JP2620409B2 - Hermetic scroll compressor - Google Patents

Description

Description: BACKGROUND OF THE INVENTION The present invention relates to a hermetic / oil-filled scroll compressor used for a refrigerant compressor, an air compressor, a helium compressor, etc., and particularly to a compressed gas and oil compressor. The present invention relates to a closed-type oil-supplying scroll compressor suitable for efficiently separating oil from a mixture.

2. Description of the Related Art As a conventional technique for separating oil from a mixture of compressed gas and oil in a closed-type oil-supply scroll compressor, there is an oil separation method disclosed in, for example, Japanese Patent Application Laid-Open No. 62-203992. The above prior art discloses a structure in which a wire mesh is lined on an inner wall surface of a casing forming a motor room in order to enhance oil separation performance from gas around a motor. On the other hand, in recent years, there has been an increasing demand for achieving a higher speed of the compressor and further reducing the size of the compressor, particularly in order to widen a capacity control range of an air conditioner or the like.

[Problems to be Solved by the Invention] Although the oil separation performance in the electric motor room is improved in the above-described conventional technology, when the compressor is downsized with an increase in speed,
For example, when the number of rotations of the compressor is as high as about 10,000 rpm, the gas flow speed is increased, the action of blowing up oil in the closed container is promoted, and the amount of oil flowing out of the compressor from the compressor. Increase. In other words, under the conditions of high speed and small size of the compressor, the oil separation performance in the motor room has reached the limit, and the oil separation efficiency of the whole chamber (closed vessel) is not improved only by improving the oil separation in the motor room. There is still the problem of being low.

If the efficiency of oil separation in a closed container deteriorates, the amount of oil flowing out of the compressor from the compressor increases, and especially at high speeds, the oil level at the bottom of the closed container must be kept at a certain position. Becomes difficult. If the oil level at the bottom of the sealed container cannot be maintained at a certain position, it becomes difficult to supply oil to bearings and the like, and there is a problem that the reliability of the compressor is reduced.

SUMMARY OF THE INVENTION An object of the present invention is to provide a structure of a closed-type oil-supply type scroll compressor which can enhance the oil separation performance of the entire compressor even when the operation is performed at high speed and is small in size, and can greatly reduce the amount of oil discharged from the compressor. Is to provide.

Means for Solving the Problems In order to achieve the above object, the present invention relates to a fixed scroll having a closed container upper lid forming a discharge chamber space above a fixed scroll and a discharge port in a closed-type refueling scroll compressor. The depth of the discharge chamber is increased by securing the axial distance of the member from the end plate to a certain value or more.Specifically, the lid of the closed container forming the discharge chamber and the end plate of the fixed scroll The height of the discharge chamber is set so that the axial dimension between the discharge chamber and the inner diameter of the chamber formed by the closed container is 0.25 times or more, and the gas flowing into the discharge chamber from the discharge port at the central portion of the fixed scroll. The gas flow direction changing body that directs the flow of gas toward the side wall of the discharge chamber is installed on the end plate of the fixed scroll so as to face immediately above the discharge port, and the volume Vdo of the discharge chamber has a ratio Vdo ^* (Vdo ^* = Vdo / ( Vth ・ N) Where Vdo is the volume occupied by the space of the discharge chamber (cm ³ ), and Vth is the stroke volume of the compressor (cm ³ / rev) N: the rated rotation speed (Hz). It is characterized by the following.

[Operation] The gas and oil flowing upward into the discharge chamber from the discharge port at the center of the fixed scroll member have a large depth of the discharge chamber, which is at least 0.25 times the inner diameter of the chamber, and a large depth, so that the discharge chamber space is sufficient. Due to the large size, the velocity in the rising flow is greatly reduced, and the collision speed between the upper lid and the rising gas flow is very low, and the oil contained in the gas is in a liquid state without being atomized. With this, the liquid accumulates in the lower part of the discharge chamber. This oil then returns to the lower motor chamber via the communication passage and further to the bottom sump. Thus, the oil separation performance in the discharge chamber can be improved, which has a great effect on the oil separation efficiency of the sealed container itself. On the other hand, in the conventional example,
The discharge chamber height is about 0.1 times the inner diameter of the chamber (specifically, 0.10
(0.15 times) and the end plate part of the fixed scroll member and the upper lid are in close proximity, so that the velocity of the gas flowing out from the discharge port is very high, about 20 meters per second, on the inner surface of the upper lid. The gas will collide, and the oil mixed in the gas will be easily fragmented and atomized,
Poor oil separation efficiency in the discharge chamber. The inventors of the present invention have experimentally found the above-mentioned effects.

Further, by providing the gas flow direction changing body in the end plate portion of the fixed scroll member, it is possible to further avoid the above-described collision action between the upper lid and the gas, and disperse the gas flow in almost all directions with the gas flow in the horizontal direction. By doing so, the gas velocity can be further reduced.

In addition, as a result of the above-described operation, the pressure pulsation in the discharge chamber is reduced during high-speed operation, so that an effect of noise reduction due to the pressure pulsation of the compressor is derived. In addition, by positioning the gas flow direction changing body close to the discharge hole, oil mixed in the gas can be forcibly suppressed in the space below the discharge chamber, and then the gas rises. Combined with the effect of generating a flow, it is possible to minimize fragmentation and atomization of oil mixed in the gas in the discharge chamber.

[Embodiment] Fig. 1 shows one embodiment of the present invention, and is a longitudinal sectional view showing the entire structure of a closed-type oil-supplying scroll compressor in which the space of a discharge chamber 1a is secured to be longer than that of a conventional machine. is there. The upper lid 2a of the closed container 1 is formed by deep drawing a thin plate material, and has an axial dimension longer than that of the conventional machine. For comparison, the upper lid of the conventional closed container is shown by a broken line in FIG. As shown in FIG. 1, in the present embodiment, the axial dimension ld between the upper lid 2a forming the discharge chamber 1a and the end plate 5a of the fixed scroll member 5 is set to be long, and the space of the discharge chamber 1a is set to a depth. It is characterized by having a relatively vertically long space.

The above-mentioned hermetic / oil-supply scroll compressor will be generally described.

In FIG. 1, a compressor unit 100
However, the motor unit 3 is housed below. The inside of the sealed container 1 is a relatively long and deep upper chamber (discharge chamber).
1a and motor rooms 1b and 1c.

In the compressor section 100, a fixed scroll member 5 and an orbiting scroll member 6 are engaged with each other to form a compression chamber (closed space) 7. The fixed scroll member 5 includes a disk-shaped end plate 5a,
The wrap 5b is formed upright on the involute curve or a curve similar to the wrap 5b. The wrap 5b has a discharge port 10 at the center and a suction port 16 at the outer periphery. The orbiting scroll member 6 includes a disk-shaped end plate 6a, and a wrap 6b that stands upright and is formed in the same shape as the fixed scroll wrap 5b.
It comprises a boss 6c formed on the anti-lap surface of the end plate 6a. The frame 11 has main bearings 40 and 9 in the center,
The rotating shaft 14 is supported by the main bearing portion, and the eccentric shaft 14a at the tip of the rotating shaft is inserted into the boss 6c so as to be capable of turning movement.

The fixed scroll member 5 is fixed to the frame 11 at the outer peripheral portion thereof by a few bolts, and is rotated by an Oldham mechanism 12 including an Oldham ring and an Oldham key interposed between the orbiting scroll member 6 and the frame 11. The member 6 makes a revolving motion without rotating on the fixed scroll member 5.
The lower portion of the rotating shaft 14 is integrated with a motor shaft 14b fixed to the motor rotor 3b, and is directly connected to the motor rotor 3b. The closed container 1 is provided at the suction port 16 of the fixed scroll member 5.
A vertical suction pipe 17 is connected through the upper lid 2a. The upper chamber (discharge chamber) 1a in which the discharge port 10 is open is a fixed scroll member 5 closely attached to the body 2b of the closed casing 1.
And it communicates with the upper motor chamber 1b via a communication passage 18 formed by a groove provided on the outer peripheral portion of the frame 11. The upper motor chamber 1b communicates with the lower motor chamber 1c via a passage 19 between the motor stator 3a and the body 2b of the closed casing 1. The upper motor chamber 1b communicates with a discharge pipe 20 penetrating the closed casing 1. Reference numeral 22 denotes an oil reservoir at the bottom of the closed container. In the drawing, solid arrows indicate the flow direction of the refrigerant gas, and broken arrows indicate the flow direction of the oil.

The closed container 1 includes a deep-drawn upper lid 2a and a body 2
b, formed by the lower lid 2c. The container 1 is integrated with the foot 2e. For the upper main bearing portion 40, a rolling bearing having high reliability against oil film shortage is used. In this embodiment, the fixed scroll member is made of cast iron, and the orbiting scroll member is made of an aluminum alloy.

In a space 41 (referred to as a "back pressure chamber") surrounded by the back surface of the orbiting scroll member 6 and the frame 11, gas pressure in a plurality of sealed spaces 7 formed by both the orbiting and fixed scroll members is provided. In order to oppose the gas force in the thrust direction (this force is a repulsive force that pushes down the orbiting scroll member 6 downward), the intermediate pressure between the suction pressure (low pressure side pressure) Ps and the discharge pressure Pd be introduced. The introduction of the intermediate pressure is performed by providing a small hole 6e in the end plate 6a of the orbiting scroll member 6, and through this small hole 6e, the gas inside the closed space 7 formed by the orbiting and fixed scroll members is passed through the back pressure chamber 41. To the intermediate pressure Pm introduced into the back pressure chamber 41.
Acts on the back of the orbiting scroll to generate a pressing force that opposes the separating force. The method of applying this intermediate pressure is disclosed in
-119412 and JP-A-55-37520, etc., and a detailed description thereof will be omitted.

The lubricating oil is stored as an oil sump 22 in the lower part of the closed container 1. An eccentric shaft portion 14a is provided on the upper portion of the main shaft 14, and the eccentric portion 14a is engaged with a turning bearing 39 provided in a boss 6c of the orbiting scroll member 6. In the main shaft 14, a central vertical hole 13 for supplying oil to each bearing is formed from a lower end of the main shaft to an upper end surface of the main shaft. Reference numeral 13a denotes an oil-lifting pipe connecting the lower end of the main shaft and the oil reservoir 22 at the bottom. At the lower part of the eccentric shaft part 14a, a balance weight 8 is formed integrally with the main shaft 14 at the upper part of the main bearing 40 facing the distal end face of the orbiting scroll boss part 6c. A high-pressure discharge pressure Pd acts on the lower end of the oil-lifting pipe 13a immersed in the lubricating oil reservoir 22, while the surroundings of the downstream slewing bearing 39 and the upper main bearing 40 are exposed to an atmosphere of an intermediate pressure Pm. Therefore, the oil in the lubricating oil reservoir 22 at the bottom of the container rises in the central vertical hole 13 due to the pressure difference of (Pd-Pm). As described above, the lubrication of each bearing portion is performed by the differential pressure lubrication method using the center hole lubrication.

The lubricating oil that has risen in the central vertical hole 13 is supplied to the lower main bearing 9 and the upper main bearing 40, and the upper space of the eccentric portion 14a (the bottom surface of the orbiting scroll boss portion 6c and the upper end surface of the eccentric shaft portion 14a). Oil is supplied to the swivel bearing portion 39 through a gap portion). The oil is supplied to the bearings 39 and 40 and enters the back pressure chamber 41.
The oil flowing into the back pressure chamber 41 mixes with the refrigerant gas and flows out to the compression chamber 7 via the back pressure hole 6e. The oil that has reached the compression chamber 7 is pressurized together with the refrigerant gas and reaches the discharge chamber 1 a above the fixed scroll 5 from the discharge port 10. Here, the oil in the gas is efficiently separated, moves to the communication passage 18 in a two-phase state of the oil layer and the refrigerant gas, and further moves to the motor chamber 1b. The oil in the refrigerant gas is separated from the gas in the electric motor room, and the separated oil falls into the oil sump 22 and is supplied again to the bearings and sliding parts.

FIG. 2 is a plan view of the fixed scroll member 5 viewed from the wrap side, FIG. 3 is a side sectional view of the frame 11, and FIG. The communication passage 18 connecting the discharge chamber 1a and the motor chamber 1b is formed as three grooves provided on the outer peripheral edges of the fixed scroll member 5 and the frame 11. this is,
This is to reduce the falling speed of oil and gas flowing down the communication passage as much as possible.

In the embodiment described above, the height ld (see FIG. 1) of the discharge chamber 1a is made higher than the conventional one (that is, the depth of the discharge chamber is made deeper), so that the oil is separated from the gas in the discharge chamber 1a. It has improved performance.

Next, in the embodiment shown in FIG. 1, the gas flow direction is further changed so that the flow of the gas flowing out from the discharge port 10 at the center of the fixed scroll member 5 is directed toward the side wall 47 of the discharge chamber 1a. FIGS. 5 to 8 show several embodiments in which a plate is attached to the fixed scroll end plate 5a so as to face the discharge port 10. FIG.
In the embodiment shown in FIG. 5 and FIG. 6, which is a top view of the fixed scroll, the gas flow direction changing plate 52 is
From the discharge chamber 1a and the motor chamber 1b.
The mounting direction is such that it faces in the opposite direction. FIG. 7 shows a gas flow direction changing plate 55 mounted in a mounting direction such that the gas flow from the discharge port 10 is directed toward the communication passage 18 described above.
Alternatively, an embodiment having a gas flow direction changing plate 54 (indicated by a dashed line) mounted in a mounting direction such that the gas flow from the discharge port 10 is directed in a direction lateral to the communication path 18 is shown. . 52a,
54a, 55a, etc. are fixing bolts for fixing the gas flow direction changing plate to the fixed scroll head plate. Reference numeral 5j denotes a bank portion of the fixed scroll head plate, and reference numeral 5p denotes an oil passage formed by cutting the bank portion 5j.
According to these embodiments, the efficiency of separating oil from the gas discharged from the discharge port 10 is further improved. Experimentally, it has been found that the embodiment shown in FIGS. 5 and 6 has the highest oil separation efficiency as the chamber itself.

FIG. 9 shows an embodiment in which means 58 having both functions of a gas flow direction changing plate function and a check valve function is attached to the end plate portion 5a of the fixed scroll. The main body 58c of the means 58 has a function of a retainer function (receiving portion) for supporting the reed valve 56 as a check valve;
It has a function as a gas flow direction change plate that changes the direction of the gas flow discharged upward from the discharge holes 10. The reed valve 56 swings up and down by about 2 to 3 mm. Even with such a valve lift, the function of changing the direction of gas flow can be sufficiently performed.
Rather, such an interval has an effect of forcibly holding oil in the lower space of the discharge chamber 1a, and is preferable in terms of oil separation action.

Here, the flow of oil and gas in the chamber (sealed container) 1 in each of the above embodiments will be described with reference to FIG.
The mixture of the compressed gas and the oil discharged into the discharge chamber 1a collides with the upper inner periphery of the body 2b of the closed container 1 and the side wall surface of the upper lid 2a forming the discharge chamber 1a, and changes the flow direction. Is separated into compressed gas and oil by the first-stage oil separation operation. The oil separated from the compressed gas by the oil separating action of the discharge chamber 1a gathers on the peripheral surface 5c on the upper surface of the fixed scroll 5 at the lower part of the discharge chamber 1a as shown in FIG. Form. The mixture of the compressed gas and the oil 28a separated in the discharge chamber 1a and the unseparated compressed gas and the oil are in phase with the fixed scroll end plate 5a of the scroll compressor and the outer edges of the frame 11 and have the same size. 1, FIG. 2, and FIG.
As shown in FIG. 10, the water flows downward and flows down to the motor room 1b. In FIG. 10, reference numeral 28b denotes the oil droplet flowing downward with the gas.

FIG. 11 and FIG. 12 are explanatory views showing the oil separating action in the closed container described above. Here, the oil discharge amount indicates the amount of oil flowing out from the discharge pipe 20 by a weight ratio with respect to the circulation amount of the refrigerant gas. The horizontal axis in FIG. 11 represents the discharge height ld ^* (dimensionless value) shown in the following equation.

Here, ld: height of the discharge chamber (see FIG. 1) D: inner diameter of the chamber (closed vessel 1) In a conventional scroll compressor, ld ^* is about 0.1. On the other hand, in the present invention, practically, the ratio ld ^* between the axial distance (discharge chamber height) ld between the upper lid 2a forming the discharge chamber and the upper surface of the fixed scroll end plate 5a and the chamber inner diameter D is 0.25.
Set to a larger value.

From FIG. 11, it can be seen that the oil separation effect is sharply improved from ld ^* = 0.25. It is preferable that the space of the discharge chamber be relatively deep in view of oil separation.

If the ld dimension is made longer than before, the volume of the discharge chamber 1a also becomes larger. FIG. 12 is an explanatory diagram expressing the size of the volume _VdO of the discharge chamber 1a from the viewpoint of oil separation. The horizontal axis represents the volume V _dO of the discharge chamber as a ratio V _dO ^* shown in the following equation.

V _dO ^* = V _dO / (V _th · N) (2) where, V _dO : volume occupied by the space of the discharge chamber 1 a (cm ³ ) V _th : stroke volume of the compressor (cm ³ / rev) N: Rated rotation speed (Hz) The ratio V _dO ^* of the discharge chamber is practically preferably larger than about 0.15 to 0.2. As described above, it has been experimentally found that the oil separation performance is significantly affected by the height dimension ld of the discharge chamber and the volume of the discharge chamber.

FIG. 13 shows an example relating to means for forming a chamber to which the present invention is applied. Fig. 13 shows the casing body
By changing the axial dimension of the upper lid 2a as L ₂ and L _{3 with} the 2b as a common part, the upper lid 2a and the fixed scroll end plate are changed.
The distance from the upper surface 5a is changed as ld ₁ and ld ₂ . By changing only the upper lid 2a, the joint 2n is at the same position, and it is not necessary to change the assembly jig or the like significantly.

Incidentally, Fig. 14, the casing body portion 2b which forms a closed container a common portion, the axial dimension of the upper cover 2a and a lower cover 2c by changing as _{L 2, L 3, L 4} , L 5 This is an embodiment showing a chamber structure in which the total length of the sealed container is changed according to the capacity of the compressor. The size change of L ₄ and L ₅ is determined by considering the amount of oil stored in the bottom chamber part or the capacity of the compressor or the oil pooling effect of the entire refrigeration cycle (related to the length of refrigerant pipes, etc.). is there. By adopting a chamber configuration in which the length can be changed arbitrarily, there is an advantage that the usability of the compressor for various uses is improved.

FIG. 15 shows an embodiment of the present invention of a scroll compressor having a low-pressure chamber structure. The refrigerant gas sucked from the suction pipe 77 is supplied to the low-pressure chamber 80 having the motor 3 below the frame 11.
And moves to the scroll compression element units 5 and 6. Here, the refrigerant is mixed with a part of the lubricating oil, and is discharged from the discharge port 10 through the discharge chamber 81.
And the refrigerant gas is dispersed in all directions by the action of the gas flow direction changing plate 82, and the oil in the gas is almost separated. The refrigerant gas from which the oil has been separated is guided to the outside via the discharge pipe 78. The separated oil flows from the oil reservoir 72 of the upper chamber 81 to the low-pressure chamber 80.
It enters through the thin tube 73 and returns to the container bottom.

16 to 21 show another embodiment for improving the oil separating action in the discharge chamber. FIG. 17 is a view of the fixed scroll as viewed from above. The embodiment shown in FIG. 16 is a position (several mm) in the vicinity of the central discharge port 10 of the end plate of the fixed scroll.
(A distance between the two), a disk-shaped flat plate 66 is provided. The discharge hole 10 at the center of the fixed scroll has a divergent hole shape so as to significantly reduce the collision speed of the gas with the flat plate. As described above, the gas and the oil that have collided with the flat plate spread in all directions in the radial direction, and forcibly flow to the upper part of the fixed scroll. The relatively heavy oil droplets reach the outer edge 5c of the fixed scroll 5 from the oil reservoir 5l on the upper surface of the fixed scroll through a plurality of passages 5p provided in the bank 5j. On the other hand, the refrigerant gas that spreads in all directions becomes an upward flow so as to pass through between the bank 5j and the flat plate 66, and eventually flows in the circumferential direction along the chamber side wall, thereby forming a communication passage.
18 will be reached. The flat plate 66 has a knock pin 66a.
To the fixed scroll head.

In the embodiment shown in FIG. 18 and FIG. 19 when the fixed scroll is viewed from above, a gas flow path having an opening 62c in a direction opposite to the communication path 18 above the discharge port 10 of the fixed scroll 5 is changed. This is an embodiment in which a body 62 is provided. The height of the change body 62 is also set to a relatively low dimension close to the height of the bank 5j of the fixed scroll 5. This makes it possible to forcibly set the position (height) where the oil flows, as in FIG. 16, to prevent the oil from floating in the discharge chamber. The 19th
As shown in the figure, the number of oil passages 5p provided in the bank portion 5j is set to be larger than that shown in FIG. 17, so that the movement of oil is smoothed. However, the number of oil passages in the bank may be the same as in each of the other embodiments described above, and the number of oil passages in the bank in each of the other embodiments is the same as in FIG. The same number may be used.

FIG. 20 shows that the gas velocity discharged from the discharge hole 10 is
This is an embodiment in which the temperature is lowered by a conical body 61 integrated with the above. The tip of the conical body 61 is located immediately above the discharge hole 10, so that the gas flow can be dispersed in the radial direction and can be spread in all directions. Thus, in FIG.
By setting the angle at which the gas and the gas collide with each other at an angle that is more inclined than the conventional 90-degree direction, the collision effect between the gas and the wall can be reduced.

FIG. 21 shows an embodiment in which the shape of the discharge hole 10 is wider than that of FIG. With this structure, the discharge holes 10
The velocity of the gas discharged from the discharge chamber 1a is greatly reduced, and the velocity of the gas dispersed in the radial direction of the discharge chamber 1a is further reduced. A hole diameter ratio (maximum hole diameter / minimum hole diameter) of the divergent discharge hole 10 provided at the center of the fixed scroll may be around 2.

Each of the above-described embodiments of the present invention has a function of effectively expanding the jet of the mixture of the refrigerant gas and the oil discharged from the discharge port to enhance the performance of separating the oil from the gas. In addition, the separated oil in the discharge chamber and the gas flow in the discharge chamber result in different flow paths and different flow modes.

[Effects of the Invention] The present invention has the following effects.

(1) Since the oil separation performance of the sealed container itself is improved,
Even if the compressor is operated at high speed, it is possible to always secure oil at the bottom of the chamber, and the reliability of the compressor is improved.

(2) Since the compressor has a closed chamber structure capable of reducing the outer diameter, the compressor can be reduced in size and weight when compared with equal capacity (horsepower) of the compressor. It is also advantageous for reducing the cost of the product.

(3) In order to obtain a predetermined height of the discharge chamber, and further to obtain a length of the closed container corresponding to the capacity of the compressor, the body of the closed container is used as a common part, and the depth of the upper lid and the lower portion are further reduced. By adopting a chamber structure in which only the depth of the lid is adjusted, there is an effect that manufacturing costs can be reduced, including improvement in assemblability.

(4) By increasing the space of the discharge chamber and avoiding the collision effect between the upper lid and the gas flow, there is an effect of reducing pressure pulsation in the discharge chamber during high-speed operation and also an effect of reducing noise.

[Brief description of the drawings]

1 is a cross-sectional view showing the entire compressor of one embodiment, FIG. 2 is a plan view of a fixed scroll member as viewed from the wrap side, and FIG. FIG. 4 is a sectional view of the frame, FIG. 4 is a bottom view of the frame, FIG.
The figures are cross-sectional views of main parts of another embodiment and a plan view of a fixed scroll viewed from above. FIGS. 7 and 8 are plan views of a fixed scroll of still another embodiment viewed from above and fixed. FIG. 9 is a cross-sectional view of a scroll, FIG. 9 is a cross-sectional view of a fixed scroll of an embodiment provided with a gas flow direction changing plate with a reed valve, FIG. 10 is an explanatory view of an oil separating operation, FIG. 11 and FIG. Graphs, FIG. 13 and FIG. 14 are diagrams showing the structure of the closed container, FIG.
FIG. 15 is a view showing an embodiment of a scroll compressor having a low-pressure chamber structure, and FIGS. 16 and 17 are cross-sectional views of main parts and a top view of a fixed scroll of still another embodiment, respectively.
FIG. 19 is a cross-sectional view of a main part and a top view of a fixed scroll of still another embodiment. FIGS. 20 and 21 are cross-sectional views of main parts of another different embodiment. DESCRIPTION OF SYMBOLS 1 ... Closed container, 1a ... Discharge chamber 1b ... Electric motor room, 2a ... Upper lid 2b ... Body part, 2c ... Lower lid 5 ... Fixed scroll member 6 ... Revolving scroll member 52, 54, 55, 56 ... Gas flow direction change plate

 ──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Atsushi Amada 390 Muramatsu, Shimizu-shi, Shizuoka Pref. Inside Shimizu Plant of Hitachi Ltd. (56) References JP-A-63-192984 (JP, A) JP-A-59 −192890 (JP, A)

Claims (2)

(57) [Claims] 1. A scroll compressor unit and an electric motor are connected and housed in a closed container via a rotary drive shaft, and a closed container chamber is divided into upper and lower chambers by a frame. The fixed scroll and the orbiting scroll that erect the spiral wrap on the disk-shaped end plate are engaged with the wrap inside, and the fixed scroll is provided with a discharge port that opens at the center and a suction port that opens at the outer periphery, and the orbiting scroll. Is configured to be engaged with an eccentric shaft portion connected to the rotary drive shaft, and by orbiting the orbiting scroll with respect to the fixed scroll without rotating, moving around the compression space formed by both scrolls. The volume is reduced to compress the gas inhaled from the suction port, and the compressed gas is discharged from the discharge port to the discharge chamber of the upper container chamber, through a communication passage communicating the motor chamber and the discharge chamber. In the hermetic scroll compressor, which is guided to the motor chamber of the lower vessel chamber and further discharged outside through a discharge pipe, the axial dimension between the upper lid of the closed vessel forming the discharge chamber and the end plate of the fixed scroll is sealed. The height of the discharge chamber is set so as to be 0.25 times or more of the inner diameter of the chamber formed by the container, and the flow of gas flowing into the discharge chamber from the discharge port at the center of the fixed scroll is directed to the side wall of the discharge chamber. The gas flow direction changing body to be directed is installed on the end plate portion of the fixed scroll so as to face immediately above the discharge port, and the volume Vdo of the discharge chamber is set to about 0.2 or more as a ratio Vdo ^* shown in the following equation. Hermetic scroll compressor. Here, Vdo ^* = Vdo / (Vth · N) Vdo: Volume occupied by the space of the discharge chamber (cm ³ ) Vth: Stroke volume of the compressor (cm ³ / rev) N: Rated speed (Hz) 2. The sealed type according to claim 1, wherein the welded joint (2n) between the upper lid and the casing body is set at a position below the upper end face (5j) of the end plate of the fixed scroll. Scroll compressor.