JPH055485A - Scroll compressor - Google Patents

Abstract

PURPOSE:To form a compressor in a small size, in the shaft through scroll compressor with no overturn moment of tilting a turning scroll. CONSTITUTION:Combination passages 2c, 3c for connecting a central minimum confining chamber to a delivery hole 12, only in a period limited by a position relation at the time of eccentric motion, are formed in an internal peripheral side end plate in a lap winding start part of a fixed scroll 2 and in a lap winding start part of a turning scroll 3. Built-in compression ratio of a compressor is determined by a volute curve of a scroll lap and open timing of the delivery hole. Thus by not increasing a number of volutes, a small size high performance compressor not increasing the diameter, improving work accuracy and decreasing mechanical loss and leakage can be realized.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor used for refrigeration and air conditioning, air compression, etc., and more particularly to a scroll compressor having a reduced number of turns.

[0002]

2. Description of the Related Art A compressor (shaft penetrating scroll compressor) having a structure in which a crankshaft penetrates an orbiting scroll can be found in, for example, Japanese Patent Application Laid-Open No. 57-131896. In the machine, since the height position of the load of the compressed gas acting on the orbiting scroll and the height position of the bearing center become equal, there is an advantage that the moment to tilt the orbiting scroll, that is, the overturning moment does not occur. .. The spiral curve forming the compression chamber is generally an involute curve, and the ratio of the volume of the compression chamber at the start of compression and the volume of the compression chamber at the start of discharge determined by the curve is the intrinsic compression ratio.

[0003]

In such a conventional shaft-through scroll compressor, since the shaft is located at the center of the spiral wrap, it is necessary to start winding the wrap from the outside. Since the volume of the minimum confining chamber formed by the wrap consisting of involute or other curved lines increases toward the outer circumference, the volume of the wrap is increased in the scroll compressor of the present structure in order to ensure a constant specific compression ratio. The number of turns must be increased outwards. Therefore,
Not only is the outer diameter of the scroll larger, but the overall length of the wrap is also longer, so the processing time is longer and the accuracy is lower.

An object of the present invention is to obtain a required specific compression ratio with a wrap having a small number of turns in a scroll compressor of a shaft penetrating type.

[0005]

The above problem is that the intrinsic compression ratio is not determined only by the spiral curve, and after the compression chamber moves to the center, the pressure in the compression chamber, that is, the minimum confinement chamber reaches the discharge pressure. After that, the minimum confining chamber is communicated with the discharge hole only until the discharge is completed. The timing of communication between the discharge hole and the minimum confining chamber is adjusted to the desired timing by providing the fixed scroll with a fixed discharge communication groove and the orbiting scroll with a swirl discharge communication groove and a discharge hole. Are made to have a position and a shape that communicate with each other only at a desired time of the eccentric movement of the orbiting scroll. Further, instead of providing the fixed discharge communication groove in the fixed scroll, a swirl discharge communication passage that connects the swirl discharge communication groove provided in the orbiting scroll and the minimum confining chamber is provided, and the swirl discharge communication groove is provided only at a desired time. It can also be realized by communicating with the discharge hole.

[0006]

[Function] When the compression chamber moves to the center with the eccentric movement of the orbiting scroll, the contact point on the inner peripheral side of the wrap separates and the two compression chambers merge into one, but they do not yet communicate with the discharge hole.
The compression action continues. When the volume of the compression chamber is reduced to a point where the pressure of the compression chamber matches the discharge pressure, that is, when the compression chamber becomes the minimum closed chamber, the compression chamber is provided with the swirl discharge communication groove and the swirl discharge communication passage. Alternatively, it is communicated with the ejection hole through the fixed ejection communication groove. Therefore, it is possible to delay the time when the communication with the discharge hole is made.

[0007]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Several embodiments according to the present invention will be described below with reference to FIG.
~ It demonstrates with reference to FIG. FIG. 1 shows the entire structure of a hermetic scroll compressor which is an embodiment of the present invention.
The hermetic scroll compressor shown in the figure has a cylindrical hermetic container 1 whose both ends are hermetically sealed and whose axial center is substantially vertical, and an axial center in the lower part of the hermetic container 1 coincides with the axial center of the hermetic container 1. And the frame 5 fixed by the fixed scroll 5, the fixed scroll 5 integrally fixed to the frame 5 from above with the wrap facing downward and the shaft center of the fixed frame 5, and the fixed scroll 2 and the frame Between the fixed scroll 2 and the orbiting scroll 3 arranged so as to allow eccentric circular movement of the shaft center with the wrap facing the fixed scroll 2;
An electric motor stator 7a and an electric motor rotor 7b for driving the orbiting scroll 3 which are arranged above the fixed scroll 2 with their axes aligned with each other, and an orbiting bearing for the orbiting scroll 3 fixed to the electric motor rotor 7b. A suction pipe for supplying a compressed gas to a section constituted by a crank shaft 4 which is rotationally driven via 3b, a wrap of a fixed scroll 2 and a wrap of an orbiting scroll 3 which are arranged to penetrate a wall surface of the hermetically sealed container 1. 10 and a discharge pipe 16 arranged so as to penetrate the upper end of the closed container 1.

The crankshaft 4, which is a drive shaft, has a portion 4d fixed to the electric motor rotor 7b and the electric motor rotor 7b.
An upper support shaft 4b which extends downward from a portion 4d fixed to the upper end and is supported by a fixed bearing 2b fixed to the center of the fixed scroll 2 at its lower end, and extends below the upper support shaft 4b and is supported by the orbiting bearing 3b. An eccentric shaft 4a, and a lower support shaft 4c that extends downward from the eccentric shaft 4a and is supported by a frame bearing 5a fixed to the center of the frame 5. Further, the rear surface of the orbiting scroll 3 (the side surface opposite to the end plate wrap, the lower surface in the figure) is in contact with the upper surface of the frame 5 via the seal ring 5b in the vicinity of the eccentric shaft 4a, and the outer peripheral portion of the upper surface of the orbiting scroll 3 is in contact. Is in contact with the lower surface of the end plate of the fixed scroll 2.

The orbiting scroll 3 is constrained by the Oldham's joint 6 so as not to rotate (rotation around the eccentric shaft 4a), and is driven by the rotation of the eccentric shaft 4a to perform an eccentric motion.
A back pressure chamber 17 is provided on the back surface of the orbiting scroll 3 (on the side opposite to the wrap).
A back pressure hole 18 formed in the end plate communicates with the compression chamber 11 having an intermediate pressure between the suction pressure and the discharge pressure. The orbiting scroll 3 is pressed against the fixed scroll 2 by the pressure of the back pressure chamber 17 with an appropriate force, and the tip of the wrap hits the end plate and is sealed. One of the back pressure chambers 17 is sealed by the outer peripheral contact portion of the orbiting scroll 3 and the fixed scroll 2, and the other is sealed by the seal ring 5b. An upper balance weight 8 is attached to the upper support shaft 4b and a lower balance weight 9 is attached to the lower support shaft 4c in order to cancel the centrifugal force of the orbiting scroll 3 and prevent the occurrence of vibrations. There is.

A partition between the wrap of the orbiting scroll 3 and the wrap of the fixed scroll 2 forms a compression chamber 11, and a discharge chamber 13 is provided between the electric motor rotor 7b and the upper surface of the end plate of the fixed scroll 2. I am doing it. The discharge chamber 13 and the compression chamber 11 are connected by a discharge hole 12 formed in the end plate of the fixed scroll 2. Further, an upper container chamber 15 is formed above the electric motor rotor 7b, and a lower container chamber 19 is formed below the frame 5. An oil tank is provided in the lower container chamber 19 and a lubricating oil 20 is stored therein. The discharge chamber 13 and the container upper chamber 15 are communicated with each other by a communication passage 14.

In the compressor having the above structure, the fluid to be compressed,
For example, air is sucked from the suction pipe 10, compressed in the compression chamber 11 and discharged from the discharge hole 12 to the discharge chamber 13, and then discharged from the discharge pipe 16 to the outside of the closed container through the communication passage 14 and the container upper chamber 15. Lubricating oil 20 in the container lower chamber 19 is supplied to the bearings and sliding portions from below the crankshaft 4.

FIG. 2 shows a state in which a part of the wrap 2a of the fixed scroll 2 which constitutes the compression portion of the first embodiment of the present invention is cut away and is looked up from diagonally below, and the orbiting scroll 3 is looked down from diagonally above. State and. On the end plate 3e of the fixed scroll 2, the crankshaft 4 (upper support shaft 4
A fixed bearing 2b for supporting b) and a discharge hole 12 are provided so as to penetrate therethrough. In the discharge process, the compression chamber 11
A fixed discharge communication groove 2c forming a part of a passage communicating with the discharge hole 12 is provided on the lower surface of the end plate of the fixed scroll 2 in a carved form. Wrap 3a of orbiting scroll 3
At the center of the end plate 3e including the central portion, there is provided an orbiting bearing 3b which penetrates and supports an eccentric shaft 4a for eccentrically driving the orbiting scroll 3, and at the tip of the inner peripheral side wrap, from the compression chamber 11 in the discharging process. A swirl discharge communication groove 3c forming a part of a passage leading to the discharge hole 12 is provided so as to penetrate the lap 3a in the height direction. The discharge hole 12 and the orbiting discharge communication groove 3c are formed at a position where the fixed scroll 2 and the orbiting scroll 3 are always assembled and operated while the orbiting scroll 3 is in any position.

3 and 4 show a fixed scroll wrap 2a and an orbiting scroll wrap 3 common to the embodiments of the present invention.
The shape of a is shown.

The involute angle of the outer winding start 2aa of the fixed scroll wrap 2a is λfo, and the involute angle of the inner winding start 2ab of the fixed scroll wrap 2a is λf.
Letting i be the involute angle of the outer winding start 3aa of the orbiting scroll wrap 3a be λmo, and the involute angle of the inner winding start 3ab of the orbiting scroll wrap 3a be λmi, the following relationships exist between these involute angles.

[Lambda] fo = [lambda] fi = [lambda] mo + [pi] = [lambda] mi- [pi] The winding start 2aa and 2ab are connected by a circular arc 2ac, and the winding start 3aa and 3ab are connected by a circular arc 3ac. Arc 2ac of the winding start end of the wrap 2a of the fixed scroll 2
And the arc 3 at the winding start end of the wrap 3a of the orbiting scroll 3.
In the compression process, ac closely seals while the orbiting scroll 3 makes a half turn.

FIG. 5 is a stroke diagram showing the discharge stroke of the first embodiment of the present invention. In this embodiment, the natural compression ratio is determined by allowing the swirl discharge communication groove 3c and the fixed discharge communication groove 2c to communicate with each other for a limited period of time.

The orbiting scroll wrap 3a is driven by the crankshaft 4 and its axis (center of the orbiting bearing 3b) orbits counterclockwise around the axis of the fixed scroll wrap 2 (center of the fixed bearing 2b). However, at that time, the orbiting scroll wrap 3a does not rotate with respect to the fixed scroll wrap 2a. In FIG. 6, the air sucked into the region R1 is confined in the region R2 at and moves to the region R3 at. The air in the region R3 moves to the region R4 at, the region R5 at the stroke of, the region R6 at the stroke of, and the region of the compression chamber 11a 'at the stroke of. When the eccentric movement of the orbiting scroll 3 progresses and returns again, the air in the region of the compression chamber 11a 'moves to the region of the compression chamber 11a in the central portion.
The area of the compression chamber 11a at the center is always the fixed discharge communication groove 2
However, in this process, the fixed discharge communication groove 2c
Is closed by the orbiting scroll wrap 3a and is not connected to the orbiting discharge communication groove 3c.

When the eccentric movement further reaches the stroke, the central compression chamber 11a reaches the discharge volume set so as to maintain a predetermined specific compression ratio. This state is the moment when the swirl discharge communication groove 3c communicates with the fixed discharge communication groove 2c which always communicates with the central compression chamber 11a, and the compression chamber 11a at this time is referred to as the minimum confining chamber. Immediately after this, the compression chamber 11a communicates with the discharge hole 12 through the fixed discharge communication groove 2c and the swirl discharge communication groove 3c, and discharge is started. In the next stroke, the swirl discharge communication groove 3c communicates with the fixed discharge communication groove 2c, and discharge is being performed. In the figure, the volume of the compression chamber 11a in the central portion becomes 0, and the end of discharge and the moment when the communication between the swirl discharge communication groove 3c and the fixed discharge communication groove 2c is broken are shown. After this, one compression chamber 11a 'on the outside
Area becomes the state of communicating with the fixed communication groove 2c,
Since the communication between the swirl discharge communication groove 3c and the fixed discharge communication groove 2c is cut off, the compression chamber 11a maintains a hermetically closed state and discharge is not performed. When the compression further progresses and the state becomes again, the ejection is started again.

According to this embodiment, the discharge hole 12 penetrating the end plate 2e of the fixed scroll in the thickness direction on the inner peripheral side of the winding start position of the fixed scroll wrap 2a and the winding start position of the orbiting scroll wrap 3a. It penetrates the orbiting scroll wrap 3a in the height direction, and the discharge hole 1 is always provided.
The swirl discharge communication groove 3c communicating with the swirl scroll 3 and the swirl scroll 3 formed in a groove shape on the surface of the end plate 2e of the fixed scroll facing the swivel scroll on the inner peripheral side of the winding start position of the fixed scroll wrap 2a. Since the fixed discharge communication groove 2c communicating with the swirl discharge communication groove 3c is provided in the eccentric position range, the minimum confining chamber can be brought closer to the axial center, and a predetermined specific compression ratio and discharge amount can be obtained. It was possible to suppress an increase in the size of the compressor required for this. Further, since the number of windings of the wrap, that is, the length or diameter of the wrap is prevented from increasing with respect to a predetermined specific compression ratio and discharge amount, it is possible to improve the processing accuracy.
The effects such as reduction of contact surface pressure and reduction of leakage were obtained.

FIG. 6 is a stroke diagram showing the shape of the discharge communication groove and the discharge stroke of the second embodiment of the present invention. In the first embodiment described above, the discharge timing and the specific compression ratio of the compressed air depend on the presence / absence of communication between the swirl discharge communication groove 3c and the fixed discharge communication groove 2c, but in this embodiment, the swirl discharge communication groove 3c. The inherent compression ratio is determined by communicating the discharge hole 12 with the discharge hole 12 for a limited period of time. The orbiting scroll wrap 3a eccentrically moves counterclockwise, and
1a is a state in which the discharge volume set as the specific compression ratio has been reached. The fixed discharge communication groove 2c is always in the central compression chamber 1
1a, and the swirl discharge communication groove 3c is the moment when communication with the discharge hole 12 is started while communicating with the fixed discharge communication groove 2c. Immediately after this, the compression chamber 11a communicates with the discharge hole 12 and discharge is started. The swirl discharge communication groove 3c communicates with the fixed discharge communication groove 2c and the discharge hole 12, and discharge is in progress. Indicates that the volume of the central compression chamber 11a becomes 0 and the discharge is completed. It is the moment when the communication between the swirl discharge communication groove 3c and the discharge hole 12 is cut off. After this, the compression chamber 11a 'on the outer side communicates with the fixed discharge communication groove 2c,
However, since the communication between the swirl discharge communication groove 3c and the discharge hole 12 is cut off, the compression chamber 11a 'is kept in a hermetically closed state, and discharge is not performed. The compression further progresses, and the discharge is started again at the moment when the state again passes.

FIG. 7 shows a third embodiment of the present invention. The illustrated compression stroke is in the state of FIG. 6 of the second embodiment, and is discharging. The difference between the second embodiment and this embodiment is that this embodiment does not have a fixed discharge communication groove 2c, but instead has a swirl discharge communication passage 3d.
The communication passage 3d is not exposed on the lap end surface, is provided in the wrap, and always communicates with the central compression chamber 11a and the swirl discharge communication groove 3c. As in the second embodiment, the swirl discharge communication groove 3c and the discharge hole 12 are communicated with each other for a limited period of time, and the specific compression ratio is determined.

In the second and third embodiments, the same effect as that of the first embodiment was obtained.

FIG. 8 is a stroke diagram showing the lap shape and the compression stroke of the fourth embodiment of the present invention. In this embodiment, the shapes and positions of the discharge communication groove and the discharge hole in the discharge stroke are the same as in the first embodiment, but the fixed scroll wrap 2a and the orbiting scroll wrap 3a have different outer peripheral winding end positions. That is, the fixed scroll wrap 2a is wound more outward than the orbiting scroll wrap 3a. Therefore, the compression start timing differs between the orbiting scroll wrap outside line side compression start compression chamber 11so and the orbiting scroll wrap inside line side compression start compression chamber 11si. Is the compression start compression chamber 11so of the outer side of the orbiting scroll wrap 3a.
Is terminating inhalation and starting compression. The volume at this time is Vso. When the rotation is advanced, the extension side compression start compression chamber 11s of the orbiting scroll wrap 3a is started.
i finishes inhalation and begins compression. The volume at this time is V
Let si. After this, when one rotation is made and the rotation further advances, the compression chambers become 11ao and 11ai. Immediately after that, both compression chambers lose their central seals and join together. The volume of 11ao is Vao, and the volume of 11ai is Vai. Since Vai is smaller than Vao, if the two compression chambers have the same volume at the start of compression as in the first to third embodiments, the pressure in the compression chamber 11ai becomes higher than the pressure in 11ao, and at the time of merging. One causes excessive compression, and the other causes insufficient compression, resulting in power loss. In this embodiment, the number of windings of the wrap is set so that each of the volumes satisfies the relationship of the following equation.

[0024]

[Equation 2]

Since the pressure is set in this way, according to this embodiment, the pressures of both compression chambers at the time of merging are the same, and the power loss generated is reduced.

FIG. 9 shows a fifth embodiment of the present invention. This embodiment relates to an oil supply structure for a shaft and a bearing portion, and is the same as the first embodiment except for the particularly mentioned portions. The crankshaft 4 has an upper support shaft 4b supported by a fixed bearing 2b, a lower support shaft 4c supported by a frame bearing 5a, and an orbiting bearing 3b fitted to the eccentric shaft 4a to drive the orbiting scroll 3 eccentrically. An oil supply passage 21 is provided inside the crankshaft 4. The oil supply passage 21 opens at the center of the lower end of the lower support shaft 4c and is eccentric to the outer peripheral side in the upper part. The lower end of the lower support shaft 4c is immersed in the lubricating oil 20. An oil supply hole 22 opens from the oil supply passage toward the fixed bearing 2b, which is the uppermost bearing, and oil is supplied to the bearing by centrifugal action due to rotation of the shaft. Upper support shaft 4b, eccentric shaft 4 from the oil supply hole
a, a continuous oil supply groove 23 is provided spirally on the shaft surface through the lower support shaft 4c, and extends to the lower end of the frame bearing 5a. The oil discharged to the oil supply hole 22 is also supplied to the slewing bearing 3b and the frame bearing 5a through the oil supply groove and is discharged downward. During this time, a seal ring 5b is provided between the back pressure chamber 17 and the back pressure chamber 17.
Is interposed so that oil does not flow into the back pressure chamber 17. A discharge oil guide 24 is provided below the frame bearing 5a, and the oil that has flowed out travels on the discharge oil guide and falls into the oil tank. The oil mixed with the gas and discharged to the discharge chamber 13 travels along the upper surface of the fixed scroll 2 and falls from the drop passage 25 into the oil tank. Also in this embodiment, any of the lap shapes and the discharge passage structure described in the first to fourth embodiments can be used.

According to this embodiment, since the oil is not agitated by the scroll, the balance weight, etc., unnecessary power is not consumed and the performance of the compressor can be improved. Also, since the oil does not flow into the back pressure chamber, the discharged gas contains almost no oil. The amount of oil discharged to the outside of the compressor can be extremely reduced.

FIG. 10 shows a sixth embodiment in which the positional relationship between the compression section and the electric motor section is changed. In this embodiment, a compression part is arranged in the upper part of the closed container 1, and electric motor parts 7a and 7b are arranged in the lower part. The compression part is arranged in the order of the frame 5, the Oldham's joint 6, the orbiting scroll 3, and the fixed scroll 2 from the top. That is, the electric motor parts 7a and 7b of the fifth embodiment, the frame 5, the Oldham coupling 6, the orbiting scroll 3, and the fixed scroll 2 are arranged in a vertically reversed arrangement.
Other points are the same as in the fifth embodiment. The gas sucked from the suction pipe 10 is discharged downward from the discharge hole 12 to the discharge chamber 13
Is discharged to the upper chamber 15 of the container through the communication passage 14 and discharged from the discharge pipe 16 to the outside of the compressor. According to the present embodiment, the compressed gas is once discharged downward and is turned up and guided upward, so that a better oil separation is performed.

FIG. 11 shows a seventh embodiment in which the positional relationship of the compression section is further changed. The sixth embodiment is different from the sixth embodiment in that the compression portion is arranged in the order of the fixed scroll 2, the orbiting scroll 3, the Oldham's joint 6 and the frame 5 from the top, and the others are the sixth embodiment. The description is omitted because it is similar to the example. In this embodiment, the discharge hole 1
The gas discharged from 2 to the container upper chamber 15 is discharged as it is from the discharge pipe 16 to the outside of the compressor. According to this embodiment, since the gas passage from the suction pipe to the discharge pipe is shortest, the heat exchange between the high-temperature discharge gas and the low-temperature suction gas can be minimized, the overheating of the suction gas is reduced, and the higher temperature is achieved. Efficiency is obtained.

Also in the sixth and seventh embodiments, any of the lap shapes and discharge passage structures described in the first to fourth embodiments can be used.

[0031]

According to the present invention, the increase in the number of spirals, that is, the increase in the number of spirals, which is the drawback of the shaft-through scroll compressor in which the crankshaft penetrates the orbiting scroll, is eliminated, the diameter is small, and the machining accuracy is high. Since it can be a high scroll wrap, there is no overturning moment, and in addition to reduction of mechanical loss due to reduction of bearing load and sliding surface pressure, there is little leakage and a compact and high-performance scroll compressor is realized. can do.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a scroll compressor that is a first embodiment of the present invention.

FIG. 2 is a perspective view showing the shapes of a wrap and a discharge passage of the fixed scroll and the orbiting scroll of the first embodiment.

FIG. 3 is a cross-sectional view showing a position shape of a wrap winding start of a fixed scroll common to all the examples.

FIG. 4 is a cross-sectional view showing a position shape of a wrap winding start of an orbiting scroll common to all the embodiments.

FIG. 5 is a stroke diagram showing a planar passage shape, a compression stroke, and a discharge stroke of the fixed scroll, the discharge hole of the orbiting scroll, the orbiting discharge communication passage, and the fixed discharge communication passage of the first embodiment.

FIG. 6 is a stroke diagram showing a flat passage shape, a compression stroke, and a discharge stroke of a discharge hole, a swirl discharge communication passage, and a fixed discharge communication passage of a fixed scroll and an orbiting scroll of a second embodiment.

FIG. 7 is a cross-sectional view showing the planar passage shapes of the fixed scroll, the discharge hole of the orbiting scroll, the orbiting discharge communication passage, and the fixed discharge communication passage of the third embodiment.

FIG. 8 is a stroke diagram showing a planar passage shape and a compression and discharge stroke of a discharge hole, an orbiting discharge communication passage, and a fixed discharge communication passage of a fixed scroll and an orbiting scroll of a fourth embodiment.

FIG. 9 is a vertical sectional view of a compressor showing an oil supply structure for a shaft and a bearing according to a fifth embodiment.

FIG. 10 is a vertical sectional view of a compressor showing a sixth embodiment.

FIG. 11 is a vertical sectional view of a compressor showing a seventh embodiment.

[Explanation of symbols]

1 Sealed Container 2 Fixed Scroll 2a Fixed Scroll Wrap 2b Fixed Bearing 2c Fixed Discharge Communication Groove 2e Fixed Scroll End Plate 3 Orbiting Scroll 3a Orbiting Scroll Wrap 3b Orbiting Bearing 3c Orbiting Discharge Communication Groove 3d Orbiting Discharge Communication Channel 3e Orbiting Scroll End Plate 4 Crank Shaft 4a Eccentric shaft 4b Upper support shaft 4c Lower support shaft 5 Frame 5a Frame bearing 5b Seal ring 6 Oldham joint 7 Electric motor 7a Electric motor stator 7b Electric motor rotor 8 Upper balance weight 9 Lower balance weight 10 Suction pipe 11 Compression chamber 11a Central compression Chamber 11ao Orbiting scroll wrap outside line central merging start compression chamber 11ai Orbiting scroll wrap inside line Central merging start compression chamber 11so Orbiting scroll wrap outside line compression starting compression chamber 11si Orbiting scroll wrap inside line compression opening The compression chamber 12 discharge holes 13 discharge chamber 14 communicating path 15 upper container chamber 16 discharge pipe 17 back pressure chamber 18 back pressure hole 19 container lower chamber 20 lubricating oil 21 oil passage 22 the oil supply hole 23 oil groove 24 oil discharge guide 25 falling passage

Claims (1)

Claim: What is claimed is: 1. An orbiting scroll member and a fixed scroll member, wherein a fixed scroll member having an end plate in which a spiral wrap is upright and an orbiting scroll member are eccentric to each other and the wraps are made eccentric. Is formed in the vicinity of the center of the combined orbiting scroll member and fixed scroll member by driving the orbiting scroll member eccentrically without rotating with respect to the fixed scroll member to compress the gas. In a scroll compressor that discharges compressed gas from a minimum enclosed chamber through a discharge hole provided in a fixed scroll member, a communication groove and a discharge hole provided in the fixed scroll member and the orbiting scroll member are provided. Minimum confinement formed near the center by combining the provided communication grooves There in one rotation of the drive shaft, through the discharge hole and communicating with a limited rotational angle range, a scroll compressor, wherein a communication between the discharge port is blocked in rotation angle range other than the. 2. The timing of communication and disconnection between the minimum confining chamber formed near the center and the discharge hole depends on the shape and relative positional relationship of the communication groove provided in the fixed scroll and the communication groove provided in the orbiting scroll. The scroll compressor according to claim 1, wherein the scroll compressor is defined. 3. The shape and relative positional relationship between the discharge hole provided in the fixed scroll and the communication groove provided in the orbiting scroll are determined with respect to the timing of communication between the discharge hole and the minimum confining chamber formed near the center. The scroll compressor according to claim 1, wherein: 4. A fixed scroll member in which a spiral wrap is upright on an end plate and an orbiting scroll member are combined so as to be eccentric and eccentric to each other, and are provided through the orbiting scroll member and the fixed scroll member. A drive shaft is provided in the fixed scroll member from a minimum enclosed chamber formed near the center of the combined orbiting scroll member and fixed scroll member by causing the orbiting scroll member to eccentrically move without rotating and compressing gas. In a scroll compressor that discharges compressed gas through the discharge hole, the discharge hole provided in the fixed scroll member and the communication groove and the communication path provided in the orbiting scroll member are combined to form near the center. The minimum enclosed chamber is ejected in a limited rotation angle range during one rotation of the drive shaft. A scroll compressor, which communicates with a discharge hole and blocks communication with a discharge hole in a rotation angle range other than the above. 5. The timing of communication and interruption of the minimum confining chamber formed near the center and the discharge hole depends on the shape and relative positional relationship between the discharge hole provided in the fixed scroll and the communication groove provided in the orbiting scroll. The scroll compressor according to claim 4, wherein the scroll compressor is fixed. 6. A portion of the scroll wrap that has a compression action is constituted by an involute curve. 1) The winding start involute angle of the outer line of the orbiting scroll wrap 3a is λmo, and 2) the winding start involute of the extension line of the orbiting scroll wrap 3a. Where 3) is the winding start involute angle of the outer line of the fixed scroll wrap 2a is λfo, and 4) is the winding start involute angle of the inner line of the fixed scroll wrap 2a is λfi, the relative winding start angle of the involute curve is 6. The scroll compressor according to any one of claims 1 to 5, wherein the different positions have a relationship of λfo = λfi = λmo + π = λmi−π. 7. The volume at the start of compression of the compression chamber formed on the outer line side of the orbiting scroll is Vso, and the volume at the moment when the gas trapped in the compression chamber merges with the gas in the compression chamber on the inner line side at the central portion is Vao. When the volume at the start of compression of the compression chamber formed on the extension side of the orbiting scroll is Vsi and the volume at the moment when the gas trapped in the compression chamber merges with the gas in the compression chamber on the outside line at the central portion is Vai , And between these roughly [Equation 1] The scroll compressor according to any one of claims 1 to 6, characterized in that 8. An oil supply passage which is formed in the drive shaft and reaches the uppermost bearing position from the center of the lower end of the shaft, and an oil supply hole which is opened from the oil supply passage to the outer surface of the drive shaft facing the uppermost bearing. The scroll compressor according to any one of claims 1 to 7, wherein a hole and an oil supply groove spirally formed downward from the oil supply hole are provided on an outer surface of the drive shaft. 9. An electric motor unit is arranged on the upper part, a compression unit is arranged on the lower part, a fixed scroll 2 is arranged on the compression unit and an orbiting scroll 3 is arranged on the lower part, and a discharge hole 12 is opened on the upper surface of the fixed scroll 2. Compressed gas is discharged to the lower space of an electric motor part, The scroll compressor in any one of Claims 1-7 characterized by the above-mentioned. 10. A compression part is arranged on the upper part, an electric motor part is arranged on the lower part, an orbiting scroll 3 is arranged on the compression part, and a fixed scroll 2 is arranged on the lower part. Compressed gas is discharged to the upper space of an electric motor part, The scroll compressor in any one of Claims 1-7 characterized by the above-mentioned. 11. A compression part is arranged on the upper part, an electric motor part is arranged on the lower part, a fixed scroll 2 is arranged on the compression part, and an orbiting scroll 3 is arranged on the lower part, from a discharge hole 12 opening on the upper surface of the fixed scroll 2. Compressed gas is discharged to the upper space of the airtight container 1, The scroll compressor in any one of Claims 1-7 characterized by the above-mentioned. 12. A fixed scroll member in which a spiral wrap is upright on an end plate and an orbiting scroll member are combined so as to be eccentric and eccentric to each other, and are provided so as to penetrate the orbiting scroll member and the fixed scroll member. The drive shaft causes the orbiting scroll member to eccentrically move without rotating with respect to the fixed scroll member to compress the gas, and a minimum enclosed chamber formed near the center of the combined orbiting scroll member and fixed scroll member. In a scroll compressor that discharges compressed gas from a fixed scroll member through a discharge hole provided in the fixed scroll member, a fixed discharge communication groove that is provided in the fixed scroll member and communicates with the minimum closed chamber, and the orbiting scroll member. And a swirl discharge communication groove for communicating the fixed discharge communication groove with the discharge hole. The discharge hole, the fixed discharge communication groove, and the swirl discharge communication groove communicate with the discharge hole in a limited rotation angle range during one rotation of the drive shaft, and the rotation angle range other than the above is included. Then, the scroll compressor is characterized in that it has a position and a shape that block communication with the discharge hole. 13. The fixed discharge communication groove is formed in a groove shape on the fixed scroll end plate surface in contact with the inner diameter side of the center side winding start end of the fixed scroll wrap, and the orbiting discharge communication groove of the orbiting scroll. The scroll compressor according to claim 12, wherein the shaft penetrating portion and the orbiting scroll wrap are connected to each other at a connecting portion so as to penetrate the wrap in a height direction. 14. A fixed scroll member in which a spiral wrap is upright on an end plate and a revolving scroll member are combined so as to be eccentric and eccentric to each other, and are provided so as to penetrate the revolving scroll member and the fixed scroll member. The drive shaft causes the orbiting scroll member to eccentrically move without rotating with respect to the fixed scroll member to compress gas, and a minimum enclosed chamber formed near the center of the combined orbiting scroll member and fixed scroll member. In a scroll compressor for discharging compressed gas from a fixed scroll member through a discharge hole provided in the fixed scroll member, a swirl discharge communication groove provided in the swivel scroll member and communicating with the discharge hole, and a swirl discharge communication groove provided in the swirl scroll member as well. And a swirl discharge communication passage communicating the minimum closed chamber with the swirl discharge communication groove. The discharge hole and the swirl discharge communication groove communicate with the discharge hole in a limited rotation angle range during one rotation of the drive shaft, and the discharge hole and the swirl discharge communication groove communicate with the discharge hole in a rotation angle range other than the above. A scroll compressor having a position and a shape that cut off communication.