JP2001200795A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve compression efficiency and stabilize an operating condition by suitably making a scroll compressor properly correspond to excessive compression in a pair of compression chambers, where closing capacity is different from each other. SOLUTION: Delivery bypass ports 5, 6 are disposed in a pair of compression chambers 3, 4, where closing capacity is different from each other, and a passage cross sectional area of the delivery bypass port 5 formed in one compression chamber 3 disposed on the side having the large closing capacity, is formed larger than a passage cross sectional area of the delivery bypass port 6, formed in the other compression chamber 4 disposed on the side having the small closing capacity.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor mainly used for refrigeration and air conditioning for business use and home use.

[0002]

2. Description of the Related Art As an electric compressor for refrigeration and air conditioning, a scroll type compressor has been put to practical use by utilizing the features of high efficiency, low noise and low vibration. In the scroll compressor, as shown in FIG. 9, a pair of compression chambers a1 and a2 are formed between a fixed scroll c and a orbiting scroll d that moves in a circular orbit. During actual operation, the refrigerant in each of the compression chambers a1 and a2 may be in an over-compressed state at a predetermined pressure or more. For efficient and proper operation in the set mode, overcompression is performed by early discharge of overcompressed refrigerant through bypass ports b1, b2 opened at a predetermined position in the pair of compression chambers a1, a2, that is, near the final compression position. The problem is solved by performing ejection.

Each of the bypass ports b1 and b2 is
As shown in FIGS. 10A to 10D, the compression chambers a1 and a2 move from the outer periphery to the center as the orbital angle of the orbiting scroll d increases, and the volume of the compression operation is reduced. Accordingly, it is necessary to open only the corresponding one of the compression chambers a1 and a2. Therefore, the size thereof is required to be smaller than the thickness of the basic blade d1 of the orbiting scroll d. Therefore, conventionally, the passage cross-sectional area required for instantaneously discharging the over-compressed refrigerant is made to satisfy the condition by providing a plurality of bypass ports b1 and b2 as shown in FIG.

[0004]

However, in diversifying the operation modes, it is important that the scroll compressor is operated at a variable speed by inverter control or the like so that an optimum operation state can be obtained at each time. Is coming.

In order to cope with the over-compression state in a pair of compression chambers in such a scroll compressor, it is appropriate to provide a bypass port under the same condition in both of the pair of compression chambers as in the related art. There is no problem.

An object of the present invention is to provide a scroll compressor which can appropriately cope with an over-compression state in a pair of compression chambers.

[0007]

In order to achieve the above object, in a scroll compressor according to the present invention, a fixed scroll in which a spiral basic blade rises on a head plate and a spiral scroll in which a spiral basic blade rises on a head plate. In a scroll compressor in which a pair of closed chambers having different closed volumes are formed between both by engaging the orbiting scroll, a discharge bypass port is provided for each of the pair of compressed chambers having different closed volumes, The passage cross-sectional area of the discharge bypass port formed in one of the compression chambers on the side of the larger closed volume is different from the passage cross-sectional area of the discharge bypass port formed in the other compression chamber on the side of the smaller closed volume. It is characterized in that it is increased corresponding to the confined volume.

In such a configuration, in a pair of compression chambers having different closed volumes, the passage cross-sectional area of the discharge bypass port is formed so as to correspond to the different volumes. In accordance with the volume, an early discharge of the over-compressed fluid is achieved through an early-discharge path such as a bypass port, so that the early discharge of the over-compressed fluid in the pair of compression chambers is almost uniformly achieved without excess or shortage. The compression efficiency is improved and the operation state is more stable. In addition, when equalization of the overcompression prevention in such a pair of compression chambers having different closed volumes is achieved, the bypass ports of the pair of compression chambers having different closed volumes have substantially the same pressure or more. At the same time, the openings are opened almost simultaneously, the compression efficiency is further improved, and when the same over-compression state occurs in both of the pair of compression chambers, they work almost simultaneously, so that the number of noise occurrences is reduced by half. become.

In the present invention, the discharge bypass ports respectively formed in the pair of compression chambers having different closed volumes have a plurality of small holes having a diameter smaller than the thickness of the basic blade adjacent to each other. The sum of the opening areas of the plurality of small holes is defined as the passage sectional area of the discharge bypass port.

In such a configuration, by forming a plurality of small holes, the sum of the opening areas of the plurality of small holes can be used as the passage sectional area of the discharge bypass port.

Further, according to the present invention, the discharge bypass port formed in each of the pair of compression chambers having different closed volumes has a plurality of small holes having a diameter smaller than the basic blade thickness and having substantially the same diameter. The number of small holes of the discharge bypass port formed adjacently and formed in one compression chamber on the side with the larger closed volume is changed to the number of holes of the discharge bypass port formed in the other compression chamber on the side with the smaller closed volume. It is characterized by having more than the number of small holes.

In this configuration, the passage cross-sectional area of the discharge bypass port can be simply formed appropriately corresponding to the volume of the compression chamber having a pair of closed volumes different from each other by the number of small holes of the discharge bypass port. Can be.

In the present invention, each of the discharge bypass ports formed in the pair of compression chambers having different closed volumes has a plurality of small holes having a diameter smaller than the basic blade thickness. Further, a valve is provided for opening and closing each discharge bypass port formed by the plurality of small holes.

In such a configuration, each of the discharge bypass ports formed by the plurality of small holes can be opened and closed by the valve.

Further, in the present invention, a counterbore covering each of a plurality of adjacent small holes is formed on the side opposite to the basic blade of the fixed scroll head plate, and the counterbore is used as a valve seat to be opened and closed by the valve. It is characterized by doing so.

In such a configuration, a counterbore that includes a plurality of small holes as bypass ports of a pair of compression chambers having different closing volumes is used as a valve seat of the valve.
Accordingly, the plurality of small holes can be opened and closed in a comprehensive manner, and the resistance of the early discharge of the over-compressed refrigerant is reduced, so that the compression efficiency is improved.

Further, according to the present invention, a ring-shaped ridge covering a plurality of adjacent small holes is provided on a side of the fixed scroll end plate opposite to the basic blade, and the ring-shaped ridge is used as a valve seat to provide the valve. To open and close.

Also in this configuration, instead of the formation of the counterbore, a ring-shaped ridge that covers each of a plurality of adjacent small holes is formed. The opening / closing operation of the valve can be performed by covering each of the small holes, and the compression efficiency is improved by reducing the resistance of the early discharge of the over-compressed refrigerant.

Further, according to the present invention, a counterbore is formed in a small hole closest to a suction side among a plurality of adjacent small holes on a side opposite to the basic blade of the fixed scroll head plate, and the small counterbore formed with the counterbore is formed. A plurality of adjacent small holes including holes are opened and closed by the valve.

In such a configuration, a counterbore is provided in each of the bypass ports closest to the suction side among the plurality of adjacent small holes. With regard to the above, the discharge resistance is reduced by the counterbore, and the early discharge of the over-compressed refrigerant is performed smoothly.

Further objects and features of the present invention will become apparent from the following description and drawings. Each feature of the present invention can be used alone or in combination in various combinations as needed.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The embodiment of the present invention is an example in which a horizontally mounted closed-type scroll compressor for refrigeration and air conditioning is used. Therefore, the fluid to be handled is a refrigerant. However, the present invention is not limited to this, and includes cases where it is used for applications other than refrigeration and air conditioning, and the direction of installation and whether or not it is sealed can be freely selected.

The scroll compressor according to the present embodiment shown in FIG. 8 is composed of a fixed scroll 1 in which spiral basic blades rise up on a head plate, and an orbiting scroll 2 in which spiral basic blades rise up on a head plate. An electric motor 21 for orbiting the orbiting scroll 2 by a scroll type compression mechanism 20
Together with the inside of the closed container 22 to form a maintenance-free scroll compressor. The electric motor 21 has a stator 21a fixed in an airtight container 22 by shrink fitting or the like, and a main shaft 23 of a crankshaft 23 directly connected to a rotor 21b.
The orbiting scroll 2 is caused to make a circular orbital motion with respect to the fixed scroll 1 through the passive portion 2c of the orbiting scroll 2 fitted with the eccentric portion 23b which is an eccentric shaft or hole provided in the compression chambers 3 and 4, and the compression chambers 3 and 4 are moved. When it is at the outer peripheral portion, it absorbs the refrigerant through the suction port 24 at the outer peripheral portion of the fixed scroll 1 and compresses the trapped refrigerant by reducing the volume of the refrigerant, thereby discharging the refrigerant at the substantially central position of the fixed scroll 1. Discharge to outlet 25. The discharge port 25 is also provided with a reed valve 26, and the opening position is regulated by the stopper 15.

The crankshaft 23 has a main shaft 23a and a sub shaft 23c opposite to the main shaft 23a, which are attached in close contact with each other by baking or the like in a closed container 22, and the main bearing member 31 and the sub bearing The fixed scroll 1 is fixed to the main bearing member 31 by bolts 35, and is rotated between the main bearing member 31 and the orbiting scroll 2 when the orbiting scroll 2 is driven to rotate. An Oldham ring 37 as an example of a rotation preventing mechanism for preventing the orbiting from moving in a circular orbit is operated, and the orbiting scroll 2 is sandwiched between the fixed scroll 1 and the main bearing member 31 to be formed on the back of the orbiting scroll 2. The orbiting scroll 2 is pressed toward the fixed scroll 1 by the back pressure guided to the back pressure chamber 50 and the pressure of the compressed refrigerant. Times scroll 2 is fixed scroll 1
So that the suction, compression and discharge operations of the refrigerant are reliably performed.

The refrigerant discharged from the compression mechanism 20 is discharged into a muffler 38 provided on the back surface of the fixed scroll 1 to prevent vibration and noise generated when the refrigerant is directly discharged into the sealed container 22. Cool it by passing it through the portion of the electric motor 21 in the closed container 22 and then
It is supplied to the refrigeration cycle through the discharge pipe 41 to the outside. The used refrigerant returned from the refrigeration cycle is
Is sucked into the suction port 24 through the suction pipe 42 and compressed again.

The lower part of the closed container 22 is an oil reservoir 44 for storing an oil 43. Oil 43 in oil sump 44
Is an oil pump 45 driven by the crankshaft 23
After suction through the suction pipe 46, the crankshaft 2
A high pressure is discharged to an oil supply passage 23d vertically passing through the inside of the cylinder 3, and the oil is supplied to each sliding portion of the compression mechanism 20. A part of the oil supply passage 23d communicates with the back pressure chamber 50 via a throttle 47 so that a stable oil pressure due to the throttle action of the throttle 47 acts as the back pressure. A back pressure control mechanism which opens when the back pressure is equal to or higher than a predetermined pressure and escapes to the suction chamber 48 in the middle of a communication path 49 communicating from the back pressure chamber 50 to the suction chamber 48 having the suction port 24 through the fixed scroll 1. 51 is provided to prevent the back pressure from fluctuating due to the operation state. While the basic blade 1a of the fixed scroll 1 is provided with two turns and a length of 3/4,
The basic blades 2a of the orbiting scroll 2 are provided with two circumferences and a length of 1/4, and one of the volumes of the suction closing portions in the pair of compression chambers 3, 4 formed by the basic blades 1a, 2a is larger than the other. Are also made smaller.

The basic blades 1a and 2a have a spiral length that satisfies a prescribed volume ratio during low-speed operation. The suction closing of a pair of compression chambers 3 and 4 formed by the basic blades 1a and 2a. One of the capacities is smaller than the other, and the basic blades 2a of the orbiting scroll 2 forming the compression chamber 4 having a small volume are provided with extended blades 2b extending further from the winding end position along the spiral shape. ,
Displacement surfaces 1b displaced in the direction of decreasing the thickness are formed on the inner wall of the extension blade 2b and the outer wall of the basic blade 1a of the fixed scroll 1 facing the extension blade 2b.

The extended blade 2b may be formed on the side of the basic blade 1a of the fixed scroll 1. In this configuration, the extended blade 2b is displaced on the outer wall of the basic blade 2a of the orbiting scroll 2 opposed thereto in the direction of decreasing the thickness. Is formed.

As described above, in order to make one of the volumes of the suction closing portions smaller than the other in the pair of compression chambers 3 and 4 formed by the fixed scroll 1 and the orbiting scroll 2, It is formed by reducing the angle of the winding end point of the basic blade 1a.

Since one of the volumes of the suction closing portions in the pair of compression chambers 3 and 4 formed by the basic blades 1a and 1b is smaller than the other, the outer diameter of the scroll compressor is reduced accordingly. As a result, it is possible to operate at a speed higher than the reference operation speed, and it is also possible to reduce the leakage loss of the refrigerant, thereby realizing high efficiency. A pair of compression chambers 3 and 4 having different closed volumes formed between the fixed scroll 1 and the orbiting scroll 2 that moves in a circular orbit are provided with bypass ports 5 and 6 that open when the pressure is equal to or higher than a predetermined pressure. Through the bypass ports 5 and 6, the compressed fluid is discharged at an early stage.

In this embodiment shown in FIGS. 1 to 7, discharge bypass ports 5 and 6 are provided in each of the pair of compression chambers 3 and 4 having different closing volumes, and the compression chambers 3 and 4 are provided on the side having the larger closing volume. The passage cross-sectional area of the discharge bypass port 5 formed in one compression chamber 3 is set to the closed volume from the passage cross-sectional area of the discharge bypass port 6 formed in the other compression chamber 4 on the side of the smaller closed volume. Correspondingly large.

In the compression operation of the compression mechanism of FIG. 7 for one cycle, FIG.
At 360 degrees, (b) is 90 degrees, (c) is 180 degrees, (d) is 270
Each turning state is repeated.

A pair of compression chambers 3, 4 formed between each other,
The refrigerant is swirled from the open position shown in FIG. 2B to the closed position shown in FIG.
The refrigerant is sufficiently confined in the swirling process returning to (a) after being sucked through the suction port 24 shown in FIG.
As the volumes of the pair of compression chambers 3 and 4 are sequentially reduced by the rotations of (c), (d) and (a), the refrigerant is gradually compressed. 2 (b) to 2 (c),
The compressed refrigerant is discharged through the discharge port 25 shown in FIG. 8 while the compression chambers 3 and 4 start to communicate with the discharge port 25 and further reduce the volume of the compression chambers 3 and 4 in the process of turning. The discharged refrigerant is connected to the outside of the closed vessel 22 through the discharge pipe 41 and then returned to the inside of the closed vessel 22 through the suction pipe 42, and thereafter, the same operation is repeated.

In the compression operation for one cycle of the compression mechanism, the closed volumes of one and the other of the pair of compression chambers 3 and 4 are different, and according to the difference of the closed volumes, the compression chambers 3 and 4 pass through the bypass ports 5 and 6. The passage cross-sectional areas of the early discharge passages 11 and 12 shown in FIGS. 1, 2 and 8 from the respective compression chambers 3 and 4 are set. As a specific method of making the confining volume different, a method of changing the winding end angle of the orbiting scroll and the fixed scroll is most common.

As another method, the winding end angle is the same, and the outside of the orbiting scroll at the winding end and the extension from the fixed scroll winding end are provided with an appropriate gap.
There is also a method in which the amount of the trapped gas is made different depending on the supercharging effect. This passage cross-sectional area is set to be larger for the compression chamber 3 having a large closed volume than for the compression chamber 4 having a small closed volume.

As described above, the pair of compression chambers 3 and 4 formed by the basic blades 1a and 1b can be operated at a higher speed than the reference operation speed by an amount smaller than the reference. The pair of compression chambers 3 and 4 having different closed volumes are appropriately adapted to the volumes thereof, so that the early discharge of the over-compressed fluid is achieved through the early discharge path by the bypass ports 5, 6 and the like. The early discharge of the super-compressed fluid in the compression chambers 3 and 4 is almost uniformly achieved without excess or shortage, the compression efficiency is improved, and the operation state is more stable.

When equalization of over-compression prevention in the pair of compression chambers 3 and 4 having different closed volumes is achieved, the bypass ports 5 and 6 of the pair of compression chambers 3 and 4 become When the pressure is substantially the same or higher, the openings are opened almost simultaneously, the compression efficiency is further improved, and the same over-compressed state occurs in both of the pair of compression chambers 3 and 4 having different closed volumes. Sometimes they work almost simultaneously, so the number of noise occurrences is halved. The discharge bypass ports 5, 6 respectively formed in the pair of compression chambers 3, 4 having different closed volumes have a plurality of small holes 5a having a diameter smaller than the basic blade thickness 1a, 2a. 6b adjacently formed,
The sum of the opening areas of the plurality of small holes 5a, 6a is defined as the passage cross-sectional area of each of the discharge bypass ports 5, 6.

By forming the plurality of small holes 5a and 6a in this manner, the cross-sectional area of the discharge bypass ports 5 and 6 can be determined by the sum of the opening areas of the plurality of small holes 5a and 6a. .

Also, discharge bypass ports 5, formed in a pair of compression chambers 3, 4 having different closing volumes, respectively.
A discharge bypass port 6 is formed adjacent to a plurality of small holes 5a, 6a having a diameter smaller than the basic blade thickness and having substantially the same diameter, and formed in one of the compression chambers 3 on the side with the larger closed volume. The number of the small holes 5a is changed to the discharge bypass port 6 formed in the other compression chamber 4 on the side with the smaller closed volume.
Are formed more than the number of the small holes 6a.

In this manner, the cross-sectional area of the passage can be easily set by the number of the plurality of small holes 5a, 6a as the bypass ports 5, 6, which form the majority of the early discharge paths 11, 12. That is, as shown in FIGS. 1 and 2, a plurality of small holes 5 a having substantially the same diameter as the bypass ports 5 and 6 having a thickness smaller than the thickness of the basic blades 1 a and 2 a.
6a, three small holes 5a are provided for the compression chamber 3 having a large confined volume, and two small holes 6a are provided for the compression chamber 4 having a small confined volume. Early discharge path 12 in passage 4
Is larger than the cross-sectional area of the passage.

However, the plurality of small holes 5a and 6a forming the bypass ports 5 and 6 may have different opening areas. Further, the opening area may be different between the plurality of small holes 5a and the plurality of small holes 6a, or it is necessary that the respective opening areas be the same between the plurality of small holes 5a and 6a. Absent.

That is, the cross-sectional area of the passage forming the sum of the opening areas of the plurality of small holes 5 a forming one bypass port 5 is the sum of the opening areas of the plurality of small holes 6 a forming the other bypass port 6. What is necessary is just to make it larger by a predetermined ratio than the passage sectional area to be formed. This ratio depends on the ratio of the volume of the compression chamber 3 to the compression chamber 4.

Each of the bypass ports 5 and 6 having a plurality of small holes formed adjacent to each other as shown in FIGS. 2 to 6 is a bypass valve formed of a spring plate provided on the back surface of the fixed scroll 1. The reed valves 13 and 14 constitute a valve and are opened and closed by the valve. The reed valves 13 and 14 constituting the valve are normally closed to the respective bypass ports 5 and 6, and the compression chamber 3 4 is opened when the pressure becomes equal to or higher than a predetermined pressure, so that the over-compressed refrigerant is discharged at an early stage. As a result, the reed valve 1 in which the discharge bypass ports 5, 6 formed by the plurality of small holes 5a, 6a compose a valve collectively.
It is opened and closed by 3 and 14.

The reed valves 13 and 14 are connected to the reed valve 2 of the discharge port 25 substantially at the center of the fixed scroll 1.
6 together with one reed valve 13, 1
4, 26, and the base end is shared and integrally formed.

As shown in FIG. 6, the stopper 15 also has stopper portions 15a to 15c for the respective reed valves 13, 14, and 26 formed on a single metal plate. Thus, the lift amount is fixed when the reed valves 13 and 14 are opened.

However, the reed valves 13, 14, 26
May be appropriately divided and formed, or the reed valves 13, 1
4, 26 may be replaced by other types of on-off valves.
In this case, when using as an element for setting the passage cross-sectional area of the excess refrigerant early discharge paths 11 and 12 based on the lift amount by which the valve opens, a type that can do so will be adopted.

The bypass ports 5 and 6 shown in FIG.
A counterbore 7 which includes a plurality of adjacent small holes 5a and 6a is formed on the opposite side of the basic blade forming the back surface of the fixed scroll 1 end plate, and the reed valve 13 is formed by using the counterbore 7 as a valve seat. , 14.

The counterbore 7 is connected to the reed valves 13, 1
The compression chamber 3 is normally closed, and is opened when the compression chambers 3 and 4 have a predetermined pressure or more, so that the over-compressed refrigerant is discharged at an early stage.

In such a configuration, the overcompressed fluid can be discharged early through the bypass ports 5, 6 having a passage cross-sectional area corresponding to the difference in the volume of the pair of compression chambers 3, 4. The early discharge of the over-compressed refrigerant in each of the compression chambers 3 and 4 is achieved almost uniformly regardless of the difference in the size of the compression chambers 3 and 4 without excess or shortage, and the compression efficiency is improved and the operation state is more stable. Become.

However, the small holes 5 serving as the bypass ports 5, 6 of the pair of compression chambers 3, 4 having different closing volumes.
When the number of a, 6a increases, the reed valves 13, 14
Of the reed valve 13, 1
4 may have reduced responsiveness. Therefore, the bypass ports 5, 6 of the compression chambers 3, 4 having a pair of closed volumes different from each other.
The counterbore 7 covering each of the plurality of small holes 5a and 6a is used as a valve seat of the valve, so that each of the plurality of small holes 5a and 6a can be opened and closed comprehensively. The compression efficiency is improved by reducing the discharge resistance.

The bypass ports 5 and 6 shown in FIG. 4 are formed with a ring-shaped ridge 8 covering the adjacent small holes 5a and 6a on the back side of the fixed scroll 1 end plate opposite the basic blade side. The ridge 8 is used as a valve seat to be opened and closed by the reed valves 13 and 14. The ridges 8 are normally closed by the reed valves 13 and 14, and the compression chambers 3 and 4 are closed.
Is opened when the pressure becomes equal to or higher than a predetermined pressure, so that the over-compressed refrigerant is discharged early.

In this configuration, instead of the formation of the counterbore 7, a ring-shaped ridge 8 covering each of the plurality of adjacent small holes 5a and 6a is formed.
As in the case of the above, the opening and closing operation of the valve can be performed for each of the plurality of small holes 5a, 6a, and the compression efficiency is improved by reducing the resistance of the early discharge of the over-compressed refrigerant.

The bypass ports 5 and 6 shown in FIG. 5 are provided on the opposite side of the fixed scroll 1 end plate from the basic blade side, among the plurality of adjacent small holes 5a and 6a, the small hole 5 closest to the suction side.
A counterbore 9 is provided in each of b and 6b, and a plurality of adjacent small holes 5a and 6a including the small holes 5b and 6b forming the counterbore 9 are opened and closed by the valve. The bypass port including the counterbore 9 is normally closed by reed valves 13 and 14 constituting a valve, and is opened when the pressure in the compression chambers 3 and 4 exceeds a predetermined pressure. Moreover, among the plurality of adjacent small holes 5a, 6a,
Since the counterbore 9 is provided in each of the bypass ports 5 and 6 closest to the suction side, the discharge resistance is reduced by the counterbore 9 in each of the bypass ports 5 and 6 on the suction side where the earliest early discharge is performed. As a result, the early discharge of the over-compressed refrigerant is performed smoothly.

The refrigerant passages when the reed valves 13 and 14 are opened also form the early discharge paths 11 and 12 for the over-compressed refrigerant. Therefore, instead of or in cooperation with the bypass ports 5, 6, the reed valves are used to make the passage cross-sectional areas of the early discharge paths 11, 12 different. Lift amount L of 13, 14
Can be handled differently.

[0055]

According to the scroll compressor of the present invention, the fixed scroll in which the spiral basic blades stand on the end plate and the orbiting scroll in which the spiral basic blades stand on the end plate engage with each other. A pair of compression chambers having different closed volumes is formed, and a discharge bypass port is provided for each of the pair of compressed chambers having different closed volumes, and formed in one of the compression chambers on the side with the larger closed volume. The cross-sectional area of the discharge bypass port is larger than the cross-sectional area of the discharge bypass port formed in the other compression chamber on the side with the smaller closed volume. Properly corresponding to that volume,
The early discharge of the over-compressed fluid is achieved through the early discharge path by the bypass port and the like, and the early discharge of the over-compressed fluid in the compression chambers having the pair of closed volumes different from each other is achieved almost uniformly without excess or shortage. The efficiency is improved and the operating condition is more stable.

Further, when equalization of overcompression prevention in the pair of compression chambers having different closed volumes is achieved, when the bypass ports of the pair of compression chambers have substantially the same pressure or more, they are almost simultaneously. It opens and the compression efficiency is further improved, and it works almost simultaneously when a similar over-compression state occurs in both of a pair of compression chambers with different closed volumes, so the number of times of noise generation is reduced. Will be halved.

[Brief description of the drawings]

FIG. 1 is an internal structural diagram of a compression mechanism showing a state in which a compression chamber is formed between a fixed scroll and an orbiting scroll in a scroll compressor according to an embodiment of the present invention.

FIG. 2 is a rear view of a fixed scroll showing a bypass port and a reed valve for opening and closing the bypass port in the compression mechanism of FIG. 1;

FIG. 3 is a rear view of a fixed scroll showing another example of a bypass port and a reed valve for opening and closing the bypass port in the compression mechanism of FIG. 1;

FIG. 4 is a rear view of a fixed scroll showing another example of a bypass port and a reed valve for opening and closing the bypass port in the compression mechanism of FIG. 1;

FIG. 5 is a rear view of a fixed scroll showing another example of a bypass port of the compression mechanism of FIG. 1 and a reed valve for opening and closing the bypass port.

FIG. 6 is a plan view showing a stopper of the reed valve of FIG. 1;

FIG. 7 is an operation diagram showing a compression operation for one cycle of the compression mechanism of FIG. 1;

FIG. 8 is a cross-sectional view showing the overall configuration of the scroll compressor.

FIG. 9 is an internal structure diagram of a compression mechanism showing a state in which a compression chamber is formed between a fixed scroll and an orbiting scroll in a conventional scroll compressor.

FIG. 10 is an operation diagram showing a compression operation state for one cycle of the compression mechanism of FIG. 9;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Fixed scroll 2 Orbiting scroll 1a, 2a Basic blade 3, 4 Compression chamber 5, 6 Bypass port 5a, 6a Small hole 5b, 6b Smallest hole on suction side 7 Counterbore 8 Ridge 9 Counterbore 12 Early discharge path 13, 14 Reed valve

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Hirofumi Yoshida 1006 Kadoma Kadoma, Kadoma City, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. 72) Inventor Noboru Iida 1006 Kazuma Kadoma, Kadoma City, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. (72) Inventor Atsushi 1006 Kadoma Kadoma, Kadoma City, Osaka Pref. AB03 BB21 BB42 BB47 CC03 CC05 CC15 CC25 3H039 AA02 AA04 AA12 BB02 BB17 BB28 CC03 CC08 CC29 CC30

Claims (7)

[Claims] 1. A fixed scroll in which a spiral basic blade rises on a head plate and a revolving scroll in which a spiral basic blade rises on a head plate, and a pair of closed volumes are made different between the two. In a scroll compressor in which a compression chamber is formed, a discharge bypass port is provided in each of the pair of compression chambers having different closed volumes, and a discharge bypass port formed in one of the compression chambers on the side with the larger closed volume. Wherein the cross-sectional area of the passage is larger than the cross-sectional area of the discharge bypass port formed in the other compression chamber on the side with the smaller closed volume, corresponding to the different closed volumes. 2. A discharge bypass port formed in each of the pair of compression chambers having different confining volumes has a plurality of small holes having a diameter smaller than a basic blade thickness formed adjacent to each other. 2. The scroll compressor according to claim 1, wherein the sum of the opening areas of the small holes is defined as a passage cross-sectional area of the discharge bypass port. 3. A discharge bypass port formed in each of the pair of compression chambers having different closed volumes has a plurality of small holes having substantially the same diameter adjacent to each other and having a diameter smaller than the thickness of a basic blade. Then, the number of small holes of the discharge bypass port formed in one of the compression chambers on the side of the larger closed volume,
3. The scroll compressor according to claim 1, wherein the number of the small holes of the discharge bypass port formed in the other compression chamber having the smaller closed volume is larger than the number of the small holes. 4. A discharge bypass port formed in each of the pair of compression chambers having different closed volumes has a plurality of small holes having a diameter smaller than the thickness of a basic blade adjacent to each other. The scroll compressor according to any one of claims 1 to 3, further comprising a valve that opens and closes each of the discharge bypass ports formed by the small holes. 5. A counterbore for covering a plurality of adjacent small holes is formed on a side of the fixed scroll head plate opposite to the basic blade, and the counterbore is used as a valve seat to be opened and closed by the valve. The scroll compressor according to any one of claims 1 to 4, wherein: 6. A ring-shaped ridge covering a plurality of adjacent small holes is provided on the opposite side of the fixed scroll end plate from the basic blade, and the ring-shaped ridge is used as a valve seat to be opened and closed by the valve. 2. The method according to claim 1, wherein
A scroll compressor according to any one of claims 1 to 4. 7. A plurality of holes including a counterbore formed in a hole closest to the suction side among a plurality of adjacent small holes on a side opposite to the basic blade of the fixed scroll head plate, and including the small hole formed with the counterbore. The scroll compressor according to any one of claims 1 to 3, wherein an adjacent small hole is opened and closed by the valve.