KR101287716B1 - Scroll compressor - Google Patents

Abstract

An object of the present invention is to prevent deterioration of the sealing property at the outermost engagement portions of the fixed scroll and the swinging scroll, to suppress the heating of the working fluid in the suction region, and to improve the energy efficiency.
The scroll compressor includes a fixed scroll (2), a swing scroll (3) which forms compression chambers (100a, 100b) between the fixed scroll by engaging with the fixed scroll, and a fixed scroll on the swing scroll. The back pressure chamber 110 which imparts a pressing force of and a oil supply passage for introducing oil on the compressor discharge side into the back pressure chamber. And a back pressure valve 26 which communicates only with the back pressure chamber and the compression chamber after the initiation of detention, and which is opened and closed by a differential pressure before and after, and which discharges the oil in the back pressure chamber into the compression chamber to control the pressure in the back pressure chamber. It is provided with the communication path 60 and the suction area | region communication path 65 which communicates only with the suction area | region 105 which reaches the said back pressure chamber and the said compression chamber, and supplies the oil of a back pressure chamber to the said suction area | region.

Description

[0001] SCROLL COMPRESSOR [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor having a fixed scroll and an orbiting scroll engaged therewith, and particularly suitable for a scroll compressor for a refrigeration cycle that compresses a refrigerant such as CO ₂ or HFC.

As a conventional scroll compressor, as described in Patent Literature 1, an oil in the discharge space is introduced into the back of the swing scroll to form a back pressure chamber that becomes a pressure between the discharge pressure and the suction pressure, and the pressure in the back pressure chamber. (Hereinafter, referred to as back pressure), some of the scroll scrolls are pressurized with a fixed scroll.

In the case of such a scroll compressor, in order to generate an appropriate back pressure, the oil introduced into the back pressure chamber from the discharge space is discharged to the compression chamber through a communication path having a back pressure valve for controlling the back pressure. The opening (compression chamber side opening) on the compression chamber side of the communication path is a groove (fixed scroll wrap tooth root) that is fitted into a fixed scroll wrap (fixed wrap) that is installed on the compression chamber side of the fixed scroll mirror plate (fixed rigid plate). It is formed in the center of the width direction). In this manner, the oil in the back pressure chamber is equally supplied to the two compression chambers formed on the inner side and the outer side of the lap (swivel lap) which is mounted on the swivel scroll swash plate (slewing lap board). The sealability of the compression chamber formed by the scroll and the swing scroll is improved.

Japanese Patent Application Publication No. 2009-257287

In the patent document 1, in the communication path to the compression chamber, the compression chamber side opening has winding end points (two locations on the inner side and the outer side) of the turning wrap in the fixed root, each of which is referred to below as the inner side turning. Vortex from the point of the fixed wrap engaged with the end of the winding and the outer side turning winding (two ends of the inner side and the outer side, respectively, hereinafter referred to as the end of the inner side fixing winding and the end of the outer side fixing winding). It is formed in the position which entered the lap center side (lap winding start side) along the fixed tooth root of shape.

As a result, the start of detention of the turning outer compression chamber by the engagement of the outer side turning winding end and the end of the fixed side winding winding, or the detention of the turning side compression chamber by the engagement of the end of the inner side winding winding and the end of the outer side fixed winding. From the timing of start (detention start of each compression chamber), the supply of oil to the engagement point (outermost engagement point) at the end of winding is insufficient for a predetermined time. For this reason, there existed a subject that the sealing property in the said outermost engagement location falls, a leak generate | occur | produced, and the energy efficiency of a scroll compressor falls.

Moreover, in the said conventional thing, although the high temperature oil of the back pressure chamber flows out to the said compression chamber side through the said communication path, it turned out that this oil flows in a large amount also in a suction area (suction chamber). As a result, the gas (working fluid such as refrigerant gas) flowing from the suction pipe into the compressor is heated, and the heated gas increases in cost, so that the mass of the working fluid introduced into the compression chamber is lowered. For this reason, in the conventional scroll compressor, little work can be done with respect to the power required for compression, and the overall heat insulation efficiency is lowered (hereinafter referred to as suction heating performance decrease), and the energy efficiency is also lowered from this point. There was also a task.

SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll compressor capable of preventing energy deterioration at the outermost engagement between the fixed scroll and the swinging scroll, and also suppressing heating of the working fluid in the suction region and improving energy efficiency. have.

In order to achieve the above object, the present invention has a fixed scroll having a hard plate and a scroll wrap erected thereon, and a fixed scroll having a hard plate and a scroll lap erected therein, and having a pivoting motion in engagement with the fixed scroll. A scroll compressor having a swing scroll for forming a compression chamber, a back pressure chamber for imparting a pulling force to the fixed scroll to the swing scroll, and an oil supply passage for introducing oil on the compressor discharge side to the back pressure chamber, wherein the back pressure chamber includes: A compression chamber communication path having a back pressure valve communicating only with the compression chamber after the start of detention and opening and closing by a differential pressure before and after, and controlling the pressure in the back pressure chamber by flowing oil from the back pressure chamber into the compression chamber; Only the suction area leading to the compression chamber after the initiation of detention is communicated. It is comprised so that it may not communicate, and it is provided with the suction area | region communication path which supplies the oil of the said back pressure chamber to the said suction area | region.

According to the present invention, it is possible to prevent the deterioration of the sealability at the outermost engagement portions of the fixed scroll and the swinging scroll, and to suppress the heating of the working fluid in the suction area, thereby providing an energy efficient scroll compressor. It has an effect.

1 is a longitudinal sectional view showing a first embodiment of a scroll compressor of the present invention.
FIG. 2 is a bottom view of the fixed scroll shown in FIG. 1 as viewed from below, (a) also includes a swing scroll lap at the start of detention of the swinging outer compression chamber, (b) detaining the swinging inner compression chamber A diagram that includes a turning scroll wrap at the start.
3 is a cross-sectional view taken along the line III-III of the fixed scroll shown in FIG. 2, illustrating a structure near the back pressure valve.
4 is a top view of the swing scroll shown in FIG. 1 as viewed from above.
5 is a VV line cross-sectional view of the turning scroll shown in FIG. 4.
FIG. 6 is an enlarged view of a portion of the fixed hard board near the suction pipe, showing an enlarged view of the portion Q in FIG. 2; FIG.
Fig. 7 is a longitudinal sectional view showing the second embodiment of the scroll compressor of the present invention.
Fig. 8 is a top view of a swinging scroll illustrating a third embodiment of the scroll compressor of the present invention.
FIG. 9 is a longitudinal sectional view of the turning scroll in FIG. 8, taken along line IX-IX in FIG.
Fig. 10 is an enlarged view of the vicinity of a suction pipe on a fixed rigid plate surface of a fixed scroll illustrating a third embodiment of the scroll compressor of the present invention, which corresponds to the Q portion in Fig. 2.
FIG. 11 is a bottom view of a fixed scroll illustrating a fourth embodiment of the scroll compressor of the present invention, in which a turning scroll wrap at the start of detention of the turning outer compression chamber is displayed in an overlapping manner; FIG.
FIG. 12 is a longitudinal sectional view for explaining the configuration of the compression chamber communication path including the back pressure valve of the fixed scroll shown in FIG. 11; FIG. 11 is a sectional view taken along the line XII-XII.
FIG. 13 is a bottom view of a fixed scroll illustrating the possibility of oil supply to the outermost engagement point with a conventional scroll compressor, and also includes a turning scroll wrap at a turning phase angle with a turning scroll of 230 degrees. FIG.
FIG. 14 is a bottom view of the same fixed scroll as in FIG. 13, including a turning scroll wrap at a turning phase angle with a turning scroll of 330 degrees; FIG.
FIG. 15 is a bottom view of the same fixed scroll as in FIG. 13, in which the swing wrap centers the fixed tooth root at the position where the polar coordinates are 270 degrees both at the start of the detention of the turning inner compression chamber and at the start of the detention of the turning outer compression chamber. Drawing explaining what comes to the fore.

First, in the above-mentioned patent document 1, the reason why oil supply to the outermost engagement part stops for a while from the start of the detention of a compression chamber is demonstrated below.

Generally, the compression chamber, which is a detention space, moves to the lap center side with the turning movement of the turning scroll. This causes some of the working fluid to flow along the lap to the center when viewed from a stationary scroll that is stationary. As a result, the oil flowing into the compression chamber from the compression chamber side opening flows toward the center of the lap through the flow of this working fluid. On the other hand, the outermost engagement point also moves to the lap center in accordance with the turning motion of the turning scroll. For this reason, in order to supply the oil which flows in from a compression chamber side opening to the outermost engagement part,

"The outermost engagement point is closer to the center of the lap than the compression chamber side opening along the lap. (One)"

This is a necessary condition. Since the outermost engagement point is determined by the turning phase angle of the swinging scroll, oil can be supplied to the outermost engagement point only when the outermost engagement point is a turning phase angle closer to the center of the lap than the compression chamber opening. In practice, other additional conditions are required.

Next, the case is the same as the conventional scroll compressor shown in FIG. 13 (when the installation direction angle of the compression chamber side opening enters the lap center side (lap winding start side) about 210 degrees from the end of the fixed winding). The additional conditions and the range of turning phase angles that can be supplied to the engagement point will be examined.

Here, the situation is different depending on whether the outermost engagement point is the outermost engagement point of the outer compression chamber or the outermost engagement point of the inner compression chamber. It is considered to be limited to the case where the turning outer line side compression chamber is formed by the engagement of the end of the fixed winding (hereinafter referred to as the turning outer line side outermost engagement point). In addition, in order to simplify, it is considered on condition that the diameter of a compression chamber side opening becomes the same as the thickness of a turning wrap. In addition, it is considered as the polar coordinate which makes a reference direction the fixed winding end direction by making the fixed scroll center the origin.

In this case, it is assumed that the lap shape is formed by a circular involute curve. However, in this case, a straight line passing through the fixed scroll center and passing through two points of the end of the fixed side winding and the end of the fixed side winding is drawn. There is no number. That is, when the two fixed winding end points are connected, it becomes a straight line which passes through the tangent of a base circle from a fixed center. Therefore, the direction angle passing through the center of the fixed winding end of said two points shall be made into a reference direction here, and it shall suppose that a some shift | offset | dyes in an angle is allowed.

If you do the above,

"The direction angle of the turning outer side outermost engagement point is equivalent to the turning phase angle of a turning scroll. (2)"

It can be seen that. (However, in the case of the turning extension side outermost engagement point, it shifts 180 degrees.)

Therefore, from the above (1), (2),

"The turning phase angle of the turning scroll is closer to the lap center than the compression chamber opening along the lap.... (3) 』

It turns out that it is a necessary condition for lubricating from the said compression chamber side opening to the outermost outer side engagement position of a turning outer side.

13 and 14 show the turning laps of the turning phase angle satisfying the above requirements, among them, the turning lap of FIG. 13 shows that the compression chamber side opening is open to the turning inner side compression chamber. Lubrication to the outer engagement point is impossible, and it turns out that lubrication to the turning outer line side outermost engagement point is possible for the turning wrap of FIG.

From this, the following can be said.

"The rotational chamber angle is opened to the rotational internal compression chamber by the rotational side angle between 90 degrees front and rear (total 180 degrees) centering on the installation direction angle of the compression chamber opening. (4)"

Here, when the turning phase angle becomes 360 degrees or more, other engagement points are formed on the outside, and the engagement points that have been considered so far disappear at the outermost engagement place.

"The swing phase angle is in the range of 0 degrees to 360 degrees or less. (5) 』

There is also a precondition, and the above (4) and (5) are conditions to be added. In summary, the following can be seen.

"The range of the turning phase angle which can be lubricated from the opening of the compression chamber side to the outermost outer engagement side of the turning chamber is 90 degrees or more than the installation direction angle of the compression chamber opening opening, and the turning phase angle is 360 degrees or less. 6) 』

In view of the above, in the conventional example as shown in Fig. 13, since the installation direction angle of the compression chamber side opening is 210 degrees, the range of the turning phase angle of 300 degrees to 360 degrees, plus 90 degrees to 210 degrees (orbital phase angle interval). You can see that it is possible to refuel.

The turning phase angle interval which can be lubricated by the turning outer side outermost engagement point calculated | required by the past consideration so far showed the turning phase angle interval which the said compression room opening opens upstream rather than the turning outer side outermost engagement point. It is still a necessary condition to be able to be lubricated and is not a sufficient condition.

That is, even if (6) is satisfied, the following exception occurs.

"If the velocity of the oil ejected from the opening of the compression chamber side is small, the ejected oil cannot reach the outermost engagement point while the turning scroll rotates 360 degrees. (7) 』

The flow rate of this oil is determined also by the flow path resistance of the communication path both in the difference between the pressure (back pressure) on the inlet side of the communication path and the pressure on the outlet side.

In the said prior art, since the back pressure valve accompanying a throttle is provided in the said communication path, flow path resistance is large and oil ejection speed becomes small. Therefore, the oil ejected from the compression chamber side opening takes time until it reaches the outermost engagement point, and in fact, the oil supply to the outermost engagement point is rarely performed, even if it is done. In the above description, in the conventional example, it has been described that the oil supply to the outermost engagement point stops for a while from the start of the detention of the compression chamber, but it has been found that there is practically no oil supply to the outermost compression chamber.

By moving the setting position of the compression chamber side opening to the outer circumferential side along the lap, the interval between the rotational phase angle of the outermost engagement portion and the compression chamber opening opening upstream than that can be increased, so as to the outermost engagement position. It may be possible to increase oil supply. However, since the velocity of oil flowing from the compression chamber side opening is suppressed small by the flow path resistance of the back pressure valve, the possibility of substantially increasing the oil supply amount is low.

Although the above description is about the case of a turning outer side compression chamber, even if it is a case of a turning inner side compression chamber, it can be said that it is the same as that mentioned above. Specifically,

"The turning phase angle of the compression chamber side opening which can be lubricated to the turning inner side outermost engagement point becomes the angle relationship which shifted 180 degrees with the turning phase angle interval which can be lubricated to the turning outermost side outer engagement part. (8)"

In addition, for the sake of simplicity, explanation has been made under the condition that "the diameter of the compression chamber side opening is equal to the thickness of the turning wrap", but when "the diameter of the compression chamber opening is smaller than the thickness of the turning wrap", The range of turning phase angles (swinging phase angle intervals) which does not face a real thing occurs. For this reason, it turns out that the turning phase angle space which can be lubricated becomes narrower than the range of the above-mentioned angle, and it turns out that lubrication to the outermost engagement part becomes further smaller.

As mentioned above, in the conventional thing provided with the back pressure valve with a large throttle, and the compression chamber side opening was formed in the fixed tooth root which entered the lap center side (winding start side) rather than the winding end of a fixed lap, It was found that the oil supply to the outermost engagement point was not substantially performed, the sealability of the compression chamber was lowered, and the performance was greatly reduced.

In addition, as shown in FIG. 15, both at the start of the turning inner compression chamber detention and at the start of the turning outer compression chamber detention, at the position of 270 degrees in polar coordinates, the position of the turning lap is the center of the root of the fixed scroll. Comes (in the middle between the laps). From this, it turns out that when the said compression chamber side opening is formed in the position where the polar coordinate is 270 degrees or more (preferably less than 360 degree) in the center of a fixed tooth root, this compression chamber side opening will open only to the compression chamber after a detention start. Can be. Moreover, when the opening position of the said compression chamber side opening shifts from the center of a fixed tooth root, communication of the compression chamber formed with the line of the adjacent fixed wrap and the said compression chamber side opening will become quick. For this reason, in order to open | release both compression chambers only to the compression chamber after a detention start, it is necessary to form the said compression chamber side opening more than 270 degree | times (but less than 360 degree is preferable) in polar coordinates, and near the center of a lap. . As described above, the position where the compression chamber side opening is formed is preferably a position of less than 360 degrees in the polar coordinates.

On the other hand, the communication path having the back pressure valve of the prior art has the compression chamber side opening of about 210 degrees from the end of the fixed wrap winding to the center side (the winding start side) along the root of the fixed wrap (the center of the fixed scroll). It is provided at the position whose direction angle is 210 degree | times in polar coordinate which makes reference point the fixed direction end direction. As described above, this is obviously smaller than 270 degrees which is the minimum value of the angle at which communication with only the compression chamber after the start of detention is always possible. Therefore, at least at some time, the compression chamber side opening is connected to the suction region (suction chamber) communicating with the suction pipe. You can see that you are avoiding.

By the way, since the back pressure chamber is maintained at the back pressure which is an intermediate pressure, the amount of oil which flows through the compression chamber side opening increases so that the pressure of the said compression chamber side opening is low. For this reason, most of the oil which flows through the said compression chamber side opening flows at the time of communication to the suction area | region where the pressure of the said compression chamber side opening becomes the lowest. That is, in the prior art, since most of the oil discharged from the back pressure chamber through the compression chamber side opening enters the suction region, the compression chamber side opening substantially constitutes a flow path communicating only the back pressure chamber and the suction region.

Since oil before flowing into the said back pressure chamber is stored in the discharge space of a scroll compressor, it is high temperature. For this reason, the oil temperature decreases due to the gasification of the working fluid (refrigerant) in the oil due to the reduced pressure when the oil flows from the back pressure chamber into the suction chamber, but the temperature is higher than the suction temperature.

For this reason, in the conventional scroll compressor, the working fluid in the suction region is heated by the high temperature oil flowing from the back pressure chamber and the high temperature working fluid dissolved in the oil to increase the temperature, thereby increasing the cost. The mass of the working fluid introduced into the compression chamber is lowered. On the other hand, the power required for compression increases because the adiabatic index increases due to the increase in suction temperature. In other words, it is also apparent that only a small amount of power is required to increase the compression, and that the overall heat insulation efficiency is lowered (that is, lowering the suction heating performance).

Therefore, in the present Example, the compression chamber side opening of the said communication path which has a back pressure valve is made to communicate only to the compression chamber after completion | finish of detention, and to open it to the position which does not communicate with the suction area | region (suction chamber). In addition, an oil supply passage (suction area communication path) of another system communicating only with the suction area is further provided, and the suction area communication path has an intermittent oil supply structure in which oil supply is intermittently performed, so that oil supply to the suction area is required at least. It was possible to make it.

Hereinafter, specific embodiments of the present invention will be described based on FIGS. 1 to 12.

[First Embodiment]

A first embodiment of the present invention will be described with reference to Figs. Fig. 1 is a longitudinal sectional view showing the scroll compressor of the present embodiment, Fig. 2 is a bottom view of the fixed scroll shown in Fig. 1 from below, and (a) also includes a turning scroll wrap at the start of detention of the swing outer compression chamber. Fig. 3 (b) also includes a swing scroll wrap at the start of detention of the swinging inner compression chamber. Fig. 3 is a cross-sectional view taken along the line III-III of the fixed scroll shown in Fig. 2, illustrating the structure near the back pressure valve. Fig. 4 is a top view of the swing scroll shown in Fig. 1 from above, Fig. 5 is a sectional view taken along line VV of the swing scroll shown in Fig. 4, and Fig. 6 is a partially enlarged view showing an enlarged Q portion of Fig. 2. The enlarged view of the fixed hard board surface near the suction pipe. In this embodiment, the diameter of the compressor is about 10 mm to 1000 mm.

First, the whole structure of a scroll compressor is demonstrated mainly using FIG.

The scroll compressor 1 shown in FIG. 1 is provided with the fixed scroll 2 and the turning scroll 3, and the fixed scroll 2 has a fixed scroll wrap (fixed wrap) which uses a circular involute as a section line. (2b) is mounted upright on the fixed scroll plate (fixed plate) 2a, and the above-mentioned orbiting scroll 3 is similarly orbiting orbiting scroll wrap (orbiting wrap) 3b having a circular involute as a section line. The compression chamber 100 is formed between them by standing up on the scroll hard plate (swivel hard plate) 3a and engaging these fixed scrolls 2 with the revolving scroll 3.

These wraps generally have the same thickness. Further, in a symmetrical scroll compressor in which the fixed wrap and the swing wrap have symmetrical releases of the same shape, the swing wrap compression chamber formed on the outside of the swing wrap 3b and the inside of the swing wrap 3b are formed. The turning inner side compression chamber used becomes the same shape.

On the other hand, there is also a so-called asymmetrical scroll compressor in which both side surfaces of the winding end 3 of the swinging scroll 3 are engaged with the fixed wrap 2b of the fixed scroll 2. In this asymmetric type scroll compressor, the stationary side winding-up end, which is the end of winding of the extension line of the fixed scroll 2, is the stationary side winding-up end α in the symmetrical release of the above-described symmetrical scroll compressor (see Fig. 2). ) Is moved to the position of β (see FIG. 2). This is a position where the involute winding angle is rotated by 180 degrees, and the outer side fixed winding end γ and the fixed wrap are positioned to face each other by sandwiching the grooves.

The fixed scroll 2 is screwed to the frame 4 on the lower surface (fixed hard plate surface 2u) of the hard plate outer side portion 2d of the fixed wrap 2b. On the other hand, the crankshaft 6 in which the swivel scroll 3 is inserted into the slewing bearing 23 provided on the back surface of the hard plate, and the eccentric pin part 6a of the crankshaft 6 is rotated and supported by the main bearing 24, It is configured to rotate by the rotation of the. The back pressure chamber 110 is formed on the rear surface of the revolving scroll 3 together with the frame 4.

In order to make the swinging scroll 3 rotate without rotating, the Oldham ring 5 is provided between the swinging scroll 3 and the frame 4. The back pressure which is the pressure of the said back pressure chamber 110 is maintained at the intermediate pressure between a discharge pressure and a suction pressure by the function mentioned later. Moreover, since the oil of discharge pressure is supplied from the oil storage part 125 of the lower part of the casing 8 which becomes the space of discharge pressure, the slewing bearing chamber 115 in which the slewing bearing 23 is provided is discharged | emitted by the discharge pressure. It is. Therefore, the revolving scroll 3 is pressed toward the fixed scroll 2 side by the back pressure of the back pressure chamber 110 and the discharge pressure of the revolving bearing chamber 115, that is, the revolving hard plate 3a is fixed to the fixed plate surface 2u. Pressurized by).

A suction pipe 50 is press-fitted and connected to the suction hole 2y formed in the fixed scroll 2 to guide a working fluid such as a refrigerant to the compression chamber 100. In addition, a check valve 70 is provided below the suction pipe 50 in order to prevent the working fluid from flowing back immediately after the compressor is stopped. In addition, a discharge hole 2f for discharging the working fluid compressed in the compression chamber 100 is formed near the center of the fixed scroll 2. A plurality of bypass holes 2e (see Figs. 1 and 2) are formed in the fixed hard plate 2a on the outer circumferential side of the discharge hole 2f, and each bypass hole 2e includes a bypass valve ( An overcompression prevention valve or release valve) 22 is provided, and if the pressure of the compression chamber 100 through which the bypass hole is communicated rises above the pressure of the fixed rear chamber 120, the bypass valve ( 22) is opened to prevent overpressurization of the working fluid.

The oil supply hole 6b which penetrates longitudinally (axial direction) is formed in the center of the crankshaft 6, and the oil of discharge pressure from the said oil storage part 125 is provided in the lower end part of the crankshaft 6; The oil supply pipe 6x and the oil supply hole 6b are supplied to the swing bearing chamber 115 through oil supply passages. In order to balance rotation of the crankshaft 6, a shaft balance 80 and a counter balance 82 are provided below the frame 4. The counter balance 82 is fixed to the lower portion of the rotor 7a of the motor 7 provided by shrink fit or press fitting to the crankshaft 6. The stator 7b of the motor 7 is fixed by shrink fit or press fit into the cylindrical casing 8a, so that the stator 7b and the rotor 7a maintain a uniform gap in the radial direction. (4) is tack-welded to the cylindrical casing 8a.

A discharge pipe 55 is provided on the side surface of the cylindrical casing 8a so as to communicate with the upper part of the motor chamber in the casing 8, and the working fluid discharged from the discharge hole 2f to the fixed rear chamber 120 is The oil flows into the motor chamber under the frame 4 to separate oil, and is discharged from the discharge pipe 55 in a refrigerating cycle or the like. A lower frame 35 for fixing the lower bearing 25 supporting the lower portion of the crankshaft 6 is fixed to the lower portion of the cylindrical casing 8a. The sub-bearing 25 is composed of a ball 25a and a ball holder 25b, and is configured such that one-sided contact does not occur even when the crankshaft 6 is bent. The ball holder 25b is fixedly arranged to the lower frame 35 by screwing or welding. Moreover, the said oil supply pipe 6x is press-fitted in the lower end part of the crankshaft 6, and is provided.

The upper casing 8b is welded to the upper part of the cylindrical casing 8a, and the bottom casing 8c is welded to the lower part, and the hermetic casing 8 is comprised. In addition, the upper casing 8b is provided with a hermetic terminal 220 that connects a motor line for supplying electric power to the motor 7 by welding, and the suction pipe that is press-fitted into the fixed scroll 2 ( 50 is also welded to this upper casing 8b. The casing 8 is filled with oil at an appropriate stage of assembly, and the oil is formed between the bottom casing 8c of the casing 8 and the lower frame 35. It is stored in. In addition, the fixed rear chamber 120 is formed between the upper casing 8b and the fixed scroll 2. In this way, the scroll compressor 1 is configured.

Next, the operation of the scroll compressor will be described. When the crankshaft 6 is rotated by the motor 7, the turning scroll 3 rotates. Thereby, the working fluid sucked from the suction pipe 50 passes through the suction region 105 (see FIG. 2) of the suction pressure and is formed by the engagement of the fixed scroll 2 and the swinging scroll 3 ( 100). The working fluid introduced into the compression chamber 100 is compressed by shrinking as the compression chamber moves to the center, and is discharged from the discharge hole 2f near the center to the fixed rear chamber 120 which is the upper space in the casing 8. The space (motor chamber) in which the fixed rear chamber 120 and the motor 7 are installed is communicated by the outer circumferential groove 71 formed on the outer circumferential surface of the fixed scroll 2 and the frame 4, thereby providing a casing ( 8) The inside is a discharge area maintained at the discharge pressure, and the scroll compressor shown in FIG. 1 is a so-called high pressure chamber scroll compressor.

In an overcompression condition in which the pressure in the compression chamber 100 becomes higher than the pressure in the fixed rear chamber 120, the valve body of the bypass valve 22 is opened, and the working fluid in the compression chamber is bypassed to the fixed rear chamber 120. Bypass is made through the pass hole 2e. That is, the bypass valve 22 is a compression chamber pressure restraining means. Thereby, since overcompression which is unnecessary work can be suppressed, performance can be improved more.

The working fluid which flows out into the fixed rear chamber 120 passes through the fixed scroll 2 and the outer circumferential groove 71 of the frame 4, and then flows into the upper space of the motor 7, and discharge pipe 55. From the outside. When the oil contained in the working fluid is discharged to the fixed rear chamber 120, the oil collides with the inner wall of the casing, and the separated oil rides through the inner wall of the casing, and finally, the oil reservoir of the compressor bottom ( Return to 125).

A part of the working fluid introduced into the upper space of the motor 7 is discharged reciprocally between the lower space of the motor 7 through the outer circumferential groove of the motor 7 or the winding gap. As a result, oil easily adheres to the windings of the stator 7b and the laminated steel plate of the motor, thereby facilitating separation of oil in the working fluid. The oil stored in the oil reservoir 125 is lubricated in the oil supply pipe 6x and the crankshaft 6 by the pressure difference between the pressure (discharge pressure) in the motor chamber and the pressure (back pressure) in the back pressure chamber 110. After oil is supplied to the slewing bearing 23 and the main bearing 24 through an oil supply path such as the hole 6b, it is introduced into the back pressure chamber 110. Since the upper part of the pin part 6a becomes the turning bearing chamber 115 to which discharge pressure is applied, the turning bearing chamber 115 has an effect which pulls the turning scroll 3 toward the fixed scroll 2 side by discharge pressure. In addition, the back pressure chamber 110 also has a function of pulling the swing scroll 3 toward the fixed scroll 2 side by the back pressure. These back pressure chamber 110 and the revolving bearing chamber 115 serve as attracting force adding means for attracting the fixed scroll 2 and the revolving scroll 3.

In addition, the sub-bearing 25 is fed with centrifugal force from the oil supply hole 6b.

The oil flowing into the back pressure chamber 110 has a pressure close to the discharge pressure, and has a function of boosting the pressure in the back pressure chamber 110. In addition, when the working fluid dissolved in the oil flows into the medium pressure back pressure chamber 110, it is gasified by the reduced pressure, there is also a pressure raising action of the back pressure chamber 110 accompanying this. The oil flowing into the back pressure chamber 110 also performs lubrication of the Oldham ring 5. Thereafter, the oil is introduced into the compression chamber 100 through the compression chamber communication path 60 (see FIG. 3) and the suction region communication path 65 (see FIG. 6) described later, and mixed with the working fluid. In this way, the back pressure is maintained at an intermediate pressure.

Next, the structure used as a main part in a present Example is demonstrated in detail using FIGS.

As shown in FIG. 2, the fixed scroll 2 is provided with the compression chamber communication path 60 which communicates the compression chamber 100 and the back pressure chamber 110. As shown in FIG. This compression chamber communication path has a c-shape as shown in FIG. In order to form this U-shaped passage, it can be realized by sealing an unnecessary portion as a passage after drilling the through hole (see the sealing portion 61).

The compression chamber communication path 60 may be formed as an inclined hole type communication path as shown by the two-dot chain line in FIG. 3, in which case the compression chamber side opening 60a of the compression chamber communication path 60 is an ellipse. However, since the compression chamber communication path 60 does not need to be formed in a U-shape, and the sealing treatment (sealing portion 61) after the through hole is no longer necessary, processing can be made easier.

Since the compression chamber side opening 60a of the said compression chamber communication path 60 is made to open to the center of the root of a fixed scroll as shown in FIG. 2, the turning outer line which is the turning wrap outer side compression chamber of the turning scroll 3 is shown. It is comprised so that communication is possible with both the compression chambers of the side compression chamber 100a and the turning internal compression chamber 100b which is an internal compression chamber.

In this embodiment, the winding end (extension extension fixing winding end) of the fixed wrap 2b extension line of the fixed scroll 2 in which the said compression chamber side opening 60a was formed is conventionally released (revolutionary extension compression chamber and turning outer line). The position where the side compression chamber extended by 180 degrees at the involute winding angle than the fixed lap extension winding end position (extension side fixed winding end) (alpha) (refer FIG. β) (refer FIG. 2 (a)) is made into what is called asymmetrical release which set the fixed side winding end. For this reason, unlike the conventional symmetrical release, the pressure level of the turning outer line side compression chamber 100a and the turning line side compression chamber 100b which communicates with the compression chamber side opening 60a can be made substantially the same. Therefore, the pressure fluctuation range of the said back pressure chamber 110 which communicates with these compression chambers 100a, 100b can also be made small.

The compression chamber side opening 60a is set to a size slightly smaller than the width of the turning wrap 3b, and is set to a size such that the entire compression chamber side opening 60a can be blocked by the turning wrap 3b. For this reason, the compression chamber communication path 60 generates a short time but a closed time, and the back pressure chamber 110 communicates with the compression chambers 100a and 100b at respective timings. Thereby, since the fixed inner side compression chamber 100a and the fixed outer side compression chamber 100b which differ in pressure level do not communicate with each other through the compression chamber communication path 60, from a high pressure side compression chamber to a low pressure side compression chamber. Leakage is unlikely to occur, and leakage loss is suppressed, so that the energy efficiency can be improved. In addition, since the diameter of the compression chamber side opening 60a is made as large as possible, the flow path resistance of the compression chamber communication path 60 becomes small, so that even when a large flow rate flows, the pressure in the back pressure chamber can be quickly set to a desired value. It works. Moreover, since this compression chamber communication path 60 becomes an intermittent communication path which closes twice or twice during one turn, it makes the notch of the opening of the back pressure valve installed in this communication path mentioned later, and ensures the operation of a back pressure valve. Thus, there is an effect of avoiding abnormal rise in back pressure.

In the present embodiment, in the above-described polar coordinates in which the position of the compression chamber side opening 60a is formed as the fixed scroll center as the origin and the reference direction is the fixed winding end direction, the fixed tooth is fixed from the end of the winding of the fixed wrap. It is set to the place where 270 degrees or more entered to the center side (winding start side) along the edge. The effect by this structure is demonstrated below.

Considering the movement of the turning lap at the time shown in FIG. 2 (a), the fixed tooth root of the compression chamber side opening 60a which is not opened to the turning outer side compression chamber 100a (suction area) before the start of detention is taken into account. The setting position on the image is at least an area indicated by hatching in (a). In addition, hatching is abbreviate | omitted since the polar coordinate is 360 degree or more, since it does not open to a suction area no matter where the compression chamber side opening 60a is formed. Similarly, the installation position on the fixed tooth root of the compression chamber side opening 60a which is not opened to the turning inner compression side compression chamber 100b (suction area) before the start of detention at the time shown in FIG. 2 (b). Also, at least the area indicated by hatching in (b) is obtained. When the compression chamber side opening 60a is formed in a region (a common portion indicated by hatching of (a) and (b)) indicated by cross hatching in (b), the compression chamber communication path 60 is always in the compression chamber after the end of detention. Can only communicate. In the present embodiment in which the compression chamber side opening 60a having a diameter close to the lap thickness is formed in the center of the fixed tooth root, the area where the compression chamber side opening 60a does not communicate with the suction area near the center of the fixed tooth root (cross hatching) The width of the part) must be at least as large as the wrap thickness. It turns out that the location which meets this condition will become a position 270 degree or more in the said polar coordinate from the distribution of this cross hatching area | region.

Accordingly, by forming the compressor-side opening 60a at a position of 270 degrees or more in the polar coordinates near the center of the fixed tooth root, the compression chamber communication path 60 is always wound at the end of the winding wrap 3b. It can be opened only in the compression chambers 100a and 100b which are the space after completion of the detention after contact with 2b), and never communicates with the suction space (the suction chamber formed between the wraps) which communicates with the suction area 105. can do. As a result, it is possible to prevent the high temperature oil (including the working fluid) from the back pressure chamber 110 from flowing into the suction region 105, so that the decrease in suction heating performance can be suppressed, thereby improving energy efficiency. It becomes possible to plan.

The back pressure chamber side opening 60b which is the other opening part of the said compression chamber communication path 60 is a recessed part which communicates with the circumferential groove 2p of the circumferential direction formed in the fixed hardplate surface 2u of the fixed scroll 2. It is open to (2p1). For this reason, the back pressure chamber side opening 60b is always in communication with the back pressure chamber 110.

Moreover, as shown in FIG. 3, the back pressure valve 26 accompanying a throttle is provided in the middle of the said compression chamber communication path 60. As shown in FIG. The structure of this back pressure valve 26 is demonstrated below.

The valve hole 2k is formed in the fixed scroll 2 of the position which communicates in the middle of the said compression chamber communication path 60 from the upper surface side, and the valve seal surface (valve seat) is provided in the bottom of this valve hole 2k. Install (26d). The valve body 26a is pressed by the valve spring 26b to this valve seal surface 26d. The valve spring 26b is held by the valve cap 25c. This valve cap 26c is also in charge of the function of sealing with the fixed rear chamber 120. The operation of the back pressure valve 26 configured as described above will be described. The differential pressure of the back pressure (pressure on the back pressure chamber side) and the pressure on the compression chamber side facing the compression chamber side opening 60a acts on the valve body 26a of the back pressure valve 26, and a force is applied to the valve spring 26b by the pressure difference. When the pressing force is exceeded, the valve body 26a is spaced apart from the valve seal surface 26d to open the compression chamber communication path 60. The back pressure is set higher by a value corresponding to the pressing force of the valve spring 26b than the pressure in the compression chamber that the compression chamber side opening 60a faces.

Since the scroll compressor of this embodiment adopts asymmetrical release, the pressure level of the swinging outer side compression chamber 100a and the swinging inner side compression chamber 100b communicating with the compression chamber side opening 60a becomes almost the same. Moreover, since the range of the turning phase angle which communicates with each compression chamber 100a or 100b also becomes small, the pressure fluctuation range also becomes small. As a result, since the fluctuation | variation of the back pressure set by the back pressure valve 26 becomes small, the fluctuation | variation of the force which presses a turning scroll with a fixed scroll is suppressed. Therefore, since the variation of the deformation of each scroll occurring with this variation of the pressing force is suppressed, the variation of the gap between both scrolls is reduced, the oil retention in the gap is improved, the sealing property is improved, and the leakage loss is improved. Reduction can be aimed at. Moreover, the reduction of the friction loss by suppressing the interference between laps is also added, and the effect which can improve energy efficiency is acquired.

In addition, since the bypass valve 22 is provided, the synergistic effect allows the swing scroll to be pressed with a fixed scroll in the entire operating range required for the scroll compressor, and the pressing force can be applied in a wide range of operating conditions. Since it becomes possible to make it small, there is an effect that a sliding compressor is small and energy-efficient scroll compressor can be realized.

As described above, it is possible to avoid the deterioration of suction heating performance by preventing the high temperature oil from flowing into the suction region 105 from the back pressure chamber 110, but if no oil is supplied to the suction region 105 at all, the compression chamber The sealing property is lowered, and conversely, a decrease in energy efficiency occurs. However, when put in the inside of the compression chamber before initiation of detention in the said suction area | region 105, there is little effect which can improve sealing property. Compression is performed by supplying the suction area communication path 65 to the suction area 105 by a configuration in which the back pressure chamber 110 and the suction area 105 are connected and the oil supply point and the oil supply amount are optimized. It is possible to realize a scroll compressor which hardly causes a decrease in suction heating performance while improving the sealability of the seal 100.

In order to realize this, in this embodiment, the suction area communication path 65 is configured as shown in Figs. That is, the suction area communication passage 65 has a small diameter swing light plate oil supply hole 65a (see Figs. 4 and 5) for passing the swing light plate 3a from the back pressure chamber 110 side to the fixed light plate surface 2u side. And a fixed platen oil supply groove 65b (FIG. 6) formed on the fixed platen surface 2u and connecting the suction area 105 with a position capable of communicating with the pivotal plate oil supply hole 65a. It is. The suction side opening 65x, which is an opening on the suction area 105 side of the suction area communication passage 65 (an opening on the suction area 105 side of the fixed plate oil feed groove 65b), is removed from the suction pipe 50. It is formed in the flow path of the working fluid to the compression chamber 100 (suction region 105).

The upper surface side opening part (fixed hard plate surface side opening part) 65a '(refer FIG. 5) of the said turning hard board oil supply hole 65a is accompanied with the turning motion of the turning scroll 2, and as shown in the trace in FIG. It overlaps with the said fixed plate oil supply groove | channel 65b in two places. Therefore, the suction area communication path 65 becomes an intermittent communication path that communicates with the suction area 105 side twice while the swing scroll 3 is turning one time. The opening timing can be adjusted in the direction of formation of the fixed platelet oil-filling groove 65b which is formed to intersect the trajectory of the swing plate plate oil-feeding hole 65a.

In this embodiment, the formation direction of the part of the fixed platen oil-feeding groove 65b that intersects the trajectory of the turning platen oil supply hole 65a is substantially parallel to the straight line connecting the two fixed winding ends β and γ. Since it is set in the direction, the suction area communication path 65 can be opened to the suction area 105 for a predetermined time at the time when the two compression chambers respectively start the detention. Therefore, since the oil is supplied when the outermost engagement point is generated and the seal is required, it is possible to seal the outermost engagement point with a smaller amount of oil supply.

In addition, it has been found from the experiment that the proper flow rate supplied from the suction region communication passage 65 to the suction region 105 improves the energy efficiency by 1% or more by making it about 1 to 5% of the working fluid flow rate. . The flow rate which flows into the back pressure chamber 110 is a range of approximately equal level from 20% of the flow volume of the actuator which a compressor sends out. From this, even if the flow rate flowing into the back pressure chamber is the smallest with 20% of the working fluid, and the flow rate of the suction area communication path 65 is most required with 5% of the working fluid amount, among the flow rates flowing into the back pressure chamber. What is necessary is just to flow 25% which is the ratio of 5/20 to the suction area communication path. Since 25% is the highest ratio among the flow rates flowing into the suction area among the flow rates flowing into the back pressure chamber, the flow rate flowing from the suction area communication path 65 to the suction area is at least the compression chamber communication path ( It turns out that energy efficiency can be improved further by making it smaller than the flow volume which flows from 60) to the compression chamber side. In practice, in most cases, the highest energy efficiency can be obtained by flowing about 1 to 10% of the oil flowing into the back pressure chamber through the suction region communication path 65. That is, according to this embodiment, it becomes possible to reduce the inflow flow volume into the suction region 105 to the minimum required amount as much as possible, thereby suppressing the deterioration of the suction heating performance, and from the compression chamber at the outermost engagement point. Since leakage to the suction region can be suppressed, there is an effect that a scroll compressor with high energy efficiency can be realized.

Moreover, the direction of formation of the part of the fixed plate | board oil supply groove | channel 65b which intersects the trajectory of the turning plate plate oil supply hole 65a is clockwise from the direction substantially parallel to the straight line which connects the said 2 fixed winding ends ((beta), (gamma)). By slightly shifting in the direction, the oil supply starting point to the suction region 105 can be made relatively quick with respect to the arresting starting point of the compression chamber. By doing in this way, the oil velocity ejected is small, and the time required to pass through the fixed slab lubrication groove 65b is long, and it is effective in such a case. In addition, the flow rate can also be increased by means such as increasing the depth of the fixed platen oil lubrication groove 65b, increasing the width, or increasing the diameter of the swing plate plate oil supply hole 65a.

The oil in the working fluid discharged from the discharge hole 2f to the discharge region in the casing 8 is mostly separated in the casing 8 and returned to the oil reservoir 125, but part of the oil is not separated. Together with the fluid, it is discharged from the discharge pipe 55 to the outside (freezing cycle). Since the oil discharged to the outside circulates through the refrigerating cycle, and finally returns to the scroll compressor 1 from the suction pipe 50 again, it serves to replenish the oil supply by the suction area communication passage 65. However, when oil is discharged to the outside of the scroll compressor, in order to reduce the performance of the refrigeration cycle apparatus in which the compressor is mounted, it is usual to take measures to reduce the oil discharged to the outside from the compressor as much as possible under the rated conditions. Therefore, this embodiment, which enables the minimum required oil supply to the suction region 105, is extremely effective since a scroll compressor with high energy efficiency is obtained.

[Second Embodiment]

Next, a second embodiment of the scroll compressor of the present invention will be described with reference to FIG. This embodiment is configured to adjust the oil supply amount from the back pressure chamber to the suction region by providing an external drive throttle valve in the suction region communication path and controlling the external drive throttle valve. Other configurations are basically the same as those of the first embodiment described above, and thus redundant descriptions are omitted.

This second embodiment will be described in more detail. The suction area communication path 65 'in the present embodiment is a suction area within the back pressure chamber 110 of the scroll compressor 1 and the flow path of the working fluid from the suction pipe 50 to the compression chamber 100 ( Outside which is provided so that the suction hole 2y of 105 may be communicated, and the opening degree can be controlled by the control apparatus 65g provided in the exterior of the scroll compressor 1 in the middle of this suction area | region communication path 65 '. A drive throttle valve (flow control valve) 65c is arranged.

The suction region communication passage 65 ′ has a back pressure side suction region communication hole 65d communicating the throttle valve 65c and the back pressure chamber 110, the throttle valve 65c, and the suction region 105. In the present embodiment, in the throttle valve 65c constituted by the suction side suction region communication holes 65e communicating with each other, the throttle valve 65c disposed between these communication holes 65d and 65e is provided. For example, a sensor for sensing the suction pressure Ps and the discharge pressure Pd is incorporated. That is, a suction pressure detection sensor (not shown) for detecting the suction pressure Ps is provided on the suction side suction region communication hole 65e side of the throttle valve 65c, and the throttle valve 65c is provided. In the part facing the fixed rear chamber 120, the discharge pressure detection sensor (not shown) for detecting discharge pressure Pd is provided.

The throttle valve 65c and the control device 65g are connected by a transmission path 65f, and the throttle valve 65c is controlled by the control device 65g via the transmission path 65f. The driving power is supplied from the control device 65g to the throttle valve 65c. Moreover, the signal from the said suction pressure detection sensor or the discharge pressure detection sensor provided in the throttle valve 65c is also introduce | transduced into the control apparatus 65g via the said transmission path 65f.

In the control device 65g, a control program for controlling the throttle valve 65c is stored, and according to the program, for example, the pressure is changed depending on the situation such as the pressure ratio Pd / Ps in the compressor. If the ratio is large, the throttle valve 65c can be controlled to increase the oil supply amount, and if the pressure ratio is small, the opening degree of the throttle valve 65c can be controlled to decrease the oil supply amount, so that the suction region 105 can be controlled. Fine oil supply can be adjusted, and the minimum required oil supply can be realized in a wide range of operating conditions by the outermost engagement point. As a result, it is possible to suppress the suction heating performance deterioration to the maximum in a wide range of operation without impairing the sealability of the outermost engagement point. Thus, an effect of obtaining a scroll compressor with extremely high energy efficiency over a wide range of operation is obtained. have.

Although the above-described pressure detection sensor has been described as a pressure sensor that directly detects the pressure, the pressure sensor is generally expensive, so that the suction pressure Ps or the discharge pressure Pd are estimated based on the information related to the pressure. You may also For example, instead of the discharge pressure detection sensor, a sensor for detecting the suction temperature and the discharge temperature of the compressor may be assembled, and the discharge pressure Pd may be estimated by combining the data and the suction pressure data from them. Moreover, the data which can grasp | ascertain the compressor operation state, such as a pressure and temperature, is acquired from the refrigeration cycle apparatus which mounts the scroll compressor 1, etc. by the external signal line 65s shown by the dashed-dotted line in FIG. The suction pressure Ps and the discharge pressure Pd of the compressor may be estimated from the data. In this case, there is no need to assemble a pressure sensor or a temperature sensor in the compressor, and the manufacturing cost can be further reduced.

Third Embodiment

A third embodiment of the scroll compressor of the present invention will be described with reference to Figs. Fig. 8 is a top view of the revolving scroll in the present embodiment, Fig. 9 is a longitudinal sectional view of the revolving scroll in Fig. 8, IX-IX cross-sectional view in Fig. 8, and Fig. 10 are fixed hard plates of the fixed scroll in this embodiment. It is an enlarged view of the vicinity of the suction pipe in a surface, and is a figure corresponded to Q part of FIG. In this third embodiment, the same reference numerals as those in the first embodiment indicate the same or corresponding parts.

In this third embodiment, instead of the swinging slab lubrication hole 65a in the first embodiment, the swinging slab lubrication recess (concave portion) 65A is a swinging slab in the swinging scroll 3 ( It is formed in the position opposite to the said fixed hard board surface 2u of 3a). Moreover, on the fixed hard plate surface 2u of the fixed scroll 2, the position which can communicate with the said turning flat plate oil supply recessed part 65A, and the fixed hard plate oil supply groove 65B which connects the said suction area | region 105 in circular arc shape are shown. Formed. In addition, a fixed hard plate recess 65C is formed in the fixed hard plate surface 2u so as to communicate with the peripheral grooves 2p formed in the fixed scroll 2. Other points are the same as in the first embodiment, and thus redundant descriptions are omitted.

As shown in the trajectory of FIG. 10, the pivotal plate oil supply recessed portion 65A is fixed plate plate recessed portion 65C connected to the peripheral groove 2p of the fixed scroll 2 facing the back pressure chamber 110. ) And the fixed plate oil supply groove 65B. By configuring the suction area communication path 65 ″ in this manner, the suction area communication path 65 sucks oil stored in the swing hard plate oil supply recess 65A every time the swing scroll 3 is turned. It can be set as the intermittent oil supply path which can supply oil to 105 once.

Therefore, in this embodiment, since the oil supply amount changes according to the volume of the oil supply recessed portion 65A, when the oil supply amount is to be increased, the volume of the oil supply recessed portion 65A is increased and the oil supply amount is reduced. If desired, the volume of the oil supply recessed portion 65A may be reduced. The volume of the oil supply recessed portion 65A can be easily produced to a desired volume by changing the depth or diameter of the recessed portion. It is not necessary to make the width 65b narrow so as to increase the throttle amount, and there is no change in the oil supply amount even when the pressure difference between the back pressure chamber and the suction region changes. As a result, it is possible to easily set a very small amount of oil supply amount with high accuracy, and the manufacturability is particularly improved. In addition, according to the present embodiment, since it is not necessary to narrow the turning platen oil supply hole 65a or narrow the width of the fixed platen oil supply groove 65b as in the first embodiment, the suction area communication path 65 ". C) can also be avoided and reliability can be improved.

In addition, in this embodiment, since it is comprised so that one time of intermittent oil supply may be performed while the turning scroll 3 makes one turn, it cannot supply oil according to the detention of a compression chamber like 1st embodiment. As a result, it is possible to extend the fixed hard disk oil feed groove 65B to increase the flow path resistance of the suction area communication path 65 ″, and to reduce the intermittent flow of oil to achieve leveling of the oil supply. The sealing property in the outermost engagement part of the two compression chambers formed in the inner peripheral side and the outer peripheral side in (3b) can be improved with a small amount of oil.

In addition, even when the oil supply by the intermittent bucket relay system by the oil supply recessed part 65A provided in the revolving scroll was used like this embodiment, the said fixed platen recessed part 65C and the turning platen oil supply recessed part 65A. ), The shape or number of the fixed platelet recesses 65C is set so that communication between the two ends occurs in one turn, and the fixed platelet oil feeding groove 65B and the pivot plate plate oiling recess 65B are formed between the respective communication lines. If the fixed slab oil lubrication groove 65B is configured so as to generate communication with each other, the oil can be lubricated in accordance with the detention of the compression chamber. Moreover, two pivoting slab oil supply recesses 65A are radially arranged so that the said fixed slab oil supply groove | channel 65B may be fitted, and each pivoting slab oil supply recess 65A accompanies the pivoting motion of a revolution scroll, If the fixed plate plate recessed portion 65C and the fixed plate plate oil feed groove 65B are configured to communicate at each timing, the oil supply amount can be further reduced while ensuring the sealability at the outermost engagement point.

According to this embodiment, since the amount of oil flowing into the suction region 105 can be set to the minimum necessary and with high precision, there is an effect of further reducing the decrease in suction heating performance.

[Fourth Embodiment]

A fourth embodiment of the scroll compressor of the present invention will be described with reference to FIGS. 11 and 12. FIG. 11 is a bottom view of the fixed scroll in the present embodiment, in which the outer compression chamber of the swing wrap overlaps the swing scroll wrap at the start of detention; FIG. 12 shows the back pressure valve of the fixed scroll shown in FIG. It is a longitudinal cross-sectional view explaining the structure of the compression chamber communication path which has, and is sectional drawing XII-XII of FIG. Also in this fourth embodiment, the same reference numerals as those in the first embodiment indicate the same or corresponding parts.

This fourth embodiment makes the compression chamber side opening 60a of the compression chamber communication path 60 in the first embodiment radially outward from the center of the root of the fixed wrap 2b, and also the polar coordinates described above. The second embodiment is different from the first embodiment in that it is provided at a position of 290 degrees, and the rest of the description is the same as that of the first embodiment, and thus redundant description is omitted.

When the compression chamber side opening 60a is radially outward from the center of the root of the fixed wrap 2b, as apparent from the cross hatching portion shown in Fig. 2B at the position 270 degrees in polar coordinates, The swing outer side compression chamber 100a communicates with the suction region before the start of detention. In order to avoid this, in the present embodiment, the compression chamber side opening 60a is moved to a position of 290 degrees (part of cross hatching shown in Fig. 2B) in polar coordinates. With this configuration, the same effects as those in the first embodiment can be obtained, and the amount of oil supply to the swinging outer side compression chamber 100a in the oil supply to the compression chamber 100 by the compression chamber communication path 60 is the swing extension. It can be made larger than the oil supply amount to the side compression chamber 100b.

In addition, in this embodiment, although the installation position of the said compression chamber side opening 60a was made into the position of 290 degree | times in polar coordinates, this is not limited to 290 degree | times, It should just be a position which communicates only to the compression chamber after the start of detention at the position larger than 270 degree | times. .

In this embodiment, since it consists of an asymmetric type scroll compressor, the turning outer side compression chamber 100a often has a higher pressure than the turning inner side compression chamber 100b arrange | positioned around it, and the tip and tooth root of a lap are many. It often becomes the upstream side of the leakage flow in the gap between them. In this embodiment, since the amount of oil supply to the turning outer side compression chamber 100a which is often the upstream side of the leakage flow in the distance between the tip of the lap and the tooth root is increased, the tip and the root of the lap are increased. By the leakage flow in the space | interval between them, a large amount of oil can be supplied to the clearance gap between the tip of a lap and the root | root, and the sealing property of the part can be improved. Therefore, the leakage can be further reduced, and the energy efficiency can be further improved.

In addition, when the lap thickness is very large or the gap between the tip of the lap and the root is very small, and the leakage between the tip of the lap and the root is extremely small, the compression chamber opening 60a is fixed. It is good to make it move to the inner peripheral side of a lap rather than a center of a li. With this configuration, the amount of oil supply to the swinging inner compression chamber 100b can be increased, so that the pressure in the swinging inner compression chamber 100b can be further increased by the working fluid dissolved in the oil. For this reason, it becomes possible to compensate for the fall of the volume ratio of the turning inner side compression chamber 100b coming from a lap shape, and to raise the pressure ratio of the turning inner side compression chamber 100b. As a result, it is possible to bring the pressure ratio of the swinging inner compression chamber 100b closer to the pressure ratio of the swinging outer compression chamber 100a, and to reduce the pressure difference between the two compression chambers when discharging the working fluid from the discharge port 2f. Since it can do this, there exists an effect which can suppress the pressure pulsation of the working fluid to discharge.

As described above, according to each of the above embodiments of the present invention, in addition to the compression chamber communication path, the suction area communication path is provided, so that lubrication can be performed at the outermost engagement portion that is the seal portion of the suction area and the compression chamber, The leakage from the compression chamber to the suction region can be suppressed, and a scroll compressor with high energy efficiency can be obtained.

In addition, since the compression chamber communication path communicates only with the compression chamber after the detention start, and the oil supply to the area suction area is performed only in the suction area communication path, high temperature oil from the back pressure chamber is required for the suction area. It becomes possible to flow by the amount of, and thereby the suction heating performance deterioration can be suppressed.

Thus, according to this embodiment, since the fall of the sealing property at the outermost engagement part of a fixed scroll and a turning scroll can be prevented, heating of the working fluid in a suction area can also be suppressed, and therefore scroll with high energy efficiency It is effective to obtain a compressor.

1: scroll compressor
2: Fixed scroll
2a: fixed slab
2b: fixed scroll wrap (fixed wrap)
2d: hardboard edge
2e: bypass hole
2f: discharge hole
2k: valve hole
2p: home around
2p1: recess
2U: fixed hardwood surface
2y: suction hole
3: turning scroll
3a: slewing slab
3b: Turning Scroll Lap
4: Frame
5: Oldham Ring
6: crankshaft
6a: eccentric pin
6b: oil supply hole
6x: Refueling Pipe
7: motor (7a: rotor, 7b: stator)
8: casing (8a: cylindrical casing, 8b: upper casing, 8c: bottom casing)
22: bypass valve
23: slewing bearing
24: main bearing
25: vice bearing
26: back pressure valve
26a: valve body
26b: valve spring
26c: Valve Cap
26d: Valve seal surface (valve seat)
35: lower frame
50: suction pipe
55: discharge pipe
60: compression chamber communication path
60a: compression chamber opening
60b: back pressure chamber opening
61: sealing part
65, 65 ', 65 ": suction area communication path
65a: slewing plate refueling hole
65a ': upper surface side opening part (fixed hard plate surface side opening part)
65b: Fixed Slab Lubrication Groove
65c: externally driven throttle valve (flow control valve)
65d: back pressure side suction area communication hole
65e: suction side suction area communication hole
65f: transmission path
65g: control unit
65s: external signal line
65x: suction side opening
65A: Slewing Plate Lubrication Recess
65B: Fixed Slab Lubrication Groove
65C: fixed plate recess
70: check valve
71: Outsourced Home
100: compression chamber
100a: swing outer compression chamber
100b: turning inner compression chamber
105: suction area (suction room)
110: back pressure chamber
115: Slewing Bearing Room
120: fixed back chamber
125: oil reservoir

Claims (15)

A fixed scroll having a slab and a scroll wrap mounted on it,
A swing scroll having a hard plate and a scroll wrap mounted thereon, the swing scroll being engaged with the fixed scroll to form a compression chamber between the fixed scroll and the swing scroll;
A back pressure chamber for imparting a pulling force to the fixed scroll to the swing scroll;
A scroll compressor having an oil supply passage for introducing oil on the compressor discharge side into the back pressure chamber,
A compression chamber communication path having a back pressure valve communicating only with the back pressure chamber and the compression chamber after the start of detention, and opening and closing by a differential pressure before and after, and controlling the pressure of the back pressure chamber by flowing oil from the back pressure chamber into the compression chamber;
A suction area communication path configured to communicate only with the back pressure chamber and the suction area leading to the compression chamber after the start of detention, and not to communicate with the compression chamber after the start of the detention, and to supply oil of the back pressure chamber to the suction area. The scroll compressor characterized by the above-mentioned. The scroll compressor according to claim 1, wherein the suction region communication passage is composed of intermittent oil supply means for intermittently supplying oil in a back pressure chamber to the suction region. The oil amount supplied to the compression chamber from the compression chamber communication path is larger than the amount of oil supplied from the suction region communication path to the suction area under at least rated operating conditions. Scroll compressor. 4. The fixed scroll and the swing scroll comprise asymmetrical releases that use both sides of the scroll wrap (orbit wrap) winding end of the orbit scroll to engage the scroll wrap (fixed wrap) of the fixed scroll. The compression chamber side opening of the compression chamber communication path is at the center of the width direction of the bottom of the groove of the fixing wrap and at a position that is 270 degrees or more from the end of the winding of the fixing wrap to the center side (winding start side) along the root of the fixing wrap. A scroll compressor, which is formed. The scroll compressor according to claim 4, wherein the opening of the compression chamber side opening is formed smaller than the thickness of the turning wrap. The hard plate surface (fixed hard plate) of the hard plate (fixed hard plate) of the said fixed scroll from the said back pressure chamber side by the said suction area communication path comprised of the said intermittent oil supply means, and the said suction area communication path. And a fixed platen oil supply groove formed on the fixed platen surface, the fixed platen oil supply hole connecting to the position and the suction area formed on the fixed platen surface, and connecting the suction area. Scroll compressor. 7. The fixed hard disk surface side opening portion of the pivotal slab oil supply hole is overlapped with the fixed slab oil supply grooves at two locations according to the swing motion of the swing scroll 2, whereby the suction area communication path is pivoted. The scroll compressor, which is configured to be an intermittent communication path communicating with the suction area side twice while the scroll is turning one time. The direction of formation of the fixed side plate oil-feeding groove portion intersecting the trajectory of the pivotal plate oil supply hole connects the internal side fixed winding end (β) and the external side fixed winding end (γ) of the fixed wrap. In the direction parallel to the straight line or the direction shifted clockwise from the parallel direction, the lubrication start time to the suction region is configured to be relatively quicker than the start time of the detention of the compression chamber or the start time of the detention. Scroll compressor. 2. The scroll according to claim 1, wherein the suction region communicating passage is provided with a throttle valve in the suction region communicating passage, and the throttle valve is configured to adjust the oil supply amount from the back pressure chamber to the suction region. compressor. 10. The suction area communication path according to claim 9, wherein the suction area communication path comprises a back pressure side suction area communication hole communicating the throttle valve and the back pressure chamber, and a suction side suction area communication hole communicating the throttle valve and the suction area. The throttle valve is arranged between communication holes, and the throttle valve is controlled based on information related to the suction pressure Ps and the discharge pressure Pd of the compressor. The pressure ratio is calculated based on information related to the suction pressure Ps and the discharge pressure Pd, and if the pressure ratio is large, the throttle valve is controlled to increase the oil supply amount, and the pressure ratio is And if it is small, controlling the opening of the throttle valve to be reduced to reduce the oil supply amount. 7. The fixed hard disk of the fixed scroll according to claim 6, wherein a rotating hard disk oil supply recess (concave) is formed at a position opposite to the fixed hard disk surface of the rotating hard disk in the rotating scroll, instead of the rotating hard disk oil supply hole. The fixed platen oil supply groove formed on the surface is formed so as to connect a position in communication with the pivot plate oil supply recess and the suction region, and a fixed platen recess is formed in the fixed platen surface so as to communicate with the back pressure chamber. A rotating compressor of the revolving slab oil supply recess is configured to reciprocate between the fixed slab recess and the fixed slab lube groove in accordance with a turning motion of the revolving scroll. The shape or number of the fixed slab recesses is set so that the communication between the fixed slab recesses and the swinging slab oil supply recesses occurs twice during one turn of the swinging scroll, and the fixed slab oiling is carried out between the communication. A scroll compressor, characterized in that the fixed slab oil-feeding groove is configured to communicate with a groove and the swivel slab oiling recessed portion, and the oil is supplied to the suction region in accordance with the detention of the compression chamber. 13. The rotating slab oil supply recesses according to claim 12, wherein two pivoting slab oiling recesses are radially disposed so as to sandwich the fixed slab oiling grooves, and each of the pivoting slab oiling recesses is fixed at each timing in accordance with the pivoting motion of the swinging scroll. A scroll compressor, configured to be in communication with a hard plate recess and the fixed plate oil feed groove, and configured to supply oil to the suction region in accordance with the start of detention of the compression chamber. 4. The fixed scroll and the swing scroll comprise asymmetrical releases that use both sides of the end of the scroll wrap winding of the swing scroll to engage the scroll wrap of the fixed scroll. The compression chamber side opening of the compression chamber communication path is formed radially outward from the width direction center of the tooth root of the fixed wrap, and the compression chamber side opening is formed along the root of the fixed wrap from the end of the winding of the fixed wrap. A scroll compressor, which is formed at a position larger than 270 degrees into the winding start side and is in a position communicating only with the compression chamber after the start of detention.

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