of the casing 2a by the oil drain hole 37 and the oil drain pipe 39. The discharged oil is captured and stored in the drain passage means 33 having a wide frontage. As shown in FIG. 9, the drainage passage opening 3 having a wide frontage
By setting it to 3a, even if it scatters, the oil motor room upper space 1
b, and the amount of oil accumulated in the oil drain passage 30 increases. For this reason, the height (head) L1 of the oil column in the oil discharge passage 30 can be held higher, so that the oil casing 2a in the oil discharge passage means 33 and 25a and the oil discharge passage means 26 connected thereto.
The falling speed along the inner wall surface 2m of the oil tank increases, and the dropping action of the discharged oil can be performed smoothly and reliably. This leads to the effect of further improving the oil separation efficiency of the container itself. The lower frame 47 and the partition plate 32a have an integrated structure. Thereby, the assemblability of the lower frame 47 and the inner wall surface of the casing 2b around the lower frame 47 is improved, and the manufacturing cost is reduced.

Here, the difference between the operation and the effect of FIGS. 1 and 9 will be specifically described. FIG. 9 shows a first drainage in which liquid-state drainage oil is directly guided to a space 25a of a core cut portion 3n of a passage at an outer edge portion of the stator 3a of the motor 3 connected to the oil drainage passage means 31 of FIG. The second oil discharge passage means 32 formed by the partition plate 32a and the inner wall surface 2m of the casing is connected to the stator 3 of the electric motor 3 with respect to the structure constituting the oil path.
This is a structure in which a second oil drainage path for guiding oil drainage from the lower end of the core cut portion 3n, which is a passage at the outer edge portion a, to the outer edge portion 47e of the lower frame 47 is added. By configuring the second oil drain passage means 32, as described above, the mixing of the compressed gas mainly flowing in the upward direction in the lower space 1c with the oil discharged from the first oil drain path is completely avoided. This can prevent the splashing phenomenon of the discharged oil caused by the blowing action of the compressed gas, that is, the atomization phenomenon of the liquid oil, which is expected in FIG. That is
It has been experimentally confirmed that the oil separation performance of the sealed container itself can be significantly improved. For example, according to the embodiment of FIG. 9 as compared with the embodiment of FIG. 1, the effect of improving the amount of oil rise of the compressor by about 2% by weight is obtained. In addition, for example, a thin oil drain pipe is passed from the vicinity of the upper bearing portion through the core cut portion 3n of the passage on the outer edge portion of the stator 3a of the electric motor 3,
An oil passage for discharging into the lower space of the motor room is conceivable, but in such a case, the oil passage area cannot be sufficiently secured to about one tenth of that of the present invention, so that it cannot function as an oil drain pipe. There is a disadvantage that.

Further, in the above cited examples, as shown in FIG. 4, spaces 25a, 25b, 25c, 25 formed by four core cut portions 3n and a casing inner wall surface 2m.
d, a space 25a connected to the first oil drain passage means
Has a function as a passage mainly through which oil flows mainly in the downward direction, while the space 25b contains a small amount of oil but is mainly a flow of compressed gas in the downward direction.
The two spaces of 25d are mainly used for cooling because of a structure for appropriately dividing the flow of oil and gas at the outer peripheral portion of the electric motor, which serves as a passage for mainly flowing the compressed gas so that the flow of the compressed gas as the upward flow flows. There is no example that discloses the cooling effect of the motor, which provides an effective cooling effect to the lower part of the motor, which is difficult to perform.

FIG. 10 is a plan view of the frame 11 of the stationary member. As shown in FIGS. 10 and 11, in order to reduce the passage resistance in the oil drain passage, the inner diameter of the oil drain hole 37 and the oil drain pipe 39 is set to be equal to or larger than the inner diameter of the eccentric vertical hole 13. I have. Also, as shown in FIG. 8, the oil discharge passage means 30 (33), 25a and the oil discharge passage means 26 connected to the oil discharge passage means 30 are located substantially at the center of the passage 18 side and the discharge pipe 20 side opposite thereto. The oil draining action is not affected by the flow of the compressed gas in the electric motor chamber 1b.

FIG. 11 is a vertical cross-sectional view taken along the line M-O-N in FIG. 10, and is a partial vertical cross-sectional view showing the structure around the frame 11 and the sealing means 34. An end plate support seat 11f for supporting a rear portion of the end plate portion of the orbiting scroll is formed at an intermediate upper portion of a frame supporting the main shaft 14 at the center, and an Oldham ring 38 as a rotation preventing member of the orbiting scroll is provided with the orbiting scroll 6 and the frame 11. Place between There is a frame base surface 11p to which the Oldham ring main body 38a is axially opposed. In FIG. 11, the sealing means 34 for sealing the back pressure chamber 36 on the back surface of the end plate of the orbiting scroll and the high-pressure hydraulic chamber 41 on the periphery of the main shaft side is provided with an end surface 11c at the center of the frame.
In preparation. The oil flowing out of the bearing gap is prevented from flowing into the back pressure chamber 36 by the sealing means 34 as much as possible. The trace oil mixed in the back pressure chamber 36 moves to the Oldham chamber 51,
Used for oil lubrication at Oldham sliding parts. Also, regardless of the axial movement and tilting of the orbiting scroll 6 of several tens of microns, the orbiting boss 6c is removed except for the sealing portion of the sealing means.
Gap δ between the tip end surface 6n of the frame and the inner peripheral surface 11c of the frame.
c is secured. That is, the height Lm of the turning boss is set to be several hundred microns smaller than the height Lf of the frame base 11f. Practically, the axial clearance δc
= A gap of about 0.3 mm to about 0.5 mm. With this,
The distal end surface 6n is not damaged, and the sealing surface of the sealing portion 34 can be prevented from being damaged, so that the service life of the sealing portion mechanism can be extended and the reliability can be improved. That is, by setting the dimensional relationship of Lf> Lm, the axial movement of the rear surface of the end plate of the orbiting scroll is restricted by the upper end surface of the frame base.

In FIGS. 10 and 11, the space formed by the back surface of the orbiting scroll end plate 6a and the frame 11 is turned by an annular frame pedestal 11f which regulates the axial movement of the back surface of the orbiting scroll end plate on the frame side. Boss 6c
And an Oldham chamber 51 provided outside the frame pedestal portion and provided with an Oldham mechanism, and a groove 11m communicating the backpressure chamber and the Oldham chamber is formed in the upper end surface of the frame pedestal portion. However, the bottom surface of the communication groove 11m is set at a position higher than the position of the bottom surface 11p of the Oldham chamber 51 outside the frame base 11f. In addition, oil will inevitably accumulate in the Oldham keyway 57a. The oil 22a accumulated in the Oldham chamber 51 scatters around the Oldham ring main body 38a as the Oldham ring main body 38a reciprocates, forming oil droplets 22c for lubricating the sliding portions of the back pressure chamber and the Oldham chamber 51. . For this reason, even if the compressor is stopped, oil remains in that part, and especially oil is always present in the Oldham keyway 57a where the rotation load acts. When the compressor is restarted, the shortage of the oil amount unlike the conventional machine does not occur. In addition, the lubrication performance of the sliding portion of the Oldham mechanism due to an insufficient amount of oil is also prevented from being impaired, and the reliability of the Oldham mechanism can be improved.

Here, the amount of oil discharged to the inner wall surface 2m of the casing 2a through the oil drain hole 37 is approximately 85% of the total oil amount (the amount that is raised and supplied from the oil pumping pipe 27).
% To around 90%. On the other hand, the amount of oil flowing from the inside of the hydraulic chamber 41 into the back pressure chamber 36 through the sealing means 34 and circulating to the compression chamber 8 and further to the discharge chamber 1a is approximately 10% to the entire oil amount. The ratio is around 15%. Thus, according to the embodiment of the present invention, the amount of leaking oil is adjusted by setting the sealing means 34. On the other hand, it is possible to optimize the passage area (size) which requires a small flow passage resistance of the oil discharge passage. In addition, according to the embodiment of the present invention, the effect of high-temperature oil leakage from the side space to the suction chamber 5f seen in the conventional machine can be suppressed to a very small amount, so that the internal heating amount of the suction gas in the suction chamber is reduced. Can be greatly reduced. For this reason, the improvement of the volumetric efficiency by reducing the amount of internal heating of the suction gas and the reduction of the stirring loss can greatly improve the overall adiabatic efficiency. In the embodiment of the present invention, the case of the closed scroll compressor by the so-called high-pressure chamber system in which the inside of the closed vessel is in an atmosphere of a high discharge pressure has been described. It is also applicable to the case of a closed scroll compressor of a chamber type. An example is shown in FIG. Reference numeral 17 denotes a suction pipe, and the upper and lower spaces 1b, 1c, 1d of the electric motor room become an atmosphere of a suction pressure, and the refrigerant gas in the atmosphere passes through the suction passage 86,
Further, it is sucked into the scroll portion through the suction groove 87.
Next, from the discharge port 10 to the discharge chamber 1a via the compression chamber 8,
Further, the refrigerant gas is guided to the outside by a discharge pipe 20 provided in the upper chamber. Here, the lubricating oil 22a inside the compressor is
An outline of the flow will be described. In FIG. 13, the lower end of the oil pump pipe 27 immersed in the oil reservoir 22 of the lubricating oil 22a receives a low suction pressure Ps. The lubricating oil 22a in the oil sump 22 at the bottom of the container is
It rises in the eccentric vertical hole 13 (13b). The surroundings of the slewing bearing 32 and the main bearing (slide bearing 40) are in an atmosphere of a low suction pressure Ps, and the sealing means 34 is not attached. The lubricating oil 22a that has risen in the eccentric vertical hole 13 is supplied to the main bearing 40 through the horizontal oil supply hole 13c and to the swing bearing 32 through the main shaft upper end chamber 77. The oil supplied to the bearings 32 and 40 is once discharged to the hydraulic chamber 93, and further moves to the Oldham chamber 51, whereby the sliding portion of the Oldham ring can be reliably lubricated. The oil inside the Oldham chamber 51
The oil is discharged to the inner wall surface 2m of the casing 2a through oil draining means 88 such as an oil drain hole 88a provided at the outer edge of the casing 2a. The discharged oil is captured and stored in a drain passage means 33 having a wide frontage, and the passage 25a is further provided with a second oil discharge passage means 32.
Thus, the oil flowing down from the lower end of the core cut portion 3n can be directly guided to the oil reservoir 22 of the bottom chamber. As described above, the oil from the Oldham chamber 51, which is a low-pressure chamber, is moved to the inner wall surface of the container by means of a drainage means such as a drainage hole, and the drainage path means 33, 25a, and 32 directly transfer the oil to the oil reservoir 2 in the bottom chamber.
2 is characterized.

Also in the embodiment shown in FIG. 13, the space of the core cut portion 3n in the outer peripheral portion of the stator is divided mainly into a compressed gas passage function and a function mainly as an oil discharge passage. The oil return path and the flow path of mainly low-pressure refrigerant gas in the motor chamber upper space 1b and the motor chamber lower space 1c along the casing inner wall surface by setting the first and second oil drain passage means 33 and 32. With the isolated configuration, it is possible to reliably prevent the oil discharged from the bearing portion or the like from directly mixing into the refrigerant gas.

[0025]

According to the present invention, the following effects can be obtained.

(1) The amount of oil rise in the compressor can be greatly reduced, and the quality of the compressor can be improved.

(2) The oil discharged from the bearing portion is not directly agitated by the balance weight, so that the agitation loss due to the rotation of the balance weight can be greatly reduced, and the input to the compressor is reduced. In addition to improving the volumetric efficiency of the compressor, the energy consumption efficiency of the air conditioner can be greatly improved throughout the year.

(3) The cooling effect of the entire motor can be improved.

(4) As a result, the performance of the entire refrigeration cycle can be improved (the cooling capacity and the heating capacity can be improved by reducing the pressure loss of the piping, and the coefficient of performance can be improved).

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a hermetic scroll compressor showing an overall configuration of the present invention.

FIG. 2 is a longitudinal sectional view of the hermetic scroll compressor showing the overall configuration of the present invention.

FIG. 3 is a partial perspective view showing a flow state of refrigerant gas and oil around a gas guide passage means 23.

FIG. 4 is a cross-sectional view taken along the line AA of FIG. 1;

FIG. 5 is a partial perspective view showing a flow of oil around an oil outlet of an oil discharge passage 37;

FIG. 6 is a perspective view in which a partition plate and an inner wall surface of a casing constitute oil discharge passage means.

FIG. 7 is a transverse sectional view taken along the line BB of FIG. 1;

FIG. 8 is a cross-sectional view taken along the line CC of FIG. 1;

FIG. 9 is a vertical cross-sectional view of the hermetic scroll compressor showing another overall configuration of the present invention.

FIG. 10 is a plan view of a frame 11 of a stationary member.

FIG. 11 is a vertical cross-sectional view of the MON cross section in FIG. 10;

FIG. 12 is a perspective view of a partition plate 33a and an inner wall surface of a casing 2a constituting an oil drain passage means.

FIG. 13 is a longitudinal sectional view of a hermetic scroll compressor showing another overall configuration of the present invention.

[Explanation of symbols]

Reference numeral 2 denotes an airtight container, 2a denotes a casing portion, 5 denotes a fixed scroll, 6 denotes a revolving scroll, 11 denotes a frame, 14 denotes a main shaft (crankshaft), 18 denotes a communication passage, 31, 32 denotes first and second oil drain passages. Means, 31a, 32a, 33a: Partition plate part, 34: Sealing means, 40: Main bearing, 51: Oldham chamber.

Continued on the front page (72) Inventor Kenji Tojo 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Inside Hitachi, Ltd. Air Conditioning System Division (72) Inventor Mitsuhiro Okada 390, Muramatsu, Shimizu-shi, Shizuoka Prefecture Inside Air Conditioning System Division, Hitachi, Ltd.

Claims (1)

[Claims] A fixed scroll and an orbiting scroll which erect a spiral wrap on a head plate are meshed with the wrap inside, and the orbiting scroll is engaged with an eccentric shaft portion connected to a main shaft via an orbit bearing portion. In combination, the orbiting scroll is rotated with respect to the fixed scroll without rotating, the fixed scroll is provided with a discharge port opened at the center, and gas is sucked from the outer peripheral portions of both scrolls,
A hermetic scroll compressor in which a scroll compression element portion and a motor portion, which move around a compression space formed by the two scrolls to reduce the volume and compress the gas and discharge the compressed gas from a discharge port, are housed in a closed container. In the machine, a plurality of passages that connect the vertical space to the outer peripheral portion of the stator portion of the electric motor is provided, and a passage means that connects one of the passages and an oil reservoir at the bottom of the closed container is provided in the closed container, A hermetic scroll, wherein the passage is a passage mainly through which oil flows downward, and the other passage is a passage mainly through which a compressed gas flows as a downward flow or an upward flow. Compressor.