JPH11148474A - Enclosed scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the oil separation performance and the reliability by forming plural notch parts to be used as gas passages and oil passages on an outer peripheral part of a motor, and setting an outside dimension of the coil end parts of the upper and lower parts of a motor stator is determined to be equal to or larger than an outer peripheral size of the notch parts formed on the outer peripheral part of the motor. SOLUTION: An outer peripheral part of a motor 3 is fixed in a state that it is closely kept into contact with an inner wall face (2m) of a casing part (2b) of a closed container, and plural notch parts 25 (25a, 25b, 25c, 25d) to be used as gas passages and oil passages are formed on the outer peripheral part of the motor. An outside dimension (D1) of the coil end parts (3c, 3d) at the upper and lower parts of a motor stator (3a) is determined to be almost equal to an outer peripheral size (D3) (size of minimum stator width) of the notch parts formed on the outer peripheral part of the motor. The notch parts 25 are formed into a sector shape or a slit in the axial direction, whereby a contact area of a mixture of the refrigerant gas and the oil with the oil end parts 3c, 3d in the motor chambers 1b, 1c can be enlarged.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a hermetic scroll compressor used for a refrigerant compressor for refrigeration and air conditioning.

[0002]

2. Description of the Related Art A hermetic scroll compressor is a high-pressure chamber type in which a high-pressure atmosphere is provided in a closed container, and a compressor portion is provided at an upper portion of the container and a motor portion is provided at a lower portion thereof. An example is disclosed in Japanese Patent Application Laid-Open No. Hei 8-284853.

[0003]

The conventional hermetic scroll compressor has a disadvantage that the hermetic container itself has an insufficient oil separation function because of the high-pressure chamber structure in which the inside of the hermetic container has a high-pressure atmosphere. It has become. On the other hand, motor cooling is performed by the flow of high-temperature refrigerant gas and oil contained in the gas, but if the cooling effect is insufficient, the motor coil temperature rises, leading to a layer short-circuit accident due to poor insulation. There is a problem in terms of reliability of the compressor as a whole.

An object of the present invention is to solve the above problems and to provide a highly reliable hermetic scroll compressor.

[0005]

In order to achieve this object, the present invention relates to a hermetic scroll compressor, in which a motor outer peripheral portion is closely fixed to an inner wall surface of a casing portion of a closed container, and the motor outer peripheral portion is fixed. Are provided with a plurality of cutouts serving as gas passages and oil passages, and the outer dimensions of the coil end portions at the upper and lower portions of the motor stator are set to be equal to or larger than the cutout outer peripheral dimensions provided at the motor outer peripheral portion. Further, the ratio of the outer dimension D1 of the coil end portion at the upper and lower portions of the motor stator to the inner diameter dimension D2 of the casing is D1 / D2 = 0.95 or more.

Further, in a vertical hermetic scroll compressor, the outer dimensions of a lower coil end portion are set to be larger than those of an upper coil end portion in outer dimensions of a coil end portion located above and below a motor stator. It is characterized by adopting a configuration.

With this configuration, the area where the mixture of the refrigerant gas and the oil in the motor chamber contacts the motor coil end can be increased. This lowers the temperature rise of the coil end portion, and can further improve the oil separation function by the collision action at the coil end portion.
As a result, the oil separation performance of the container itself is improved, and the operation and effect of reducing the amount of oil rising from the compressor are obtained.

[0008] When the motor cooling is improved as compared with the conventional machine, the coil temperature is reduced, so that the actual motor efficiency is improved. This has the ripple effect that the input of the compressor can be reduced and the performance can be improved, and the energy consumption efficiency of the air conditioner can be greatly improved throughout the year.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS.

FIG. 1 is a longitudinal sectional view showing an embodiment of the hermetic scroll compressor according to the present invention. FIG. 2 is a cross-sectional view of FIG.
It is a top view showing C section.

In FIGS. 1 and 2, a scroll compressor unit 4 is accommodated in the upper part of the closed vessel 2 and a motor part 3 is accommodated in the lower part. The outer peripheral portion of the motor 3 is fixed in close contact with the inner wall surface 2m of the casing portion 2b of the closed casing 2. The inside of the closed container 2 is divided by a frame 7 into a discharge chamber 1a and a motor chamber 1b. The scroll compressor unit 4 forms a compression chamber (sealed space) 8 by interlocking the fixed scroll 5 and the orbiting scroll 6 with each other.

The fixed scroll 5 has a disk-shaped end plate 5a.
And a wrap 5b standing upright and formed into an involute curve and an arc curve. As shown in FIG. 2, a discharge port 10 is provided at the center and suction ports 16 and 16c are provided at the outer periphery. The orbiting scroll 6 includes a disc-shaped end plate 6a, an upright wrap 6b formed in the same shape as the wrap of the fixed scroll, and a boss 6c formed on an opposite lap surface of the end plate.

The frame 7 has a bearing portion formed at the center thereof, and a rotating shaft 14 is supported by the bearing portion. An eccentric shaft 14a at the tip of the rotating shaft is inserted into the boss portion 6c so as to be able to pivot. I have. The fixed scroll 5 is fixed to the frame 7 by a plurality of bolts. The orbiting scroll 6 is supported on the frame 7 by an Oldham mechanism 38 including an Oldham ring and an Oldham key. The orbiting scroll 6 does not rotate with respect to the fixed scroll 5. It is formed so as to make a turning motion.

A motor rotor is integrally connected to the lower part of the rotating shaft 14. 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.
a and 18b communicate with the motor chamber 1b.

The motor chamber 1b communicates with a discharge pipe 20 that penetrates the closed casing 2. The upper and lower portions of the motor chamber 1b are defined by the motor stator 3a and the side wall 2m
And a motor stator 3a and a motor rotor 3b. In addition, suction pipe 1
A seal through O-ring 53 is provided between the fixed scroll 5 and the high-pressure portion and the low-pressure portion. A check valve means 13a is provided in the suction pipe 17. The check valve 13a prevents the rotation of the rotating shaft 14 when the compressor is stopped, and allows the lubricating oil in the closed vessel to flow to the low pressure side. It is to prevent that.

A space 36 (hereinafter, referred to as a back pressure chamber) surrounded by the compressor unit 4 and the frame 7 is formed on the back surface of the end plate of the orbiting scroll 6. An intermediate pressure between the suction pressure and the discharge pressure is introduced through the fine holes 6 d formed in the end plate, and gives an axial force to press the orbiting scroll 6 against the fixed scroll 5.

The lubricating oil 22a is stored in the bottom portion 22 of the closed container 2, and the lubricating oil 22a is caused by a pressure difference between a high pressure in the closed container and an intermediate pressure in the back pressure chamber 38. After being sucked up, it rises in the hole (oil supply hole) 13 in the rotary shaft 14, and is supplied with oil to the swivel bearing 32, the main bearing 40, and the auxiliary bearing 39 through the lateral hole. The oil supplied to each bearing portion is injected into the compression chamber 8 of the scroll wrap via the back pressure chamber 38, mixed with the compressed gas, and then discharged to the discharge chamber 1a together with the discharge gas.

With the above configuration, when the rotary shaft 14 directly connected to the motor rotor 3b rotates and the eccentric shaft 14a rotates eccentrically, the orbiting scroll 6 makes a revolving motion via the revolving bearing 32. Due to this swirling motion, the compression chamber 8 gradually moves to the center and the volume decreases. The working gas enters the suction chamber 5f from the suction pipe 17 via the suction port 16, and the oil lubricating the bearings is supplied from the outer peripheral gap of the orbiting scroll 6 to the suction chamber 5f.
Into the working gas. The working gas containing the oil passing through the bearing and the oil injected from the hole 6d is compressed in the compression chamber and discharged from the discharge port 10 to the upper chamber 1a, and passes through the passages 18a and 18b to the motor chamber 1b. Flows into

As shown in FIG. 2, the passage 25 (25a, 2a)
5b, 25c, 25d) are fan-shaped notched passages provided on the outer peripheral portion of the motor 3. In FIG. 1, solid arrows indicate the flow of the refrigerant gas, and broken arrows indicate the flow of the oil. The working gas and oil flowing from the narrow passages 18a and 18b into the motor chamber 1b in the wide space have their flow rates sharply reduced, and the flow direction of some of the gases changes.

The gas and oil flow down through the passage 25b to reach the lower motor chamber 1c. The gas velocity is reduced in the space between the coil end portion 3d and the partition plate 47, and an oil separating action is performed in the space due to the change in direction from the vertical direction to the horizontal direction. Further, the gas rises through the passage 25c and enters the upper motor chamber 1b again. Since the space is a wide space, the gas velocity in the space decreases, and most of the oil contained in the gas is separated.

Further, the gas flows out into the discharge pipe 20. The oil is supplied to the holes 47f and 47g of the partition plate 47 (FIG. 5).
(See FIG. 2) and accumulates at the bottom 22 of the closed container 2. Lubricating oil 22a stored in the bottom 22 of the closed container 2
Is the pressure (discharge pressure) in the closed container 2 and the back pressure chamber 36
Flows into the pipe 27 by a pressure difference from the pressure (intermediate pressure).

As described above, since the inside of the closed container 2 has a relatively large space, the closed container 2 itself has an oil separating function, and most of the oil and the refrigerant gas discharged into the closed container 2 have an oil separating function. Is separated from the gas in the closed container 2 and then collected in an oil reservoir at the bottom of the container.

FIG. 3 is a plan view of one embodiment showing a cross section taken along line AA of FIG. FIG. 4 is a plan view of another embodiment showing the AA cross section of FIG. As shown in FIG.
The outer peripheral portion of the motor 3 is fixed in close contact with the inner wall surface 2m of the casing portion 2b of the sealed container, and a plurality of cutout portions 25 (25a, 25a) serving as a gas passage and an oil passage are provided in the outer peripheral portion of the motor.
b, 25c, 25d).

The outer dimensions D1 of the coil end portions 3c and 3d at the upper and lower portions of the motor stator 3a are determined by the outer dimensions (minimum stator width dimension) of the notch provided on the outer peripheral portion of the motor.
It is set almost equal to 3. The cutout portion 25 is set in a fan shape or a slit shape in the axial direction. FIG.
Is an embodiment in which D3 <D1 is set.

Further, the effect of the present invention is that the ratio of the outer dimension D1 of the coil end portions 3c and 3d at the upper and lower portions of the motor stator 3a to the inner diameter D2 of the casing is D1 / D2 = 0.95 or more. It is a practical value obtained.

With this configuration, the motor chamber 1b,
The area where the mixture of the refrigerant gas and the oil in 1c contacts the motor coil end portions 3c and 3d can be increased.
This reduces the temperature rise at the coil end,
Further, the oil separation function by the collision action at the coil end can be dramatically improved. As a result, the oil separation performance of the container itself is improved, and the operation and effect of reducing the amount of oil rising from the compressor are obtained. The notch outer peripheral dimension (minimum stator width dimension) D3
The ratio of the ratio of D3 / D2 to the inner diameter D2 of the casing D3 / D2 = 0.92 to 0.95 is a practical dimension. Within this range, the above dimensional relationship is appropriate.

Next, in FIG. 5, gas and oil flow down through the passage 25b to reach the lower motor chamber 1c. Since the gap L2 is smaller than that of the conventional machine, the gas and the oil easily collide directly with the coil end 3d. Coil end 3d
The gas velocity is reduced in the space between the partition and the partition plate 47, and an oil separation action is performed in the space in accordance with the change in direction from the vertical direction to the horizontal direction. Further, the opposite coil end portion 3
Through d ', it rises through the passage 25c and reaches the upper motor chamber 1b again. Since the space is large, the gas velocity in the space decreases, and most of the oil contained in the gas is separated. Further, the gas flows out into the discharge pipe 20. The oil flows down through the holes 47f and 47g of the partition plate 47, and flows into the bottom portion 22 of the closed container 2.
Accumulate in

FIG. 6 is a partial sectional view showing the flow of gas and oil in the motor chamber according to another embodiment of the present invention. In FIG. 6, in the vertical closed scroll compressor, the outer dimensions of a coil end portion 3d lower than the outer dimension D2 of the upper coil end portion 3c in the outer dimensions of the coil end portions located at the upper and lower portions of the motor stator 3a. D7 is set to be large.

With this configuration, the gaps L2 and L3 between the coil end portion 3d and the inner wall surface 2m of the casing are smaller than the gap L1 between the upper coil end portion 3c and the inner wall surface 2m of the casing. The region where the mixture of the refrigerant gas and the oil directly contacts and collides with the motor coil end portion in 1c can be further enlarged. This lowers the temperature rise of the lower coil end portion, and the oil separation function by the collision action with the coil end portion 3d can be remarkably improved. As a result, the oil separation performance of the container itself is improved, and the operation and effect of reducing the amount of oil rising from the compressor are obtained.

Improvements in motor cooling over conventional machines further improve substantial motor efficiency, especially as the lower coil temperature is reduced. With this configuration, the area where the mixture of the refrigerant gas and the oil in the motor chamber contacts the motor coil end portion can be increased. This lowers the temperature rise of the coil end portion, and can further improve the oil separation function by the collision action at the coil end portion. As a result, the oil separation performance of the container itself is improved, and the operation and effect of reducing the amount of oil rising from the compressor are obtained.

When the motor cooling is improved as compared with the conventional machine, the coil temperature is reduced, so that the actual motor efficiency is improved.

[0032]

(1) By improving the motor cooling according to the present invention, motor characteristics such as motor efficiency are improved.
As a result, it is possible to provide a highly reliable compressor including the performance improvement and the effect of reducing the amount of oil rise as a single compressor,
The restriction is further reduced by the operation range on the unit side, and the usability can be improved.

(2) The motor input is reduced, a scroll compressor with high energy saving is obtained overall, and the energy consumption efficiency of the air conditioner can be greatly improved throughout the year.

(3) Easier coil shaping, which can prevent scratches on the coil during coil shaping and can improve the mass productivity of motor manufacturing.

(4) An accident due to a short-circuit occurring in a conventional motor can be prevented.

[Brief description of the drawings]

FIG. 1 is a longitudinal section of a hermetic electric compressor showing an entire structure of the present invention.

FIG. 2 is a plan view showing a CC section of FIG. 1;

FIG. 3 is a plan view of one embodiment showing an AA cross section of FIG. 1;

FIG. 4 is a plan view of another embodiment showing a cross section along AA in FIG. 1;

FIG. 5 is a partial cross-sectional view showing a flow state of gas and oil in a motor chamber according to the present invention.

FIG. 6 is a partial cross-sectional view showing a flow state of gas and oil in a motor chamber according to another embodiment of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Closed container, 1a ... Discharge chamber, 1b ... Motor chamber, 3 ... Motor part, 4 ... Scroll compressor part, 5 ... Fixed scroll, 5a ... Disc-shaped end plate, 5b ... Wrap, 5f ... Suction chamber, 6 ... orbiting scroll, 6a ... disk-shaped end plate, 6b ...
Wrap, 6c: boss, 6d: intermediate pressure hole, 7: frame, 8: compression chamber, 10: discharge port, 13: oil supply hole, 13a
... check valve means, 14 ... rotating shaft, 14a ... eccentric shaft, 16 ...
Suction port, 16c passage, 17 suction pipe, 20 discharge pipe,
Reference numeral 22 denotes a closed container bottom, 22a denotes lubricating oil, 27 denotes an oil suction pipe, 32 denotes a swivel bearing, 36 denotes a back pressure chamber, 38 denotes an Oldham mechanism, 39 denotes an auxiliary bearing, and 40 denotes a main bearing.

Claims (1)

[Claims] 1. A compressor unit and a motor unit are housed in a closed container, and the compressor unit is configured by engaging a fixed scroll and an orbiting scroll which erect a spiral wrap on a head plate with the wraps inside each other. The orbiting scroll is engaged with an eccentric mechanism connected to the rotating shaft to make the orbiting scroll orbit relative to the fixed scroll without rotating. The fixed scroll has a discharge port opened at the center and a suction port opened at the outer periphery. In a hermetic scroll compressor in which a gas inlet is provided, a gas is suctioned from a suction port, the gas is compressed around a compression chamber formed by both scrolls to reduce the volume, and the compressed gas is discharged from a discharge port. The outer peripheral portion of the motor is fixed in close contact with the inner wall surface of the casing portion of the sealed container, and a plurality of cutout portions serving as a gas passage and an oil passage are provided in the outer peripheral portion of the motor. Le compressor - hermetic scroll, characterized in that set equal to or larger than the notch portion outer peripheral dimension provided with outer dimensions of a coil end portion to the motor outer peripheral portion.