KR960004247B1 - Scroll type compressor - Google Patents

Abstract

No content.

Description

Scroll compressor

1 to 3 relates to an embodiment of the present invention,

1 is a longitudinal side view of a scroll compressor,

2 is a view for explaining the release action in order,

3A is a view for explaining a release mechanism in normal operation;

3 (b) is a view for explaining the release mechanism at the time of release;

4 is a view for explaining the release action of another embodiment in order;

5 (a) is a view for explaining a release mechanism during a running operation of another embodiment;

5B is a view for explaining the release mechanism at the time of release;

6 is a plan view of a release mechanism of another embodiment,

7 is a longitudinal sectional view of the release mechanism of the embodiment;

8 is a partially omitted longitudinal cross-sectional view of a scroll compressor of another embodiment;

9 is a partially omitted longitudinal cross-sectional view of a scroll compressor of another embodiment.

* Explanation of symbols for main parts of the drawings

1: sealed case 2: support frame

6: rotation shaft 7: motor

8: rotor 9: stator

10 eccentric hole 15 compression chamber

22: release mechanism 25: spring

29: Oldham ring 33: discharge tube

The present invention relates to, for example, a scroll compressor for use in a refrigeration cycle apparatus, which forms a compression chamber between a fixed scroll and a scroll and sucks, compresses and discharges refrigerant gas, which is a compressed gas, in the compression chamber.

In recent years, among compressors for refrigerant gas used in a refrigeration cycle apparatus, scroll compressors are particularly used.

For example, the scroll compressor is particularly used as a scroll compressor rather than a rotary compressor.

For example, the scroll compressor is more efficient than the rotary compressor, so that a valve mechanism is not required, and the number of parts can be reduced and operation noise can be reduced.

The compressor is accommodated in a rotating shaft in a hermetic case, and a scroll compression mechanism is installed in which the rotating shaft sucks and compresses refrigerant gas at one end.

The scroll compression mechanism is composed of a combination of a rotating scroll which is engaged with an eccentric unit which is integrally installed on the rotating shaft, and which is controlled by rotation, and which only rotates, and a fixed scroll mounted on the support frame.

These orbiting scrolls and fixed scrolls are each formed from a wing portion in which a plate body is wound in a spiral shape, and a disk portion called integrally provided at one end of the wing portion.

Each wing portion is engaged with each other to form a compression chamber, which is a pair of compression spaces between each disc portion.

The refrigerant gas is sucked into each compression chamber of the outer circumference along with the turning motion of the turning scroll.

These compression chambers gradually move to the center of the vortex while at the same time narrowing their volume.

At the place where the compression chamber has moved to the center, the refrigerant gas is compressed to a predetermined high pressure and discharged from a discharge hole provided opposite thereto.

The problem with the scroll compressor which achieves this effect is as described below.

For example, in a rotary compressor, the operating compression ratio changes according to the operating conditions and is automatically adjusted to the optimum state at all times.

On the other hand, the scroll compressor has a structure that operates at a constant compression ratio regardless of load fluctuations such as discharge pressure and suction pressure of the refrigeration cycle.

Too high or too low operating compression ratio leads to high compression loss and poor performance.

For example, when the suction pressure is high and the operation compression ratio is extremely small, the gas pressure generated in the compression chamber becomes extremely large or the pressure on the wing and the wing portion of each scroll increases, which adversely affects reliability.

In such a state, a part of the gas in the compression chamber of the compression chamber is directly returned to the gas suction unit, so that the so-called release mechanism can be provided to reduce the gas pressure in the compression chamber, and the above-mentioned drawback is almost solved.

However, as a feature of the scroll compression mechanism, a pair of compression chambers are formed in symmetrical positions.

These compression chambers simultaneously suck and compress gas.

Therefore, it is conceivable that the above-mentioned release mechanism is provided exclusively in each compression chamber, and at the same time, the same amount of gas must be released.

Even if there is a slight misalignment, the pressure difference occurs between a pair of compression chambers, and the turning scroll is tilted.

As a result, the swinging scroll is strongly in sliding contact with the fixed scroll in part, which may cause wear damage.

Therefore, the release mechanism must be of a relatively complex structure and at the same time, it is extremely difficult to release the same amount of gas accurately.

Japanese Patent Laid-Open No. 63-259104 has been disclosed for the purpose of eliminating this drawback.

The scroll compressor of the present invention is characterized in that a passage communicating with the gas suction portion and the compression space is provided in the fixed scroll, and the valve for capacity control can be provided in this passage.

Another proposal is Japanese Laid-Open Patent Publication No. 62-105389.

The pair of bypass passages are provided on the wing bottom side of the fixed scroll portion, and the communication passages communicating these bypass passages are provided on the surface opposite to the surface on which the wing portion of the fixed scroll disc portion protrudes.

Each of the bypass passages is provided with a liquidate for opening and closing the bypass toe, respectively.

However, both of these proposals have a large number of parts, adversely affect the cost, and at the same time, it is difficult to accurately release the same amount from a compression chamber of dynamic pressure, and control reliability is low.

This invention is made | formed by such a situation, and the objective is formed as a pair of characteristics of this compression mechanism.

It is an object of the present invention to provide a scroll compressor capable of accurately releasing a gas at the same time from a dynamic pressure chamber of a dynamic pressure and improving the release efficiency with a relatively simple structure.

The scroll compressor which forms a compression chamber between the fixed scroll and the swing scroll of the present invention to perform a compression action is connected to the swing drive means and the swing drive means and protrudes from the disc portion and one side of the disc portion. It consists of the wing which is a spiral body wound in a spiral shape, and consists of a swinging scroll and a disk part for pivoting movement, and a wing part of the disk body that is projected on one side of the disk part and wound in a swirl shape. A fixed scroll meshed with the gas, a gas suction means for introducing and introducing a compressed gas opposed to the fixed scroll and the outer periphery of the rotating scroll, and installed against the vortex center of the wing of the fixed scroll and the rotating scroll to be compressed. Gas discharge means for guiding the discharge of gas, the wing portion and the disc portion of the fixed scroll and the line A pair of spaces formed between the wing portion and the disc portion of the rotating scroll, which is input from the vortex outer end of each wing portion of the rotating scroll to fix the gas guided by the gas suction means in conjunction with the turning movement of the rotating scroll; A first compression chamber and a second compression chamber, which are always at the same pressure, which compress the gas which is moved toward the vortex center of each wing portion, and whose volume is gradually reduced and discharged to the gas discharge means, and the first compression chamber and A first introduction hole and a second introduction hole opened to face a position during compression of the second compression chamber, a communication path communicating these first introduction holes and the second introduction hole, and at least the Directly opening and closing a portion of one of the compression chamber gases in a state of opening and closing freely between the first compression chamber and the second compression chamber and the gas suction means, A part of the other compression chamber gas was provided to the said gas suction means by the same amount by the same amount through the said 1st, 2nd introduction hole, the said communication path, and one compression chamber simultaneously.

An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.

Fig. 1 shows, for example, a scroll compressor used in a refrigeration cycle apparatus.

A support frame 2 is installed at the lower portion of the inner side of the sealed case 1 elongated in the longitudinal direction.

The spindle 3 is attached to the support frame 2, and the rotation shaft 6 is freely installed on the spindle 3.

The axis of rotation 6 is axially oriented in the vertical direction and the upper part is formed with a main shaft portion 6a having a thin diameter.

The main motor unit 6a is provided with an electric motor unit 7.

The motor portion 7 has a rotor 8 fitted to the main shaft portion 6a and an inner circumferential surface having a narrow distance from the main surface of the rotor 8 and from the stator 9 attached to the sealing face 1. do.

The motor unit 7 adopts an inverter type that can control the driving frequency.

The part provided in the said spindle number 3 at the lower side of the rotating shaft 6 of the said spindle part 6a becomes the eccentric part 6b.

This eccentric part 6b is formed larger in diameter than the main shaft part 6a.

The eccentric hole 10 which has an axial center which is eccentric with the axial center of the rotation shaft 6 of a certain length toward this from the lower end surface is provided.

The scroll compression mechanism 12 is connected to the eccentric portion 6b.

The scroll compression mechanism 12 includes a swing scroll 13 having a boss portion 13c engaged with the eccentric hole 10, and a fixed scroll 14 fixed to the support frame 2. .

The electric motor unit 7 is a rotational movement driving means (S) for driving to rotate the pivoting scroll 13 in the eccentric portion (6b) integrally installed on the rotary shaft (6) and the rotary shaft.

These orbiting scrolls 13 and fixed scrolls 14 are composed of wing portions 13a and 14a, and disc portions 13a and 14a, which are referred to as integral plate portions integral with the wing portions 13b and 14b, respectively. do.

The wing portions 13a and 14a are respectively plate bodies wound in a spiral shape and mesh with each other.

In each of the turning scrolls 13 and the fixed scrolls 14, a compression chamber 15 to be described later, which is a space portion of the wing portions 13a, 14a and the disc portions 13b, 14b, is formed.

The discharge hole 16 is provided in the center of the turning scroll disc 13b.

This discharge hole 16 communicates with the gas discharge path 17 provided along the central axis of the water retaining portion 13c.

The gas discharge path 17 is connected to the eccentric hole 10 of the rotary shaft 6 and communicates with the gas guide hole 18 that is opened on the outer circumferential surface of the rotary shaft 6.

The gas discharge means E is constituted by the discharge holes 16, the gas discharge path 17, the gas guide holes 18 and the like.

On the other hand, a first introduction hole 20a and a second introduction hole 20b are provided in the turning scroll disc portion 13b.

One open end of the first and second introduction holes 20a and 20b is opened in the bottom face of the wing 13a side of the disc 13b.

The other open end is connected to a communication path 21 provided in the plate of the disc portion 13b.

Therefore, the compression chamber 15 and the " 15 " interaction between the introduction holes 20a and 20b and the introduction holes 20a and 20b are interlocked through the communication passage 21.

Although the communication path 21 is provided from the main surface of the circular canopy 13b, the closing member 19 is inserted and closed in the opening end of the disk part 13b.

In the fixed scroll disc portion 14b, a release mechanism 22 constituting the release means is provided.

As shown in FIG. 2, the first compression chamber 15a and the second compression chamber 15b of the same pressure are always formed in the symmetrical position with the turning movement of the turning scroll 13.

That is, when the turning scroll 13 pivots, each turning, the end Z of each winding of the fixed scroll blades 13a and 14a ends, Z and the wing 13a and 14a mesh with each other. A pair of space parts P1 and P2 which are opened to the outer peripheral part are formed between the circumferential wall of the opposite wing part 14a and 3a.

The end Z at which the winding ends is an outer circumferential end of each of the wing portions 13a and 14a formed in a swirl shape.

In the same drawing, the space portions P1 and P2 start to form at a rotational angle of 60 °, and the end Z, which is wound at a rotational angle of 180 °, "Z" and the relative wing portions 13a and 14a. ) The gap with the main wall is maximum.

After this, the interval is gradually narrowed so that the end Z, which is wound around the rotation angle between 300 ° and 0 °, “Z” touches the circumferential wall of the opposite wing parts 14a and 13a.

The outer circumferential portion of the scrolls 13 and 14 faces the gas suction means described later, so that gas first enters the spaces P1 and P2.

In conjunction with the turning movement of the turning scroll 13, the spaces P1 and P2 are closed to form a first compression chamber 15a and a second compression chamber 15b.

These first compression chambers 15a and the second compression chambers 15b are at the same pressure and are accompanied by the rotational movement of the revolving scroll 13, and the winding start ends of the scroll blades 13a and 14a are mutually equal. A), it moves by the same amount toward "A".

The winding start end A is a vortex center end of each wing 13a, 14a formed in a vortex shape.

At the same time, the volume of each compression chamber 15a, 15b is gradually reduced.

The amount of change in volume is the same as that of each compression chamber 15a, 15b so that they always maintain dynamic pressure.

The first introduction hole 20a and the second introduction hole 20b select and open positions opposing the first compression chamber 15a and the second compression chamber 15b with respect to the relatively low pressure side. do.

The release mechanism 22 is provided here at a portion where the second inlet hole 20b opens and faces the second compression chamber 15b.

However, part of the release radix 22 which is connected to the position of this wing | blade part 13a because the turning scroll 13 rotates is a part where a 1st part opposes the 1st compression chamber 15a. There is also.

The position of the release singer 22 is not limited to the above embodiment, but the winding start end A is inward from the end Z where the winding of the fixed scroll vane 14a ends. It is good to set in the range of 360 degree toward ().

The release mechanism 22 is configured as shown in FIG.

The release hole 23 penetrates the fixed scroll disc portion 14b.

The release hole 23 is a small diameter portion 23a having a small diameter opening on the compression chamber 15 and a large diameter portion 23b having a largest diameter on the side opening on the outer surface of the disc portion 14b. have.

Between these small diameter part 23a and large diameter part 23b, 23c which is the diameter of these diameters is formed, and these are connected in the same axial direction.

The release valve 24 is accommodated freely in the release hole 23.

The release valve 24 has a valve body 24a that is freely accommodated in the release hole large diameter portion 23b.

The valve body 24a is freely accommodated in the large-diameter portion 23b with the spring 25 and is freely received. The force is further applied in the direction of exiting the outer surface side of the disc portion 14b at all times by the elastic force of the spring 25. Become.

A valve head 24b is formed on the upper side of the valve body 24a and slides freely in the release hole small diameter portion 23b to open and close the small diameter portion 23a simultaneously with the movement of the valve body 24a. It is supposed to be.

The lower side of the valve body 24a is formed with a small diameter protrusion 24c and protrudes outward from the release hole diameter portion 23b for release.

This projection 24c is fitted freely and hermetically to the valve receiving member 26 by sliding.

The valve receiving member 26 is provided through a fixing member (not shown) on the bottom surface of the fixed scroll disc portion 14b, and closes the release hole large diameter portion 23b.

One end of the release communication hole 32 communicates with a part of the release hole large diameter portion 23b.

The other end of the release communication hole 32 is opened at a position outside the outer peripheral surface of the fixed scroll blade portion 14a.

By the up and down positions of the release valve 24, the valve body 24a opens and closes between the release communication hole 32 and the large diameter portion 23b.

The release valve 24 receives the action from the driving means K to open and close the release hole 23.

The drive means K may use the difference between the pressure of the compression chamber 15 and the pressure outside the fixed scroll blade 14b, or may guide and control the suction pressure or the discharge pressure of the compressor itself or the solenoid valve. May be connected to operate.

As shown in FIG. 1, the thrust ring 28 which receives the thrust load of the turning scroll 13 is interposed between the back side of the turning scroll disc part 13b, and the lower surface of the main spindle 3. As shown in FIG.

On the outer circumferential portion of the thrust ring 28, an Oldham ring 29 is fitted between the rear surface of the disc portion 13b and the support frame 2 to serve as a means for regulating the rotation of the swing scroll.

At the side of the sealed case 1, a suction pipe 30 penetrates the gas suction means communicating with an evaporator (not shown) of the refrigeration cycle apparatus.

The suction pipe 30 is opened to face the outer periphery of the turning scroll 13 and the fixed scroll 14.

On the other hand, the discharge pipe 33 is connected to the upper end of the sealed case 1 in communication with the condenser (not shown) of the refrigeration cycle apparatus.

The earth pipe 33 communicates with the interior of the sealed case 1.

Next, the operation of the scroll compressor configured in this way will be described.

When the motor unit 7 rotates the rotary shaft 6, the turning scroll maintenance part 13c engaged with the eccentric hole 10 makes a turning motion, and the turning scroll 13 makes a turning motion.

The low pressure refrigerant gas evaporated from the evaporator of the refrigeration cycle apparatus is led to the scroll compression mechanism (12) through the suction section (30).

As described earlier in FIG. 2, the low-pressure refrigerant gas includes the end portions Z, "Z" and the wing portions 13a and 14a, which are wound around each turning and fixed scroll wing portions 13a and 14a, respectively. The space | intervals P1 and P2 which were formed between the main wall of the wing part 14a, 13a of the mating partner, and were opened are collected.

Then, the space portions P1 and P2 opened in conjunction with the swinging movement of the swinging scroll 13 are closed to change into the first compression chamber 15a and the second compression chamber 15b.

These compression chambers 15a and 15b are moved by the same amount toward the winding start ends A and " A " of the respective scroll vanes 13a and 14a.

The pair of compression chambers 15a and 16b move under the same pressure, and at the same time their volume is gradually reduced so that the guided gas is compressed.

Where these compression chambers 15a and 15b have moved to the winding start end A, " A ", the refrigerant gas rises to a predetermined pressure and merges with each other.

The compressed, high pressure gas is shown in FIG. 1 and discharged from the discharge hole 16 to be guided to the gas discharge path 17.

Moreover, it is led to the gas guide passage 18 and discharged into the sealed case 1 to be filled.

The high-pressure gas rises in the upper portion of the sealed case 1 through the gap between the rotor 8 and the stator 9 of the motor unit 7 and the oil return hole provided in the rotating shaft.

Then, it is discharged from the discharge tube 33 of the upper end of the case 1 to the shaft of the refrigeration cycle apparatus.

The release mechanism 22 is not operated during such a normal compression operation.

3 (a) shows the state at this time.

By acting the drive means K, a force for pressing the release valve 24 against the elastic force of the spring 25 is added.

The valve head 24b of the release valve 24 fits into the small diameter portion 23a of the release hole 23 and closes the bottom surface of the wing portion 14a side of the fixed scroll disc portion 14b.

Therefore, the first and second compression chambers 15a and 15b, through which the first and second introduction holes 20a and 20b open, have these introduction holes 20a and 20b and the communication path 21 as well. Only communicate with each other.

As a result, the compression capacities for the mutual compression chambers 15a and 15b do not change and have no effect on the compression action.

When the compression ratio is changed in response to the load, the release mechanism 22 may be operated.

Specifically, as shown in FIG. 3 (b), only the operation of the driving means K is stopped.

Then, the elastic force of the spring 25 acts to push down the release valve 24.

The valve head 24b of the release valve 24 opens the small diameter portion 23a, and the valve body 24a communicates with the outer circumferential portion of the fixed scroll blade portion 14a through the release communication hole 32.

Again, as shown in FIG. 2, it is called a rotation angle of 0 degree with respect to the figure shown to the left uppermost position.

At this time, each of the first compression chamber 15a and the second compression chamber 15b completes suction of the refrigerant gas, and the compression operation is started.

Hereinafter, the revolving scroll blade portion 13a performs the revolving motion according to the arrow and changes the position of the revolving scroll blade portion 14a.

Since the release hole 23 is open, a part of the gas in the second compression chamber 15b is directly released from the release hole 23 to the outer peripheral part of the wing portion 14a, which is a gas suction part, at a rotational angle of 60 °. It is done.

In addition, a part of the gas of the first compression chamber 15a is released through the direct release hole 23, and a part of the gas is introduced into the first introduction hole 20a, the communication path 21, and the second introduction. Even if the hole 20b is sequentially moved and once enters the 2nd compression chamber 15b, it will be released through the release hole 23 on it.

At the position of the rotation angle of 120 °, the gas of the second compression chamber 15b is the direct release hole 23, and the gas of the first compression chamber 15a communicates with the first introduction hole 20a. The hole 21 and the second introduction hole 20b are sequentially released and released through the second compression chamber 15b and the release hole 23.

At the position of the rotational angle of 180 degrees, the state of the rotational angle of 120 degrees is obtained.

At the position of the rotation angle of 240 °, the positive compression chambers 15a and 15b are completely separated from the release hole 23, so that the release action is completed.

The position of the rotation angle 360 ° is the same as the rotation angle 0 ° described above, and the same operation is repeated.

In this manner, the release mechanism can be used to change the compression ratio according to the load while being a scroll compressor, and the stress on each blade portion 13a, 14a is reduced, thereby improving the compression performance.

Moreover, since the compression ratio is variable, the compression ratio changes, which is advantageous for low speed operation and continuous operation.

It is two compression spaces at the same time, and can accurately release the same amount of gas from the 1st compression chamber 15a and the 2nd compression chamber 15b.

These operations can be made into a relatively simple structure of only one release mechanism 22, and a large improvement in the release efficiency can be achieved.

In addition, since the position of the said release mechanism 22 was provided inward from the winding end part Z of the fixed scroll blade part 14a within the range of 360 degrees, the 1st, 2nd compression chamber 15a is provided. In (15b), the compression operation can be performed after the release operation is completely completed, respectively.

Therefore, a large release rate can be maintained without reducing compression efficiency.

The position of the release mechanism 22 may be near the end Z where the winding of the fixed scroll blade portion 14a ends.

In this case, formation of the release hole 23 becomes easy.

On the other hand, since it is provided in the extremely near end part of a compression space, the release rate becomes small compared with the case where it is provided in the inside and 360 degree range than the winding end Z.

4 shows the release action in the case of having a release means composed of the first release mechanism 22A and the second release mechanism 22B.

The first release mechanism 22A is provided on the inner side of the fixed scroll blade portion 14a at the end of the winding end Z and in the range of 360 °.

The structure of the second release mechanism 22A may be the same as the release mechanism 22 as described above in FIG. 3.

The second release mechanism 22B is configured as shown in Figs. 5A and 5B.

That is, the release valve 24, the spring 25, the valve receiving member 26 and the driving means K are the same as described above.

23A of new release holes 23A are provided with the small diameter part 23q and the large diameter part 23b.

5 (a) is a normal operation state, and the valve head 24b of the release valve 24 closes the small diameter portion 23a, so that there is no influence on the compression action.

5 (b) shows the state of the release action.

When the driving force is stopped and the driving force is dissipated, the elastic force of the spring 25 acts so that the valve head 24b of the release valve 24 opens the open end of the small diameter portion 23a.

At this time, the release hole 23A is partitioned by the revolving scroll blade portion 13a so as to face the compression chambers 15 and "15" on both sides.

As shown in FIG. 4 again, the first release mechanism 22A functions exactly the same as the release mechanism 22 described with reference to FIG.

However, the first release mechanism 22A has only a very small amount of release from the second compression chamber 15b between the setting of the position and the rotation angle from 0 ° to 60 °.

On the other hand, the 2nd tooth release mechanism 22B newly provided is in the position which smoothly releases the gas of the 2nd compression chamber 15b in the range of the same rotation angle.

That is, the opening end of the release hole 23A is partitioned so as to face the compression chambers 15 and "15" on both sides by the revolving scroll blade portion 13a.

In the same figure, the inner compression chamber 15 corresponds to the second compression chamber 15b, and the outer compression chamber 15 is a position facing the gas suction section. In particular, the rotation angle is from 0 ° to 60 °. It is possible to reduce the loss of gas pressure in the second compression chamber 15b, to prevent unnecessary compression, and to secure the release efficiency.

The second release mechanism 220B of the modification as shown in FIGS. 6 and 7 may be used.

In this case, the release valve 24, the spring 25 and the valve receiving member 26 are the same as described above.

The lap groove 33 is newly installed.

The lap groove 33 communicates with the opening end of the compression chamber 15 side of the release hole 23b and extends to the gas suction side.

Under normal conditions without release, it does not affect the compression efficiency as described above.

At the time of release, the total area of the release hole 23b and the lap groove 33 is opened, and the gas in the compression chamber 15 is immediately delivered to the gas suction side, and the pressure loss can be reduced.

It may be a scroll compressor as shown in FIG.

The difference from the scroll compressor described with reference to FIG. 1 is that one end of the communication passage 21 is opened on the main surface of the disc portion 13b of the turning scroll 13.

All other configurations are the same as those described in FIG.

Therefore, the position of the communication path 21, the position of the 1st, 2nd introduction holes 20a and 20b which communicate with the communication path 21, and the structure of the release mechanism 22 are exactly the same.

The thrust ring 28 is divided into an inner circumferential portion and an outer circumferential portion that are formed between the main surface and the back side of the turning scroll disc portion 13b and the main shaft number 3.

The outer circumferential portion is in a state of communicating with the open end of the communication passage 21, which is referred to as an intermediate pressure chamber 40.

The inner circumferential part is called the high pressure chamber 50 because the inner circumferential part communicates with the inside of the sealed kit 1 at intervals between the main shaft number 3 and the eccentric part 6b.

In the scroll compression mechanism 12A configured as described above, that is, in the normal compression operation, the compression chambers 15 and 15 of the same pressure are applied to the first and second inlet holes 20a and 20b. Gas is simultaneously drawn to the communication path 21 by the same amount.

Since the conduction path 21 communicates with the intermediate pressure chamber 40 formed on the main surface of the disc 13b, the gas under compression is led from the communication path 21 to the intermediate pressure chamber 40.

The gas of the intermediate | middle pressure chamber 40 in the state where the gas pressure with respect to the compression chamber 15 and "15" which communicated with the said 1st, 2nd inlet 20a, 20b fell below the gas pressure of the intermediate | middle pressure chamber 40. FIG. Returns from the communication path 21 to the compression chamber 15, "15" through each introduction hole 20a, 20b.

Therefore, in each compression chamber 15 and "15" which communicate with each introduction hole 20a, 20b, dynamic pressure is always ensured.

In addition, the compressed gas delivered to the intermediate pressure chamber 40 pressurizes the main surface and the back side of the turning scroll disc portion 13b.

Since this pressure is under compression, it is called medium pressure.

While the intermediate pressure applied to the main surface of the disc portion 13b does not have any effective action on the swinging scroll 13, the intermediate pressure applied to the back side presses the entire swing scroll 13 in the axial direction.

That is, while the gas is filled in the intermediate pressure chamber 40, the pressure acts on the back side of the turning scroll disc portion 13b so that the scroll disc portions 13b and 14b opposing the ends of the scroll blade portions 13a and 14a. Seal between them.

On the other hand, the high pressure chamber 50 is always discharged in the sealed case 1 and a part of the high pressure gas filled therein is delivered to become high pressure.

Therefore, a high-pressure negative pressure is applied to the rear side of the turning scroll disc portion 13b, particularly around the boss portion 13c, to ensure sealing between the scrolls 13 and 14.

The scroll compression mechanism 12B as shown in FIG. 9 may be used.

In this case, a pair of introduction holes 120a and 120b are provided in the fixed scroll disc portion 14b.

The lower end openings of the introduction holes 120a and 120b communicate with the communication path 121 which is connected to the plate thickness side of the disc portion 14b.

One end of the communication branch 121a communicates with the connection portion between the communication path 121 and one of the introduction holes 120a.

The communication branch path 121a is connected to the plate thickness side of the disc portion 14b and extends to the main end side thereof, and is bent upwards at a position outside the main end of the turning scroll disc portion 13b thereon. It extends within (2).

The support frame 2 is bent in the horizontal direction and is opened between the thrust ring 28 and the uldom ring 29.

Therefore, the intermediate pressure chamber 40 is formed at the outer circumferential portion of the thrust ring 28.

On the other hand, the inner circumferential side of the thrust ring 28 becomes the high pressure chamber 50.

In addition, one end of the branch passage 123 communicates with the connection portion between the communication passage 121 and the other introduction hole 120b.

The branch passage 123 is exposed along the inside of the plate thickness of the disc portion 14b and is in direct communication with the suction section 30 connected thereto.

The branch passage 123 is provided with a release mechanism 122 that is, for example, a solenoid valve that opens and closes the communication passage 121.

Also in such a structure, some compression gas 15 is drawn from the equal-pressure compression chamber 15 and "15" to the communication path 121 from the mutual introduction hole 120a, 120b which mutually communicates by the same amount at the same time.

The gas is led from the communication passage 121 to the intermediate pressure chamber 40, and applies an intermediate pressure to the rear side of the turning scroll disc portion 13b.

Therefore, there is no change in securing the sealing property between the turning scroll 13 and the fixed scroll 14.

In addition, when the release mechanism 122 is opened from the solenoid valve, the gas under compression conducting through the communication path 121 is directly introduced to the suction pipe 30 so that a high pressure release is possible, and the compression ratio according to the load can be changed. have.

In addition, in the scroll compressor having the same drawing, the same parts as those described in FIG.

Such a scroll compressor can be used not only for a refrigeration cycle apparatus but also for other purposes.

Claims (20)

The scroll compressor, which forms a compression chamber between the fixed scroll and the swinging scroll and performs the compression action, is connected to the swing drive means and the swing drive means and protrudes on the disc and one side of the disc to form a spiral shape. A rotating scroll which is formed from a wing which is wound into a plate body, and which rotates and which is pivoted, and a disk part and a wing which is spirally wound and protruded on one side of the disk part, and the wing part is engaged with the wing part of the swing scroll. A gas suction means for introducing and introducing a scroll and a gas to be compressed by being installed opposite the fixed scroll and the outer periphery of the swing scroll, the wing and the disc portion of the fixed scroll, and the wing and the disc portion of the swing scroll. A pair of spaces formed therebetween and from the gas suction means in conjunction with the turning movement of the turning scroll. The guided gas is fixed, moved from the vortex outer end of each wing of the swing scroll to the vortex center of each wing, and its volume is gradually reduced so that the compressed gas is compressed and discharged to the gas ejection means. First and second compression chambers, a first introduction hole and a second introduction hole opened to face the position during compression of the first compression chamber and the second compression chamber; A communication path communicating the inlet hole of the inlet hole with the second inlet hole, and at least one of the first compression chamber and the second compression chamber and the gas suction means open and close freely. A portion of the gas is directly returned to the gas suction means at the same time through a portion of the gas in the other compression chamber through the first and second introduction holes, the communication path, and one compression chamber. A scroll compressor comprising a return means for coming. The rotating drive means according to claim 1, wherein the swing drive means includes an electric motor portion, a rotation shaft connected to the previous synchronization portion, and a rotation shaft, an eccentric portion installed on the rotation shaft and engaged with the disc portion of the swing scroll, and rotating the swing scroll. Scroll compressor, comprising the Oldham ring to regulate the. The scroll compressor as claimed in claim 1, wherein the pivot drive means, the gas suction means, the gas ejection means, the pivot scroll, the fixed scroll, and the release means are housed in a sealed case. The gas suction means is a suction pipe installed through the sealed case, and the release means has a winding which is a vortex outer end of the opening of the suction pipe and each scroll wing of the positive compression chamber when the gas is opened. Scroll compressor is guided between the end and the end. 2. The release means as set forth in claim 1, wherein said release means compresses after the release action is completely completed in the first compression chamber and the second compression chamber in which the opening ends of the first introduction hole and the second introduction hole face each other. A scroll compressor, which is installed inward from the end where the winding ends of the fixed scroll blades are wound, and from the end where the winding ends, to the center of the vortex, in a range of 360 ° to effect the action. 2. The release means according to claim 1, wherein the release means is provided through the disc portion of the fixed scroll and one end thereof is a release hole for opening in one of the compression chambers, the release hole, and a gas suction means; It is fitted freely in the communication hole communicating with the sliding hole and the release hole, and opens and closes the release valve and the release valve between the release hole and the release communication hole. And a driving means for opening and closing the tooth communication hole. 7. The release hole is a small diameter portion having the smallest diameter on the side opening to the compression chamber, and a large diameter portion having the largest diameter on the side opening on the outer side of the disc portion, and between the large diameter portion and the small diameter portion. The middle diameter portion, which is the diameter of the middle diameter of the diameter of the large diameter portion and the small diameter portion, is installed in the axial direction, the release communication hole communicates the large diameter portion of the release hole and the gas suction means, and the release valve And freely opening and closing the small diameter portion of the release hole at the same time, and simultaneously opening and closing the release communication hole at its main surface. 7. The end of the release valve always protrudes outward from the disc portion of the fixed scroll so that the protruding end of the release valve slides freely, and the valve receiving member fitted in the sealed state has an outer surface of the disc portion. Scroll compressor, characterized in that installed on the side. 7. The driving means according to claim 6, wherein the drive means uses a differential pressure between the compression chamber in which the release hole is opened and the outer circumferential pressure of the fixed scroll to guide and control the suction pressure and the discharge pressure of the compressor, or at least one of the solenoid valves. Scroll compressor, characterized in that one means. 7. The total area of the release hole and the lap groove is opened when the lap groove communicating with the opening end of the release hole is provided in the compression chamber facing surface of the swing scroll disc portion. Scroll compressor. 2. The scroll compressor as set forth in claim 1, wherein the release means is installed at a position near an end portion at which the fixed scroll blade ends are wound. 12. The release hole according to claim 11, wherein the release means is provided in a disc portion of the fixed scroll and has one end opening opened at a position where the one end opening is circumscribed between the compression chamber and the gas suction side by a wing portion of the swing scroll; A scroll compressor, comprising: a release valve freely fitted in a release hole, the release hole being free to open and close; and a driving means for opening and closing the release valve. 13. The release hole is a small diameter portion having a small diameter on the side opening to the compression chamber, and a large diameter portion having a large diameter on the side opening on the outer surface of the disc portion, and these large diameter portions and the small diameter portion are located in the axial direction. Therefore, it is connected, the release valve is a scroll compressor, characterized in that opening and closing the small diameter portion of the release hole at one end. 2. The release mechanism according to claim 1, wherein the release means comprises: a first release mechanism provided inwardly at an end of the end of the winding of the fixed scroll blade and in the range of 360 ° from the end of the winding; It consists of the 2nd release mechanism provided in the vicinity of an end part, and by opening these 1st and 2nd release mechanisms, gas is always discharged from either release mechanism regardless of the rotation angle of the said rotating shaft. Scroll compressor characterized in that the delivery. 2. The communication path according to claim 1, wherein the communication path has a communication branch path for guiding a part of the first and second compressed chamber gases to the back side of the swing scroll disc part, and the negative pressure is applied to the swing scroll guided from the communication branch path. A scroll compressor, characterized in that forcibly sealing between the distal end of the scroll wing and the opposite scroll disc. The thrust ring receiving thrust load of the turning scroll is provided on the back side of the turning scroll disc part, and the inner circumference of the thrust ring is a high pressure chamber in which the high pressure compressed gas discharged from the gas ejection means is guided. And an outer circumferential portion of the thrust ring is an intermediate pressure chamber filled with gas delivered from the communication paper. The scroll compressor as set forth in claim 1, wherein said first and second introduction holes and said communication path are provided in a rotating scroll disc portion, and said release means is provided in said fixed scroll disc portion. 16. The method according to claim 15, wherein the first and second inlet holes and the communication passage are provided in the swing scroll disc portion, the communication paper is opened in the main surface of the swing scroll disc portion, and the release means is formed in the fixed scroll. Scroll compressor, characterized in that installed in the disc portion. 16. The method of claim 15, wherein the first and second introduction holes and the communication passage are provided in the fixed scroll disc portion, and the communication paper extends from the fixed scroll disc portion to the rear side of the swing scroll disc portion and opens. The release means is a scroll compressor, characterized in that installed in the fixed scroll disc. 20. The scroll compressor according to claim 19, wherein the communication path and the gas suction means communicate with the branch path, and the release means is provided in the middle portion of the branch path.