KR20120040262A - Scroll compressor, refrigerating cycle device, and heat pump water heater - Google Patents

Abstract

If the oil seal of the compression chamber is not sufficient, the compression of the refrigerant is not sufficient, so the efficiency cannot be increased. That is, from the viewpoint of improving the efficiency, the problem is how to perform oil sealing. An object of the present invention is achieved by disposing a back pressure control valve at a position at which communication start of intermittent communication is performed when the volume of both the suction chamber on the inner side of the swing scroll and the suction chamber on the outer side of the swing scroll increases. . It is also achieved by lubricating the tip end of the compression chamber via a space provided at a position deeper than the root of the fixed scroll.

Description

SCROLL COMPRESSOR, REFRIGERATING CYCLE DEVICE, AND HEAT PUMP WATER HEATER}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor for compressing a refrigerant, and more particularly, to a structure for supplying lubricating oil to a compression chamber to improve sealing and to reduce leakage loss.

The scroll compressor used for the room air conditioner and the bottom pump water heater controls the back pressure which is the pressure of the back pressure chamber installed on the opposite side of the swing scroll with the back pressure control valve, presses the swing scroll to the fixed scroll by the controlled back pressure, The refrigerant is compressed in the compression chamber formed by the scroll. Moreover, as a structure provided with a back pressure control valve, the intermittent communication structure is known other than a normal communication structure.

Lubricating oil is supplied to the compression chamber to increase the sealability of the compression chamber and to reduce leakage loss. If the leakage loss can be suppressed as small as possible, the efficiency of the compressor can be improved by that amount. Patent document 1 and patent document 2 are known as a technique of reducing leakage loss.

The compressor disclosed in Patent Document 1 has a two end oil supply structure, and is an oil supply passage for supplying lubricating oil from the oil storage portion of the bottom of the hermetically sealed container, and has a space 20 and a rotating scroll on which the discharge pressure acts. A passage (second communication passage) for contacting the tip of the lap is provided in the turning scroll. A pair of circular arc grooves are provided at the tip of the lap of the revolving scroll to open into compression chambers on both sides of the lap, and one of the pair of circular arc grooves is configured to communicate with the second communication passage. This discloses that lubrication of the sliding portions of the swing scroll and the fixed scroll can be satisfactorily maintained even in a compression space having a higher pressure than the suction chamber.

In the compressor disclosed in Patent Document 2, a communication path communicating with the high pressure part, which is an inner region of the sliding partition ring, and the compression chamber is provided inside the swing scroll, and one of the openings of the communication path is discharged from the center of the fixed scroll. It is installed at the lap end of the swivel scroll to face the port. It is disclosed by this to supply to the compression chamber relatively close to the end of compression, and to prevent the sizing of the lap end of a fixed scroll and the hard plate of a revolving scroll. In addition, it is disclosed to suppress performance deterioration due to a decrease in volumetric efficiency due to suction heating.

Moreover, in the conventional product, the back pressure control valve is arrange | positioned at the about 11 o'clock position as seen from the direction of FIG. 3 of this application (FIG. 22), and it uses the oil which flows in from the back pressure chamber to the suction side through a back pressure control valve, and uses a compression chamber. The sealing was performed.

Japanese Patent Application Publication No. 2009-062908 Japanese Patent Application Publication No. 2009-052464

However, in Patent Document 1, when an arc groove is provided at the tip of the lap, leakage occurs between the compression chambers on both the inside and the outside of the lap, that is, between the turning inner chamber and the turning outer chamber, which will be described later. In order to prevent leakage, it is considered to increase the oil supply amount to increase the sealing property, but for this purpose, it is necessary to deepen the arc groove. If the arc groove is deepened, an opposite phenomenon such as an increase in leakage between the compression chambers occurs.

Moreover, in patent document 2, oil sealing of the compression chamber by the area | region (region near a suction part) relatively close to the start of compression, ie, the outer diameter side far from a discharge port, cannot be expected.

If the oil seal of the compression chamber is not sufficient, the compression of the refrigerant is not sufficient, so the efficiency cannot be increased. That is, from the viewpoint of improving the efficiency, the problem is how to perform oil sealing.

In the conventional product, the R-groove 5h is provided to lubricate the large portion of the hard plate surface of the fixed scroll and the hard plate surface of the swing scroll. That is, the back pressure control valve is provided at the 11 o'clock position mainly from the viewpoint of lubrication. Therefore, there is a possibility that the efficiency can be improved by devising the position of the back pressure control valve in view of the sealing property of the compression chamber and the efficiency improvement.

In view of the above problems, an object of the present invention is to provide a highly efficient scroll compressor. Moreover, the objective of this invention is providing the high efficiency refrigeration cycle apparatus and the bottom pump water heater.

SUMMARY OF THE INVENTION An object of the present invention is a scroll compressor having an intermittent communication structure in which a swing scroll is pressed against a fixed scroll by a back pressure controlled by a back pressure control valve, and the refrigerant is compressed in a compression chamber formed by both scrolls. When the volume of both the suction chamber on the inner side and the suction chamber on the outer side of the swing scroll increases, it is achieved by a scroll compressor in which the back pressure control valve is arranged at a position at which communication start of intermittent communication is performed.

It is also an object of the present invention to provide a double end lubrication structure for pressing the swing scroll against a fixed scroll by back pressure, which is the pressure of the back pressure chamber provided on the side opposite to the swing scroll, and compressing the refrigerant in the compression chambers formed by both scrolls. In a scroll compressor, it is achieved by a scroll compressor for supplying end oil to the compression chamber through a space provided at a position deeper than the root of the fixed scroll.

Moreover, the objective of this invention is to control the back pressure which is the pressure of the back pressure chamber provided on the opposite wrap side of a turning scroll with a back pressure control valve, pressurize the said turning scroll to a fixed scroll by controlled back pressure, and formed by both scrolls. In the scroll compressor of the intermittent communication structure and the end lubrication structure which compress a refrigerant in the compression chamber, when the volumes of both the suction chamber on the inner side of the swing scroll and the suction chamber on the outer side of the swing scroll increase, The back pressure control valve is arranged at a position at which communication start is to be performed, and is achieved by a scroll compressor for supplying end end lubrication to the compression chamber through a space provided at a position deeper than the root of the fixed scroll.

According to the present invention, a highly efficient scroll compressor can be provided. In addition, a highly efficient refrigeration cycle device and a bottom pump water heater can be provided.

Objects, features, and advantages other than the present invention will become apparent from the following description of the embodiments of the present invention with reference to the accompanying drawings.

1 is a longitudinal sectional view of a scroll compressor.
2 is a refueling structure.
3 is a view of pivoting scroll and fixed scroll being engaged.
4 is a view showing a virtual swinging cabin and a virtual swinging cabin.
5A is a diagram showing a communication section of the suction chamber volume change and the communication hole of the back pressure control valve.
FIG. 5B is a graph comparing the graph of FIG. 5A with the first derivative. FIG.
FIG. 6 is a diagram illustrating leaks from the virtual swinging combustion chamber and the virtual swinging cabin. FIG.
The figure explaining the arrangement position of a back pressure control valve.
8 is a diagram illustrating a relationship between the oil supply amount into the suction space and the volumetric efficiency.
9 is an explanatory diagram (1) of end oil supply.
10 is an explanatory diagram (2) of end oil supply.
11 is an oil seal explanatory diagram of a compression chamber.
12 is a view showing shapes other than the communication holes.
Fig. 13 is a diagram showing a change in pressure at the start.
14 shows the engagement of a symmetrical wrap scroll.
15 is a sectional view of a transverse scroll compressor.
Fig. 16 is a comparison of the efficiency of the compressor in 65 DEG C boiling water condition of the present embodiment and the prior art.
17 is a unit configuration diagram of a bottom pump water heater.
18 is a diagram for explaining recesses;
19 is a diagram in which a discharge pressure oil supply chamber communicates with a turning outer compartment.
20 is a diagram illustrating an axis through scroll compressor.
21 is a diagram explaining forced oil supply.
22 is an arrangement position of a back pressure control valve of the conventional product.

EMBODIMENT OF THE INVENTION Hereinafter, the Example of this invention is described, referring drawings.

<Example 1>

The first embodiment will be described in detail below.

1 is a longitudinal sectional view of a scroll compressor, FIG. 2 is an oil supply structure, and FIG. 3 is a view in which a swing scroll and a fixed scroll are engaged. 2 is not a single cross section of the reality, but a convenient cross section for explaining various configurations.

The structure and operation | movement which are the basis of the scroll compressor 1 are demonstrated. The scroll compressor 1 includes a compression mechanism unit 3, an electric motor 4 driving the compression mechanism unit 3, an oil supply unit 50 for supplying lubricating oil to the compression mechanism unit 3, and a compression mechanism unit ( 3) and the airtight container 2 which accommodates the electric motor 4 and the oil supply part 50 is provided.

The airtight container 2 is comprised by the lid chamber 2b and the bottom chamber 2c being welded up and down to the cylindrical case 2a. The suction pipe 2d is provided in the lid chamber 2b, and the discharge pipe 2e is provided in the side surface of the case 2a. The compression mechanism part 3 is arranged in the upper part of the airtight container 2, the electric motor 4 is arranged in the lower part, and the oil supply part 50 is arrange | positioned in the lower part. The lubricating oil 13 is stored at the bottom of the sealed container 2. Moreover, the inside of the airtight container 2 is a so-called high pressure chamber type scroll compressor used as the discharge pressure chamber 2f.

The compression mechanism part 3 is the orbiting scroll 6 which installed the spiral wrap 6a on the base board 6b, and the fixed scroll which installed the spiral wrap 5c on the base board 5d, and installed it. Has (5). In the fixed scroll 5, the turning scroll 6 is arranged so as to be able to turn to face each other. The Oldham ring 12 is arrange | positioned between the lower surface side of the revolving scroll 6, and the upper surface side of the frame 9, and each key formed in one surface and the other surface of the Oldham ring 12 is provided. And the groove formed on the lower surface side of the revolving scroll 6 and the groove formed on the upper surface side of the frame 9 at right angles with the groove.

The fixed scroll 5 is fixed with the bolt 8 with respect to the frame 9. As the outer periphery of the frame 9 is fixed to the inner wall surface of the airtight container 2 by welding, the compression mechanism part 3 is fixed to the airtight container 2. The frame 9 is equipped with the main bearing 9a which rotatably supports the crankshaft 7. The eccentric part 7b of the crankshaft 7 is inserted in the lower surface side of the revolving scroll 6. The swing scroll 6 is positioned between the fixed scroll 5 and the frame 9, and the swing scroll 6 is supported by the crankshaft 7.

The electric motor 4 has the stator 4a and the rotor 4b. The stator 4a is fixed to the sealed container 2 by press fitting and / or welding. In addition, the rotor 4b is fixed to the crankshaft 7 and is rotatably arranged in the stator 4a. The crankshaft 7 is comprised with the main shaft 7a and the eccentric part 7b, and is supported by the main bearing 9a and the lower bearing 17 which were provided in the frame 9. As shown in FIG. The eccentric portion 7b is eccentrically formed with respect to the main shaft 7a of the crankshaft 7 and is integrally formed. The eccentric portion 7b is fitted to the swing bearing 6c provided on the rear surface of the swinging scroll 6, and the crankshaft 7 ) Supports the turning scroll 6.

The crankshaft 7 is driven by the electric motor 4, and the eccentric part 7b eccentrically rotates with respect to the main shaft 7a. The oldham ring 12 transmits the eccentric rotation of the eccentric portion 7b of the crankshaft 7 without rotating the swinging scroll 6, and functions to orbit the swinging scroll 6. Moreover, the crankshaft 7 is provided with the oil supply passage 7c which guides the lubricating oil 13 to the lower bearing 17, the main bearing 9a, and the slewing bearing 6c, The lower side of FIG. The oil supply pipe 7d which sucks up the lubricating oil 13 and guides the oil supply passage 7c to the shaft end side on the (4) side is attached. The oil supply part 50 is the mechanism for supplying lubricating oil to each part through this oil supply passage 7c.

As shown in FIG. 2, the back pressure chamber 14 is formed between the rear surface of the swing scroll 6 and the frame 9, that is, on the side opposite to the swing scroll 6. Through the oil supply passage 7c, the lubricating oil applied with the discharge pressure which is the pressure in a sealed container is introduce | transduced into the space between the back surface of the turning scroll 6 and the upper end part of the crankshaft 7. This space will be referred to as discharge pressure oil supply chamber 51. The discharge pressure oil supply chamber 51 is also formed on the side opposite to the turning scroll 6.

The lower portion of the sealed container 2 in which the lubricating oil 13 is stored is the oil supply passage 7c → the discharge pressure oil supply chamber 51 → the clearance between the swing bearing 6c and the eccentric portion 7b → the back pressure chamber 14 → back pressure control. The valve 16 communicates with the passage of the suction space 10. Further, the oil supply passage 7c → the hole 7z → the gap between the main shaft 7a and the main bearing 9a → the cutout portion 100 → the back pressure chamber 14 → the back pressure control valve 16 → the suction space 10 It is connected by the path of. From the lower part of the sealed container 2 which becomes discharge pressure, the lubricating oil 13 tries to flow into the suction space 10. At this time, from the back pressure chamber 14, on the inlet side of the oil, the clearance between the swing bearing 6c and the eccentric portion 7b and the clearance between the main shaft 7a and the main bearing 9a become the diaphragm. The back pressure control valve 16 becomes an aperture, and the back pressure Pu which is the pressure of the back pressure chamber 14 becomes an intermediate pressure between the suction pressure PS and the discharge pressure PD. In addition, the lubricating oil 13 is supplied to the swing bearing 6c and the main bearing 9a by the pressure difference of the discharge pressure of the compressor lower space and the back pressure of the back pressure chamber 14. So-called differential pressure oil supply.

When the orbiting scroll 6 revolves based on the rotation of the crankshaft 7 driven by the electric motor 4, the gas refrigerant is transferred from the suction pipe 2d to the orbiting scroll 6 and the fixed scroll 5. Guided to the compression chamber 11 formed by. The compressed gas refrigerant is discharged into the sealed container 2, that is, into the discharge pressure chamber 2f, from the discharge port 5e provided at approximately the center of the bottom plate 5d of the fixed scroll 5, and is discharged from the discharge pipe 2e to the outside. Going out The coolant that flows out is returned to the scroll compressor 1 through a suction pipe 2d through a first heat exchanger, an expansion device, and a second heat exchanger (not shown). A structure in which these are sequentially connected in a loop shape is called a refrigeration cycle, and a device using the same is called a refrigeration cycle device.

The release valve 15 is provided in the fixed scroll 5. The release valve 15 is for discharging from the compression chamber 11 to the discharge pressure chamber 2f when the pressure in the compression chamber 11 becomes equal to or higher than the pressure in the discharge pressure chamber 2f. For example, in the case of a liquid compression state or an overcompression state, the release valve 15 acts. In addition, a release valve hole 15a is provided between the release valve 15 and the compression chamber. The release valve hole 15a can be said to be a space provided at a position deeper than the root of the fixed scroll 5.

In this embodiment, at least one release valve 15 is arranged in each compression chamber. In order to be able to communicate with the release valve 15 also in the compression chamber of almost any crank angle, it is for making a pressure drop rather than making a compression chamber a complete sealed space. Therefore, when the number of turns of the lap increases and the number of compression chambers increases, it is preferable to increase the number of release valves 15 corresponding to the number of compression chambers.

Generally, the pressure in a compression chamber is represented by Formula 1, and is determined by the ratio of an exhaust volume and a compression chamber volume.

Pc = Ps? (VO / Vc ) r [ Equation 1]

Here, Pc represents a compression chamber pressure, Ps represents a suction pressure, K0 represents an exhaust volume, Vc represents a compression chamber volume, and r represents an adiabatic index.

Depending on the operating pressure conditions, the pressure in the compression chamber may be higher than the pressure in the discharge pressure chamber 2f. At this time, the gas refrigerant is discharged from the release valve 15. Since the release valve 15 located on the outer diameter side of the bottom plate is not so high in pressure, it is rarely opened during normal operation. However, the release valve 15 is installed to avoid liquid compression when liquid refrigerant is sucked in immediately after starting. There is a big reason.

FIG. 3 shows both scrolls 5, the hard plate surface of the revolving scroll 6 (the tooth plane of the revolving scroll 6), or the hard plate surface of the fixed scroll 5 (the end face of the fixed scroll 5). 6) is cut | disconnected and the case seen when it faces toward the fixed scroll 5, ie, upward of FIG. The lap of the swing scroll 6 is hatched. The center side is called the start of winding of the lap, and the outer diameter side is called the end of winding of the lap. In FIG. 3, the wrap is wound in the clockwise direction. You can also rewind the lap counterclockwise.

The origin of the axis shown in FIG. 3 is the center of the hermetic container 2. This coincides with the center of the base plate of the fixed scroll 5. The vertical axis is as follows, and the horizontal axis passes through the origin at right angles to the vertical axis.

The vertical axis | shaft is based on the position of the winding end 6of the outer side wrap of the turning scroll 6, when the turning outer chamber with the largest volume is formed. The swing outer chamber is a compression chamber on the outer diameter side of the lap of the swing scroll 6. The turning outer room with the largest volume is also the turning outer room on the outermost side (11a). From this point, the swinging outer compartment is also formed on the inner diameter side, which is indicated by reference numeral 11a '.

3 is shown so that the point where the winding end 6 of the outer side wrap of the revolving scroll 6 may contact the fixed scroll 5 may rise on the vertical axis. The contact on the fixed scroll 5 side at that time is called winding end 5i of the inner side wrap of the fixed scroll 5. Similarly, the winding end 5b of the outer side wrap of the fixed scroll 5 is also defined, and these winding end 5b rises on the vertical axis | shaft of FIG. When the winding end 5b of the outer lap of the fixed scroll 5 and the winding end 6i of the inner lap of the swinging scroll 6 come into contact with each other, the inner diameter of the lap of the swinging inner chamber, that is, the lap of the swinging scroll 6 The compression chamber of the side is formed. The turning station at this time is the turning station with the largest volume, and is also the turning station on the outermost side. Although not shown in FIG. 3, depending on the rotational angle of the crankshaft 7, the swinging inner chamber is also formed therein on the inner diameter side. For example, it is shown by 11b 'of FIG. 6 (b). In addition, although expressed as "contact | adherence," it means that the length of the imaginary line which connected the virtual line (AA, 6 Ｘi-5 Ｘ) which connected each winding end part (6 Ｘ-5-5) more precisely is minimum. . In addition, an extension and an external line refer to the side of the tooth which is a vortex, ie, the lap side.

The portion where the curve continues further clockwise than the winding end portions 5 종료 i and 5ＸＸ of the fixed scroll 5 is called an extension part. In Fig. 3, the winding end portions 5i and 5v are positioned at the 6 o'clock position indicated by the hour hand of the clock, and the suction pipe 2d and the suction port 2d1 indicated by broken lines are positioned near the 7 o'clock position of the extension portion. . Moreover, R groove 5h is formed until 11 o'clock, and the back pressure control valve 16 is arrange | positioned at the 9 o'clock position. The conduction path 5i of the back pressure control valve 16 communicates with the R groove 5h. As for the 2nd upper limit and the 3rd upper limit, the contact area of the hard board surface of both scrolls 5 and 6 becomes larger than the 1st upper limit and the 4th upper limit in FIG. It is installed in the part. This is a groove which guides oil from the back pressure control valve 16 in order to lubricate the hard plate surfaces of both scrolls 5 and 6.

As shown in FIG. 3, the suction space 10 and the compression chamber 11 which are suction parts are formed between the wrap 5c and the wrap 6a. The suction space 10 refers to a region where the pressure becomes a suction pressure, and communicates with the suction pipe 2d. The compression chamber 11 is an area | region which the communication with the suction pipe 2d is interrupted, and is divided roughly into two types, a turning outer chamber and a turning inner chamber.

Generally, the boundaries of the compression chamber are four, that is, a first boundary formed by the roots of a fixed scroll first, a second boundary formed by the roots of a second scroll, and a third boundary formed by an extension of a revolving scroll. Fourthly, it has four boundaries of the fourth boundary formed by the outer line of the fixed scroll. For example, like the room indicated by 11b of FIG. 3, compression chambers having such boundaries are referred to as swinging interior chambers (or fixed exterior chambers). Further, the first and second boundaries are the same as above, and the compression chamber having four borders, the third boundary formed by the outer line of the turning scroll and the fourth boundary formed by the inner line of the fixed scroll. It is called a cabin (or a fixed internal space), for example, and it is the room indicated by 11a, 11a 'of FIG.

Lubricant oil is supplied between these boundaries to maintain the sealability. In any compression chamber, there exists a micro clearance (about 5 micrometers or less) between lap side surfaces, ie, between a 3rd border and a 4th border. In the minute gap close to the discharge port 5e of the front end of the compression chamber, i.e., close to the winding start of the lap, a compression chamber having a higher pressure is further formed in front of the front end. Therefore, a gas refrigerant having a higher pressure leaks from the minute gap between the third boundary and the fourth boundary. On the other hand, in the gap close to the suction port 2d1 of the rear end of the compression chamber, that is, close to the winding end of the wrap, the compression chamber having a lower pressure is further formed behind the rear end. Therefore, gas refrigerant leaks from the minute gap between the third boundary and the fourth boundary into the compression chamber having the low pressure. Leakage at the front end or the rear end can be said to be a leak from the swinging interior chamber to the swinging interior chamber or from the swinging exterior chamber to the swinging exterior chamber. This is called leakage of the first kind.

On the other hand, there is a smaller gap (about 3 μm or less) between the tip and the root, respectively. When viewed from the compression chamber, the minute gap exists between the turning inner and outer cabins and between the first boundary and the third boundary, and between the second boundary and the fourth boundary. The compression chamber 11 is adjacent to the compression chamber with a higher pressure and the compression chamber with a lower pressure on the space | interval of these gaps. Naturally, gas refrigerant leaks from the compression chamber with high pressure and gas refrigerant leaks into the compression chamber with low pressure. Leakage between the tip and the root can be said to be a leakage from the turning cabinet to the turning cabin, or from a turning cabin to the turning cabin. This is called the second type of leakage.

In order to reduce these leaks, oil is supplied to the compression chamber and the gap is filled with this oil. Therefore, how to seal this part becomes important.

The winding end 6i of the inner side wrap of the turning scroll 6 mentioned above is set to the position of FIG. 3 at the 6 o'clock position of the clock, and moves so as to draw the trajectory in the counterclockwise direction as shown by the broken line. Already, the winding end 6b of one outer side lap also traces similarly, but illustration is abbreviate | omitted. In FIG. 3, the turning outer room indicated by 11a is shown by the turning outer room of 0 degree crank angle. Then, the turning outer cabin indicated by 11a 'can be represented by the turning outer cabin with a crank angle of 360 degrees. The volume of the swinging outer chamber 11a of 0 degree crank angle is the largest among the volumes of the swinging outer chamber. In addition, the turning cabinet is formed at a crank angle of 180 degrees, and the turning interior chamber volume at that time is the largest in the turning interior chamber volume (see FIG. 6B).

Thus, the compressor of the system by which the timing of the compression start of the turning internal and external cabins shift | deviated 180 degrees by the rotation angle of the crankshaft 7 is called an asymmetric wrap type. In addition, although the turning cabinet of the largest volume is shown in FIG. 6 (i), it is not shown in FIG. In FIG. 3, the turning stationary chamber indicated by 11b is a turning stationary chamber which the crank angle advanced 180 degrees from the turning cabinet of the largest volume, and turns into a turning stationary chamber of crank angle 360 degrees. 3, a turning outer chamber 11a with a crank angle of 0 degrees, a turning outer chamber 11a 'with a crank angle of 360 degrees, a turning inner chamber 11b with a crank angle of 360 degrees, and a turning inner chamber of a crank angle of 720 degrees. A total of four compression chambers of 11b 'are shown. Since the turning internal chamber 11b 'of the crank angle 720 degrees is opened to the discharge port 5e, it cannot be called strictly with a compression chamber, but it expresses it like this for easy understanding.

Next, the back pressure control valve 16 which is a mechanism which adjusts the back pressure PJ which is the pressure of the back pressure chamber 14 is demonstrated. The swinging scroll 6 is pressed against the fixed scroll 5 by the back pressure PJ. The swinging scroll 6 is said to receive a force which can be pressed toward the fixed scroll 5 by the back pressure PJ. If the back pressure is large, the pressing force is also large, and the friction force generated between the scrolls is also large, which is undesirable. The back pressure control valve 16 is a valve for controlling the back pressure so as not to become too large.

5 f of spring accommodating holes are formed in the fixed scroll 5. 5 g of through-holes are formed in the back pressure chamber 14 of the spring accommodation hole 5f, and the piece 16a is press-fitted in this through-hole 5g. In the piece 16a, the communication hole 16b which communicates the spring accommodating hole 5f and the back pressure chamber 14 is formed. The valve body 16c is arrange | positioned at the spring storing hole 5f, and the valve body 16c is pressurized by the spring 16d so that the communication hole 16b may be blocked. The spring 16d is attached to the sealing member 16e, and the sealing member 16e is press-fitted into the fixed scroll 5 so as to partition the spring receiving hole 5f and the discharge pressure chamber 2f. A conduction path 5i is formed on the side surface of the spring accommodating hole 5f to communicate with the R-groove 5h formed in the extension portion of the hard plate surface of the fixed scroll 5. Since the R-groove 5h communicates with the suction pipe 2d, the pressure of the spring accommodating hole 5f becomes the suction pressure Ps.

The operation of the back pressure control valve 16 will be described. The lubricating oil 13 stored below the sealed container 2 passes through the oil supply pipe 7d and the oil supply passage 7c by the pressure difference between the pressure in the sealed container 2 and the pressure in the back pressure chamber 14. It is lubricated in the bearing. The lubricating oil 13 which has reached the end of the upper crankshaft 7, that is, the discharge pressure oil supply chamber 51 flows into the back pressure chamber 14 through the diaphragm. There is also a lubricating oil 13 flowing into the back pressure chamber 14 through the hole 7z and the cutout 100. In this back pressure chamber 14, the refrigerant dissolved in the lubricating oil 13 is foamed.

The upward force (upward force in FIGS. 1 and 2) applied to the valve body 16c by the pressure difference between the pressure in the back pressure chamber 14 and the spring storage hole 5f pressure, that is, the suction pressure Ps, When the force is greater than the downward force by the spring 16d, the valve body 16c is opened, and the lubricating oil 13 in the back pressure chamber 14 passes through the conduction path 5i and the R groove 5h, and the suction space 10 Supplied by. This is because not only the gas refrigerant but also the oil passes through the back pressure control valve 16. This oil is considered to be oil attached to a hole or a wall surface, or oil of mist shape. The pressure of the back pressure chamber 14 is adjusted by the spring force in this way, and becomes the suction pressure Ps + constant value. This constant value is determined by the spring force of 16d, and the back pressure (PJ) can be increased as the amount of deflection of the spring when the valve is closed and the spring constant k, that is, the spring is less likely to bend.

In a so-called bottom pump hot water heater called EcoCute (registered trademark), carbon dioxide (CO ₂ ) is used as a refrigerant of a refrigeration cycle apparatus. This refrigeration cycle is called a supercritical refrigeration cycle in which the pressure on the high pressure side exceeds the critical point of CO ₂ . This high pressure is produced by, for example, the scroll compressor as in the present embodiment. The scroll compressor using CO ₂ as a refrigerant has three to five times the operating pressure and three to five times the differential pressure controlled by the back pressure control valve. When the back pressure determined by the spring force [= suction pressure (Ps) + constant value] is reached, the back pressure control valve opens. However, under such a high pressure differential environment, there is a large amount of gas refrigerant and oil flowing from the back pressure chamber to the suction space. Therefore, a difference occurs between the back pressure at the moment of opening the back pressure control valve and the back pressure after opening. The back pressure after opening becomes lower than the back pressure at the moment of opening. Since back pressure in normal operation has an appropriate pressure for efficiency, the back pressure control valve is designed in accordance with the back pressure in normal operation. For this reason, it is hard to bend the spring so that a back pressure may not fall too much even if a back pressure control valve operates. Then, it was found out that the back pressure control valve did not open even when necessary, such as during startup.

As a means for solving this problem, the so-called intermittent communication structure which uses the orbital motion of the revolving scroll 6 to block or communicate the communication hole 16b of the back pressure control valve 16 with the hard plate surface. There is. This is because the orbiting scroll 6 orbits relative to the fixed scroll 5 based on the rotation of the crankshaft 7, so that the hard plate surface of the bottom plate 6b of the orbiting scroll 6 has the back pressure control valve 16. The communication hole 16b is intermittently blocked. In other words, the back pressure control valve 16 and the back pressure chamber 14 are intermittently connected.

The valve body 16c and the piece 16a are in metal contact only by the spring force, and there is a small gap due to the surface roughness of the member, so that the leak cannot be completely zero. While the bottom plate 6b is blocking the communication hole 16b, the gas refrigerant in the communication hole 16 'leaks into the spring storage hole 5f at a minute gap between the valve body 16c and the piece 16a. At this time, since the back pressure control valve 16 is blocked, the back pressure does not change. By the way, the volume of the communication hole 16b is small, for example, when the diameter of the hole of the communication hole 16b is 2 mm, the volume is about 0.03 cm <^3> . The pressure inside is reduced. When the pressure in the communication hole 16k is lowered, the gas coolant and oil in the back pressure chamber 14 are discharged when the bottom plate 6b of the swing scroll 6 communicates with the back pressure chamber 14 through the communication hole 16b. It flows into the communication hole 16b, and the inertial force F shown by following Formula acts on the valve body 16c.

Ｆ∝Ａ * ρ * Ｖ ² [Equation 2]

Here, F is an inertia force, A is a cross-sectional area of the communication hole 16b, ρ is a fluid density, and Ｖ is a flow rate.

In this way, the intermittent communication structure allows the inertia force of the fluid to act on the valve body 16c in response to the pressure difference between the back pressure chamber 14 and the spring storage chamber 5f, thereby making it easier to open the back pressure control valve 16. . Moreover, since such an effect is recognized by the scroll compressor used in a supercritical refrigeration cycle, even if it is a scroll compressor for a plon type refrigerant | coolant which operates at a lower pressure, although the degree may be small, it is thought that it has the same effect.

When the intermittent communication structure is set, the amount of oil supplied from the back pressure chamber 14 through the back pressure control valve 16 to the swing outer chamber 11a and the swing inner chamber 11b is positioned at the position of the back pressure control valve 16. Change accordingly. The oil supply distribution to this turning outer chamber and turning inner chamber is demonstrated with reference to FIGS. Fig. 4 is a view showing a virtual swinging inner chamber and a virtual swinging outer chamber; Fig. 5A is a view showing the volume change of the suction chamber and the communication section of the communication hole of the back pressure control valve; Fig. 5B is the graph of Fig. 5A and the first system; It is a figure comparing the differential graph and arrange | positioning in the same size so that mutual relationship may be known. It is a figure explaining the leakage from a virtual turning internal chamber and a virtual turning outer chamber, and FIG. 7 is a figure explaining the arrangement position of a back pressure control valve.

Fig. 4 shows imaginary rooms 11A and 11Ｂ in which gas refrigerant and oil flow into the suction stroke, and these regions are called suction chambers and are part of the suction space 10. These virtual rooms 11A and 11 'are called the virtual turning outer room 11A and the virtual turning interior room 11'. Therefore, the suction chamber is referred to as the virtual swing outer chamber 11A or the virtual swing inner chamber 11 '. Both the virtual swinging outer chamber 11A and the virtual swinging inner chamber 11k are suction pressures. This is because the above described virtual lines AA and X always communicate with the suction pipe 2d. In addition, the virtual swinging outer chamber 11A and the virtual swinging inner chamber 11 'are defined as follows.

The virtual swinging outer room 11A is a virtual line AA which connects the winding end 5a of the inner side lap of the fixed scroll 5 and the winding end 6a of the outer lap of the swinging scroll 6 to each other. And the area surrounded by the outer line wrap of the swing scroll 6 and the inner wrap of the fixed scroll 5.

The virtual swinging interior chamber 11 'is an imaginary wire which connects the winding end 5a of the outer side lap of the fixed scroll 5 and the winding end 6a of the inner side lap of the swinging scroll 6 to each other. And an area surrounded by the inner side wrap of the swinging scroll 6 and the outer side wrap of the fixed scroll 5.

Although each room 11A, 11 Ｂ is not partitioned, the space which these rooms target becomes a turning outer chamber 11a and a turning inner chamber 11b in the future. That is, the room 11A at the time of suction completion becomes the turning outer chamber 11a which becomes a maximum volume, and the room 11A at the time of suction completion turns into the turning interior room 11b which becomes a maximum volume. Thereafter, the volume is reduced in accordance with the rotation of the crankshaft 7 to compress the gas refrigerant.

FIG. 5A shows a change in the rotation angle of the crankshaft 7 of the volume in each suction stroke of each suction chamber and the communication hole 16b of the back pressure control valve 16 at the back pressure control valve position θb. The communication section of is shown. Although the type of spiral in this scroll compressor 1 is an involute curve, it is known to show the same volume change even in a logarithmic spiral. Here, the volume change of the suction chamber is shown at the ratio of 1 at the completion of suction. Accordingly, the peak of the suction volume ratio is larger in the virtual swinging inner chamber 11 'than in the virtual swinging outer chamber 11A. The longitudinal axis intercept and rotation angle 0 degrees are the suction start of the virtual swinging outer chamber 11A, and are shown in FIG. 3 or FIG. 6 (a).

Back pressure control valve position (theta) b is shown by the angle which made the negative side of the vertical axis | shaft of FIG. 7 0 degree. You may think that it responds similarly to the crank angle mentioned above. In addition, when it shows with the hour hand, (theta) b = 0 degrees are 6 o'clock directions, (theta) b = 210 degrees are 11 o'clock directions, and (theta) b = 270 degrees are 9 o'clock directions. The virtual swinging cab 11A gradually increases in volume while the swinging scroll 6 rotates, exceeds the volume when it is closed (α ₁ ), meets a peak along the way (α ₂ ), and then decreases. Thus, it is lost at a rotation angle of 360 ° (α ₃ ). Then, the next virtual swinging outer compartment 11A defined as described above is also newly formed to show the same volume change.

As shown in FIG.6 (b), the virtual swinging combustion chamber 11 'side shows the volume change which shifted | deviated 180 degree from the virtual turning outer chamber 11A. In FIG.3 and FIG.6 (a), the virtual turning stationary chamber 11 'of the magnitude | size of a certain magnitude | size is shown, and as shown in FIG. 5A, it is about 60% of the maximum turning volume. Thereafter, the volume of the virtual turning stationary chamber 11Ｂ gradually increases, exceeds the volume when closed (β ₁ ), meets the peak along the way (β ₂ ), and then decreases, and disappears at a rotation angle of 180 °. (Β ₃ ). Then, the next virtual turning stationary chamber 11 'defined as described above is also newly formed to show the same volume change.

However, if the volume of the virtual swinging outer chamber 11A and the virtual swinging inner chamber 11Ｂ serving as the suction chamber follows the target space, such a space becomes a compression chamber which is a closed space in the suction chamber and is called. The swing outside chamber 11a and swing inside chamber 11b are changed. That is, when the winding end part which is an element of the virtual line of each suction chamber is matched by the orbital motion of the turning scroll 6, when a virtual line becomes the minimum length strictly, a suction stroke is completed and the suction chamber of the suction chamber is completed. Since the communication with the suction pipe 2d is blocked in the virtual swinging outer chamber 11A and the virtual swinging inner chamber 11k which are the target spaces, the words of the "virtual" are taken out and the codes are changed, respectively. It becomes a compression chamber which is a space, and a name changes to turning outer chamber 11a and turning inner chamber 11b, respectively.

When only the volume change of the virtual swinging outer chamber 11A and the virtual swinging inner chamber 11 Ｂ is seen, almost the same volume change is repeated every 180 degrees. For example, in the case where the back pressure control valve 16 is installed at the position of θb = 30 °, that is, the five o'clock position, the communication section of the communication hole 16b is in the range of 130 ° to 290 ° in the rotation angle. In this back pressure control valve position, the volume of the virtual turning stationary chamber 11 시작 begins to decrease with the rotation of the crankshaft 7 at the beginning of communication of the communication hole 16b (β ₂ to β ₃ ). In the case where the back pressure control valve 16 is installed at a position of θb = 210 °, that is, at an eleven o'clock position 180 ° away from this, the communication section of the communication hole 16b is in the range of 310 ° to 470 ° at the rotation angle. . At this back pressure control valve position, the volume of the virtual swinging outer chamber 11A begins to decrease with the rotation of the crankshaft 7 at the beginning of the communication of the communication hole 16b (α ₂ to α ₃ ).

Moreover, the communication section of the communication hole 16b which is a communication section of intermittent communication is a part between two oblique broken lines shown in FIG. 5A. For illustrative purposes, the characteristic back pressure control valve 16 installation position is shown by a white arrow. Naturally, even if the back pressure control valve 16 is disposed at any position, the angle ranges in which the back pressure control valve 16 and the back pressure chamber 14 communicate with each other by intermittent communication are equal to 160 °.

The oil passing through the back pressure control valve 16 from the back pressure chamber 14 passes through the R-groove 5h and is supplied to the virtual swing outer chamber 11A and the virtual swing inner chamber 11 ', furthermore, the swing outer chamber ( It flows into 11a) and turning stationary chamber 11b, and is used for sealing a compression chamber. However, in the sections α ₂ to α ₃ and β ₂ to β _{3 in} which the volume is decreasing, the gas refrigerant escapes from the suction chamber and flows back in the direction of the suction port 2b, so that the oil supply is reversed to this. Will be done. That is, it is difficult to refuel in this section, and the efficiency of refueling is poor. It can be said that oil supply is hindered. This section can be seen in Figure 5b. The section in which the volume is decreasing is a portion where the graph of the first derivative in FIG. 5B (b) becomes negative.

That is, when θb = 30 °, lubrication to the virtual swinging interior chamber 11k is difficult, and when θb = 210 °, lubrication to the virtual swinging cabin 11A is difficult. In particular, it is thought that the oil passing through the back pressure control valve 16 from the back pressure chamber 14 will go out in a large amount at the moment when the back pressure control valve 16 is opened, and it can be lubricated at the beginning of the communication of the communication hole 16b. If not, most of the oil can not be supplied. Therefore, the oil supply distribution of the turning outer chamber 11a and the turning inner chamber 11b is biased to either side. In the compression chamber in which oil flowed in less, the sealing property of a compression chamber may fall and leakage loss may occur.

Here, in the conventional product, the back pressure control valve 16 was provided at the approximately 11 o'clock position, that is, the position of (b) 210 degrees so that oil may be supplied to the edge part of R groove 5h. This is because the hard plate surfaces of both scrolls 5 and 6 can be lubricated over a wide range.

However, as mentioned above, since the back pressure control valve 16 was provided at the 11 o'clock position, it is considered that it was difficult to supply oil to the virtual swinging outer chamber 11A from one side. In general, the oil is further supplied, and the remaining oil is discharged from the discharge port 5e to the discharge pressure chamber 2f. Conventionally, although both the virtual turning outer chamber 11A and the virtual turning inner chamber 11A thought that oil could be lubricated more than an appropriate amount from the viewpoint of volumetric efficiency, that is, the oil could be lubricated in a balanced manner as a whole. Though it was considered, there was an imbalance in the amount of oil supply in regard to the sealability of the compression chamber 11, and in part, an adequate amount of oil was supplied to the appropriate amount from the viewpoint of volumetric efficiency, and the excess was partially used. It is thought that oil was supplied excessively. Even if the back pressure control valve 16 is arranged at the 10 o'clock position α ₂ to α ₃ , the imbalance is the same. Of course, this imbalance is due to intermittent communication, and an imbalance does not occur in the case of normal communication described later.

On the other hand, when the back pressure control valve position (theta) b is made into the position of 270 degrees, ie, the 9 o'clock position, for example, a bias can be eliminated. At θb = 270 °, both the virtual swinging outer chamber 11A and the virtual swinging inner chamber 11 이 have no portion where the suction chamber volume is decreasing, so there is no backflow (α ₄ ). It is easy to lubricate the cabin 11A and the virtual turning stationary room 11 '. That is, when the back pressure control valve is provided in the position where communication start of intermittent communication is performed, when the volume of both the virtual swinging outer chamber 11A and the virtual swinging inner chamber 11k is not reduced, the crankshaft 7 The volume of each suction chamber increases with rotation, and the suction chamber introduces oil on its own. It is considered to be a phenomenon such as natural intake in the reciprocating engine of an automobile. Thus, the back pressure control valve position (theta) b which the part (beta _3- alpha ₂ , alpha ₃ to beta ₂ ) which the suction chamber volume does not decrease, and the beginning of communication overlap is 90 degree-210 degree, 270 degree-390 It is a position of °, it is a position 11 o'clock to 3 o'clock, and a position 5 o'clock to 9 o'clock.

In contrast with gasoline injection, it takes time for the oil injected from the back pressure control valve 16 to reach the suction chamber. This time may be an extremely short time and may not necessarily be as follows. However, since the crankshaft 7 rotates and the volume is changing during the arrival time, the oil is virtually turning inside and outside the cabin (11A, It is more preferable to inject the oil from a position where the volume does not decrease when reaching 11 kPa). In other words, it is considered preferable to avoid injection just before the bottom dead center of the piston. Therefore, a preferable range is made into the position of 90 degrees-150 degrees, 270 degrees-330 degrees from these points, and is made into the 1 hour-3 hours position, and the 7 hours-9 hours position. This is a point symmetrical position as can be seen in FIG. This is because the volume change of the suction chamber is repeated every 180 degrees, and it is preferable to set it as such a position because it is an asymmetric wrap type scroll compressor. However, at the position of 1 o'clock to 3 o'clock, the R groove 5h must be increased from 11 o'clock to 12 o'clock to 1 o'clock to 3 o'clock, so that the change of the outer diameter or the change of the vortex on the inner diameter side becomes necessary.

In the present embodiment, since the wrap is wound in the clockwise direction, there is no root of the fixed scroll 5 at the position of 270 ° to 330 °, that is, the 7 to 9 o'clock position, and there is sufficient space for arranging the back pressure control valve 16. There is. Therefore, it is more preferable to arrange | position the back pressure control valve 16 in this position. In addition, although the volume of virtual turning outer space 11A seems to be hardly [near 4 o'clock position ((alpha) ₄ ), when it considers with the injection of gasoline, when oil reaches | attains the virtual turning outer space 11A, It is thought to enter the area where the volume increases. In this regard, the distance from the back pressure control valve 16 to the suction chamber becomes long at the position of 1 o'clock to 3 o'clock, and it is difficult to adjust the timing of the oil injection from the back pressure control valve 16.

Therefore, it is more preferable to arrange the back pressure control valve 16 at the 7 to 9 o'clock position from the point of injection, and the closer to the 7 o'clock position, the shorter the distance between the back pressure control valve 16 and the suction chamber can be. Therefore, the time for oil to reach the suction chamber can be shortened. Compared with setting the back pressure control valve 16 to the 1 to 3 o'clock position, since the volume change of the suction chamber in this short time is small, the angle of rotation from the start of communication of intermittent communication until the oil reaches the suction chamber, The rotation angle of the volume change of the suction chamber can be examined with little consideration of time delay. Moreover, if the back pressure control valve 16 is arrange | positioned in the 7-9 o'clock position, the oil of the R groove 5h from the position to the 11 o'clock position will likely remain. In practice, however, the supplied high pressure oil leaks through the gap between the hard plate surfaces, so that the oil can be circulated. High pressure here is back pressure (PJ) with respect to suction pressure (PS).

If a more preferable position is examined, space is required for arranging the suction pipe 2d, and therefore, workability and assemblability are also improved by moving the portion. In the present embodiment, as shown in Fig. 7, it is considered that there is no room at the position of 7:30, so the position of approximately 7:40 to 9:00, that is, the position of 270 ° to 310 ° is more preferable.

In addition, it is thought that the range (alpha _5- beta ₂ ) in which both suction chambers increase in volume is more preferable. This is because when both the suction chambers increase in volume, the back pressure control valve 16 and the back pressure chamber 14 communicate with each other and the injection can be started while there is a flow that is sucked into the suction chamber. However, if the volume of the suction chamber exceeds 1 in the ratio, the volume is soon reduced and finally the ratio becomes 1. In other words, both the virtual swinging inner and outer cabins are larger than the volume when the compression chamber, which is an enclosed space, becomes larger, and at the end, the volume is reduced and closed. Considering the time for the oil to reach the suction chamber by injection, both the suction chambers and the back pressure control valve 16 and the back pressure chamber 14 are in the range where the volume increases until the volume ratio becomes 1 (α ₅ to β ₁ ). ) Is preferably communicated. More preferred is a position of approximately 7 to 8:30, that is, a position of 285 ° to 330 °.

In other words, the communication start of intermittent communication is performed when the volumes of both the spaces of the virtual turning inner and outer cabins which are suction chambers increase to the volume when each compression chamber and the turning inner and outer cabins become closed spaces. It is preferable to arrange the back pressure control valve at the position.

Therefore, the range considered as the best position becomes a position of 285 degrees-310 degrees, ie, a position of 7: 40-8: 30.

As described above, by supplying oil to both the turning inner side and the turning outer side in a balanced manner before forming the compression chamber, both can maintain the sealing property from the start of the compression stroke and improve the efficiency.

By the way, in each said bearing part, the lubricating oil 13 stored in the lower part of the airtight container 2 is filled with the oil supply pipe 7d by the pressure difference of the pressure of the airtight container 2 and the pressure of the back pressure chamber 14. Although it has been explained that oil is supplied through the super oil supply passage 7c, this oil supply amount is closely related to the volumetric efficiency. Here, bearing oil supply amount is demonstrated. The bearing oil supply amount is the amount of oil flowing into the back pressure chamber 14, the amount flowing into the back pressure chamber 14 through the gap between the swing bearing 6c and the eccentric portion 7b, the main shaft 7a and the main bearing. It is the sum total of the quantity which flowed into the back pressure chamber 14 through the clearance gap of 9a. That is, the bearing oil supply amount is mainly an amount of oil for lubricating the bearing.

This oil is supplied to the suction space 10 from the back pressure control valve 16. Basically, you may think that the oil supply amount to the suction space 10 is the same as the bearing oil supply amount. However, the amount of oil supplied from the back pressure control valve 16 to the suction space 10 and the amount of oil actually supplied into the compression chamber 11 are different. A portion of the oil supply to the suction space 10 is used for lubrication of the hard plate surface, a part of which flows into the suction chamber and is supplied into the compression chamber 11.

When the amount of lubrication to this suction space 10 is small, the amount of lubrication to the compression chamber 11 further lowers, sealing with oil is not possible, leakage loss increases, and volumetric efficiency falls. However, even if the amount of oil supply to the suction space 10 is too large, the volumetric efficiency is lowered. The reason is as follows. Since the oil supplied to the suction space 10 through the back pressure control valve 16 has a higher temperature than the suction gas, the suction gas is heated. As a result, the gas density of the suction gas decreases, and the amount of refrigerant circulating in the gas refrigerant flowing into the suction chamber and further into the compression chamber 11 decreases. Therefore, the volumetric efficiency falls from the following formula (3). This is called heating loss of the suction gas.

That is, the oil supply amount to the suction space 10 exists in an appropriate range from the viewpoint of volumetric efficiency. Fig. 8 schematically shows the relationship between the oil supply amount to the suction space and the volumetric efficiency. Here, the range where volumetric efficiency becomes a value more than fixed is made into the appropriate. However, if the oil supply amount to the suction space 10 is made appropriate from a volume efficiency point of view, it is impossible to supply the required amount as the bearing oil supply amount. If the bearing oil supply amount is too small, problems such as sizing, which are more serious than a decrease in volumetric efficiency, may also occur. Therefore, in general, oil is additionally supplied, and the remaining oil is discharged from the discharge port 5e to the discharge pressure chamber 2f. Thus, there is also a required oil supply amount from the viewpoint of the reliability of the bearing and the sliding part, and the bearing oil supply amount, which is the oil supply amount necessary for the entire scroll compressor, must be set to an appropriate amount. In this case, the amount of oil supply to the suction space 10 as seen from the volumetric efficiency is more than the amount of oil supply appropriate and becomes excessive. That is, due to the heating loss of the suction gas, the volumetric efficiency is lowered.

In the present embodiment described below, the heating loss of the intake gas can be reduced, which will be described below with reference to FIGS. 9 to 13 and 6. FIG. 9 is an explanatory view (1) of the end oil supply, FIG. 10 is an explanatory view (2) of the end oil supply, FIG. 11 is an explanatory view of oil sealing of the compression chamber, FIG. 12 is a view showing shapes other than the communication holes, and FIG. It is a figure which shows the pressure change at the time of starting.

As shown in FIG. 9, oil is to be supplied from the back pressure chamber 14 to the compression chamber 11 (swing outer chamber 11a) through the communication hole 18 and the release valve hole 15a1. The structure for supplying oil at the end of the swinging scroll 6 in this way is referred to as the end oil supply structure. In FIG. 9, oil is added to the compression chamber 11 (revolving outer chamber 11a) using the release valve hole 15a1 which is a space provided in a position deeper than the root of the fixed scroll 5 in addition to the tooth lubrication structure. To supply.

The swinging scroll 6 has a communication hole 18 in the lap, the first opening is provided at this end, which is the end face of the lap, and is opposite to the first opening with respect to the bottom plate of the swinging scroll 6, that is, opposite the first opening. The second opening is provided on the wrap side. The first opening will be referred to as the wrap front side opening or the tip opening, and the second opening will be referred to as the opposite wrap side opening. This end opening communicates with the release valve hole 15a1, and the opposite wrap side opening communicates with the back pressure chamber 14, which is a space for back pressure, formed on the opposite wrap side of the swing scroll 6.

FIG. 10 shows how the communication hole 18 communicates with the release valve hole 15a1. By the orbital motion of the revolving scroll, the back pressure chamber 14 and the revolving outer chamber 11a communicate with each other via the end opening of the communication hole 18 and the release valve hole 15a1. This release valve hole 15a1 is a hole corresponding to the release valve 15 located in the outer diameter side of the bottom plate shown in FIG. 3, and is for the turning outer chamber 11a formed in the outermost diameter side.

FIG. 10A is the same as the positional relationship between the scrolls 5 and 6 shown in FIG. 3, and the angle of the crankshaft 7 is 0 °. Here, the communication hole 18 is not in communication with the release valve hole 15a1, and the opening at the lap tip side of the communication hole 18 is blocked by the lap bottom surface of the fixed scroll 5.

10B illustrates a case where the angle of the crankshaft 7 is about 80 degrees. The communication hole 18 is in communication with the release valve hole 15a1 here. As shown in FIG. 9, since the back pressure chamber 14 and the turning outer chamber 11a communicate with each other through the communication hole 18 and the release valve hole 15a1 at this timing, the lubricating oil from the back pressure chamber 14 ( 13 is supplied to the turning outer chamber 11a. In addition, the back pressure chamber 14 and the turning outer chamber 11a communicate with each other via the communication hole 18 and the release valve hole 15a1. The angle of the crankshaft 7 is about 45 ° to about 90 °. It is a range and it can be said that it is intermittently connected.

10C is a case where the angle of the crankshaft 7 is about 120 degrees. Here, the communication hole 18 is not in communication with the release valve hole 15a1, and the end opening of the communication hole 18 is blocked by the wrap bottom surface of the fixed scroll 5 again.

The schematic diagram of the state in which the clearance gap in a compression chamber is sealed by lubricating oil is shown in FIG. Compression chamber pressure shall be P1 <P2 <P3. The lubricating oil 13 supplied to the compression chamber 11 is attached to the lap wall surface, seals between the tip and the root, and suppresses the second type of leakage. In addition, although not shown in this figure, of course, the oil which flowed into the compression chamber 11 seals the clearance gap between wraps, and also suppresses the 1st type leakage.

In FIG. 11, since there exists a pressure difference in the adjacent compression chamber, the lubricating oil 13 flows into the clearance 191 or the clearance 192 by this pressure difference. When there is little lubricant 13 supplied to the compression chamber 11, the clearances 191 and 192 will not be filled with the lubricant 13, and seal will be torn. Then, since the sealability cannot be maintained, the ejection of the gas refrigerant occurs, which leads to an increase in leakage loss, further leading to a decrease in efficiency.

As described in FIG. 10B, when the pressure in the back pressure chamber 14 is higher than the pressure in the swing outer chamber 11 a, the lubricating oil 13 flows from the back pressure chamber 14 into the swing outer chamber 11 a. do. At this time, not only the lubricating oil 13 but also a gas refrigerant flows into the turning outer chamber 11a. In the meantime, since the crankshaft 7 rotates about 45 degrees, the pressure of the turning outer chamber 11a rises. This rise is the rise from the broken dashed line shown in FIG. 13 to the broken dashed line shown in FIG. 13. Inflow of oil and a gas refrigerant also contributes to the increase in pressure, but a volume change of the swinging outer chamber 11a is a main factor.

When the communication hole 18 is blocked by the wrap bottom of the fixed scroll 5, the minimum sealing length of the gap 192 is half the thickness t of the wrap minus the diameter of the communication hole 18. . Even if the sealing length in other parts is sufficiently maintained, a situation may arise in which the minimum sealing length is short and insufficient, as described above.

Therefore, the minimum sealing length has a lower limit from the viewpoint of the strength of the wrap, the viewpoint of the sealability, and the viewpoint of the supply amount of the lubricating oil 13. From the viewpoint of the supply amount, the diameter of the communication hole 18 is preferably as large as possible. However, in terms of sealability and strength, it is preferable that the diameter of the communication hole 18 is made small so that the sealing length is as large as possible.

Assuming that the thickness of the lap is 3.0 mm, for example, from the viewpoint of strength, the diameter of the communication hole 18 is at most 2.0 mm if the minimum dimension as the thickness is ensured. In addition, the value determined from the size of the tool becomes the minimum dimension of the communication hole 18, but this is, for example, 0.6 mm. Therefore, the diameter of the communication hole 18 is, for example, about 0.6 mm to 2.0 mm (1/5? T to 2/3? T). When the supply amount of the lubricating oil 13 is insufficient, such as when the diameter of the communication hole 18 is 0.6 mm or less, further devising is required as shown in FIG. 12 described later. In these cases, the ratio of the thickness (t) of the wrap to the minimum seal length is 1/6? T to 2/5? T, that is, the minimum seal length is 17% or more and 40% of the thickness (t) of the wrap. The following becomes preferable. However, this is a case where the center of the communication hole 18 of a circular cross section is made to coincide with the center line of the lap. As mentioned above, the actual minimum sealing length does not depend on the ratio with this thickness, but should be represented by length only. When the present scroll compressor is considered, this thickness falls within a range of about 1.5 to 6.0 mm, which is at most half, and thus the minimum sealing length is also expressed in proportion as described above.

Since the diameter of the release valve hole 15a is 1.8 mm, if it is such a minimum sealing length, as shown in FIG. 9, it becomes possible for the release valve hole 15a1 to engage the communication hole 18. As shown in FIG. Therefore, oil can be supplied from the back pressure chamber 14 to the turning outer chamber 11a via the communication hole 18 and the release valve hole 15a1.

In addition, as shown in FIG. 12, the communication hole 18 may be made into a long circle shape. 12 shows the motion trajectory of the communication hole 18 when the swing scroll 6 is idle. By making the communication hole 18 into a long circular shape or the like, the section where the release valve hole 15a1 and the communication hole 18 communicate with each other can be lengthened. Moreover, the area which the communication hole 18 opens to the release valve hole 15a1 can be enlarged, maintaining the minimum sealing length large, and the oil supply amount from the back pressure chamber 14 to the turning outer chamber 11a can be increased. There is an advantage that it is.

Conversely, when the pressure in the swinging outer chamber 11a is higher than the pressure in the back pressure chamber 14, the lubricating oil 13 flows in reverse to that described in FIG. 10 (b). If a reverse flow occurs, the gas in the turning outer chamber 11a flows into the back pressure chamber 14 in a large amount, thereby excessively raising the pressure in the back pressure chamber 14. However, since the back pressure control valve 16 is opened, the back pressure PU is fixed to a predetermined value. In this case, even if it compresses all the way to the middle, the energy consumed by it wastes and it reduces efficiency. Therefore, in order to maintain sealing property here, it is necessary to take sufficient sealing length. Here, too, it is said that it is preferable to make the minimum sealing length 17% or more and 40% or less of the thickness t of a lap here.

13 shows the pressure change after the scroll compressor is started. The three lines of the suction pressure PS, the back pressure PS and the discharge pressure PD are experimental results. The part shown by PPM is the pressure of the turning outer chamber 11a of the section which the communication hole 18 and the release valve hole 15a1 which are shown in FIG. 10 communicate. When the compressor is started, the pressure difference between the discharge pressure Pd and the suction pressure Ps increases.

When the virtual swinging cab 11A follows the same space, it changes to the swinging cab 11a at the closed moment. The pressure of the turning outer chamber 11a at that moment is PS. Thereafter, as the crankshaft 7 rotates, the pressure in the swinging outer chamber 11a increases. The movement of both scrolls in the case of ascending is shown in FIG.

The band-shaped portion (part indicated by Pc'm) surrounded by the broken line in FIG. 13 indicates the pressure Pc'm of the turning outer chamber 11a when the communication hole 18 and the release valve hole 15a1 communicate with each other. It is shown. That is, it is the pressure of the turning outer chamber 11a demonstrated by FIG. 10 (b). However, the pressure after n rotation is shown continuously, rather than following the closed turning outer chamber 11a.

Before starting operation, the suction pressure (Ps), back pressure (Pb), the discharge pressure chamber pressure (P _2f) is of course the same since there is no difference, initially immediately discharge pressure chamber of the pressure (Pc) of the compression chamber after the start-up (P _2f) a As a result, the release valve 15 is opened. As shown in Equation 1, the compression chamber pressure Pc is determined by multiplying the ratio between the exhaust volume and the compression chamber volume by a constant value, and thus, the discharge pressure Pd and the suction as in the immediate after startup. when the ratio (Pd / Ps) of the pressure (Ps) is low, a pressure (Pc) of the compression chamber 11 is because it just reached the pressure (P _2f) of the discharge pressure chamber (2f). Then, the pressure of the turning outer chamber 11a is equal to the pressure P _2f of the discharge pressure chamber, and in FIG. 13, Pc is shown as the discharge pressure Pd. This is area A. Further, the discharge pressure chamber pressure (P _2f) is synonymous with the discharge pressure (Pd).

Therefore, in the section A immediately after the start, the ratio Pd / PS is low, the peak is P _2f or more, and the release valve 15 is opened. When Pc is higher than the back pressure (Pv) as immediately after starting, the back pressure chamber 14 and the turning outer chamber 11a communicate with each other through the communication hole 18 and the release valve hole 15a1, thereby turning the swinging chamber 11a. Gas coolant flows back into the back pressure chamber 14, and tries to raise the pressure in the back pressure chamber 14. At this time, since the difference between the back pressure P and the suction pressure PS is a small pressure, it cannot yet be overcome by the pressing force by the spring 16d of the back pressure control valve 16, and the back pressure control valve 16 is not opened. Therefore, the back pressure (PJ) increases due to the reverse flow, and the turning scroll 6 reliably floats at the start of the scroll compressor 1, and the gap between the tip and the tooth root can be reduced. That is, the efficiency at the start can be improved.

After a certain period of time, the difference between the suction pressure PS and the discharge pressure PD increases. This is area B. At the beginning of this region B, the release valve 15 is opened, and the peak is the discharge pressure Pd. To this vicinity, since the peak is higher than the back pressure (PV), a gas refrigerant flows into the opposite lap side opening from this end opening, thereby increasing the back pressure (PV).

Thereafter, Pcm decreases with the suction pressure Ps. In Equation 1, when Vc is the volume of the turning outer chamber 11a when the communication hole 18 and the release valve hole 15a1 communicate with each other, and Pc is Pc, Pc is the suction pressure Ps. It turns out that this becomes low and falls. The back pressure PJ is controlled to be a constant value of the suction pressure Ps + by the spring force of the back pressure control valve 16, but the behavior becomes P> Ps as shown in FIG. 13 unless the valve is opened in response to the spring force. To show. When the valve is opened against the spring force, the back pressure (PJ) suction pressure (Ps +) becomes a constant value. As a result, the peak of the start side of the section B is higher than the back pressure (PV), but then lowers than the back pressure (PV).

When the Pc is lower than the back pressure (Pk), i.e., when the back pressure (Pk) is higher than Pc, such as in normal operation, the lubricating oil 13 of the back pressure chamber 14 is introduced so that the gas coolant flows from the opposite lap side opening to the end opening. Is supplied to the turning outer chamber 11a via the communication hole 18 and the release valve hole 15a1. As described above, in the conventional product, since the back pressure control valve 16 was provided at the 11 o'clock position, it is considered that it was difficult to supply oil to the virtual swinging outer chamber 11A. Therefore, after the turning outer chamber 11a is formed, the oil is lubricated to the turning outer chamber 11a which is a closed space, thereby improving the sealing property of the turning outer chamber 11a and improving the efficiency of the compressor. In addition, the tip lubrication acts in a direction in which the aforementioned imbalance is resolved.

Moreover, the rotating outer chamber which is a closed compression chamber which does not introduce a part of the lubricating oil 13 supplied to the back pressure chamber 14 by lubricating a bearing to the suction chamber from the suction space 10 via the back pressure control valve 16 ( Since it is directly supplied to 11a), the heating loss of the suction gas can be reduced to improve the volumetric efficiency. In detail, it is as follows.

When oil is supplied to the virtual swinging outer chamber 11A or the virtual swinging inner chamber 11k, which is the suction chamber, via the back pressure control valve 16 and the suction space 10, the suction gas is heated to decrease the density of the gas refrigerant. The circulation amount is lowered and the volumetric efficiency is lowered. However, if the oil supplied to the suction space 10 is reduced, the fall of the refrigerant circulation amount can be suppressed and the decrease of the volumetric efficiency can also be suppressed. The amount of oil supply reduced as described above is supplied to the compression chamber 11 through the communication hole 18 at this end. Since the compression chamber 11 is a closed space, the refrigerant circulation amount does not change, and the volumetric efficiency does not decrease.

That is, the direct oil supply which supplies oil directly to the compression chamber 11 without passing through the suction space 10 from the indirect oil supply path which indirectly supplies oil to the compression chamber 11 via the suction space 10. Even if a part of the oil supply amount is moved along the path, the heating loss of the suction gas does not move from the indirect oil supply path directly to the oil supply path, so that the heating loss of the suction gas as a whole is reduced only as much as the amount of oil supply to the suction space 10 is reduced. Can be reduced. Therefore, the amount of oil supply of the compression chamber 11 via the back pressure control valve 16 and the suction space 10 from the back pressure chamber 14, which has been excessive in terms of volumetric efficiency, is reduced, and only the reduction is made. The fall of volume efficiency can be suppressed and volume efficiency can also be improved as a whole. This corresponds to shifting to the left side in the “excess” range in FIG. 8, that is, approaching the “titration” range. This is because the bearing lubrication amount becomes insufficient if it becomes the "suitable" range.

For example, even if the oil supply volume to the virtual turning internal and external cabins is already balanced by arranging the back pressure control valve 16 at regular communication or at the 7 to 9 o'clock position, the effect of improving the volumetric efficiency by the end oil supply is attained. Can be obtained. Moreover, it is the structure which always communicates the back pressure chamber 14 and the back pressure control valve 16 with the regular communication structure, and is used when the pressure of the back pressure chamber 14 is suppressed comparatively small. That is, the back pressure control valve 16 is easy to open even without intermittent communication. It is mainly used as the above-mentioned scroll compressor for a plon type refrigerant | coolant. Further, the so-called Eco-cute area of (R) as the projected area of the discharge pressure in the longitudinal direction of the opposite raepcheuk of the scroll compressor may be an orbiting scroll (6) of CO ₂ as a refrigerant used for the Bottom pump water heater serves to If the configuration is larger than that of the present embodiment, the back pressure can be reduced, and an always communicating structure can be adopted.

As described above, immediately after starting, the pressure function of the back pressure chamber 14 is raised to reliably press the swing scroll 6 to the fixed scroll 5, and after that, the normal operation is performed. The lubricating oil 13 can be supplied to the turning outer chamber 11a to improve the sealability in the compression chamber and to improve the efficiency of the compressor.

Here, the use of the lubricating oil 13 in the gap sealing varies depending on whether the gap in the compression chamber 11 is adjacent to a room having a high pressure or a room having a low pressure.

First, it is explained concretely that the first type of leakage is suppressed.

The compression chamber formed as one of the chambers has a lower pressure than the compression chamber formed 360 degrees earlier with a crank angle than the compression chamber. Therefore, the oil from the 360 ° leading chamber leaks from the gap between the front end of the compression chamber. Moreover, oil leaks from the clearance gap of the rear end part of the said compression chamber to the room which is 360 degree | times followed.

Since the turning outer chamber 11a 'shown to FIG.6 (a), (b) starts compression 360 degree ahead with the crank angle by the turning outer chamber 11a, it turns with the turning outer chamber 11a'. When the pressure of the outer chamber 11a is compared, the pressure side of the turning outer chamber 11a 'is increased. Therefore, the lubricating oil 13 in the turning outer chamber 11a 'leaks through a clearance gap to the turning outer chamber 11a in a compression stroke, and the leaked lubricating oil 13 of the clearance of the turning outer chamber 11a is carried out. Sealing is performed. Moreover, the lubricating oil 13 supplied to the turning outer chamber 11a leaks into the virtual turning outer chamber 11A, and also seals the turning outer chamber.

Since the turning internal chamber 11b 'shown to Fig.6 (a), (b) starts compression 360 degree ahead with the crank angle than the turning internal chamber 11b, it turns with the turning internal chamber 11b'. When the pressure of the internal chamber 11b is compared, the pressure side of the turning internal chamber 11b 'becomes high. Therefore, the lubricating oil 13 in the turning internal chamber 11b 'leaks through a clearance gap to the turning internal chamber 11b in a compression stroke, and the leaked lubricating oil 13 of the clearance of the turning internal chamber 11b is carried out. Sealing is performed. In addition, the lubricating oil 13 in the turning inner chamber 11b leaks into the virtual turning inner chamber 11 ', and further seals the turning inner chamber.

Next, it is explained concretely that the second type of leakage is suppressed.

In FIG. 11, the turning outer chamber 11a to which the lubricating oil 13 was supplied through the communication hole 18 and the release valve hole 15a1 is called room of P2. The lubricating oil 13 in the turning outer chamber 11a leaks through the gap 191 into the room of the low pressure P1, thereby suppressing the gas refrigerant from leaking out of the gap 191. Since the lubricating oil 13 leaks from the clearance gap 192 of the side adjacent to the room of high pressure P3, the sealing property of the room is maintained.

Since the turning outer chamber 11a 'shown in FIG. 6 (a) starts compression 180 degrees at a crank angle ahead of the turning inner chamber 11b, it turns into the turning volume 11a' and the same volume of turning outer chamber 11a '. When the pressure of the cabin 11b is compared, the pressure side of the swinging outer chamber 11a 'is increased. Therefore, the lubricating oil 13 in the turning outer chamber 11a 'leaks through a clearance gap to the turning inner chamber 11b in a compression stroke, and the leaked lubricating oil 13 of the clearance of the turning inner chamber 11b is carried out. Sealing is performed. In addition, the lubricating oil 13 supplied to the swinging outer chamber 11a 'leaks into the virtual swinging inner chamber 11' and further seals the swinging inner chamber.

In addition, since the turning internal chamber 11b shown in FIG.6 (a) starts compression 180 degrees ahead of the turning outer chamber 11a by the crank angle, since the turning outer chamber 11a and the turning internal chamber 11b are compressed, ), The pressure side of the swinging inner chamber 11b is increased. Therefore, the lubricating oil 13 in the turning inner chamber 11b leaks through the clearance to the turning outer chamber 11a in the compression stroke, and the leaked lubricating oil 13 seals the gap between the turning outer chamber 11a. Will be done.

In addition, since the turning outer chamber 11a shown in FIG.6 (a) starts compression ahead of the virtual turning inner chamber 11 ', the pressure side of the turning outer chamber 11a is high. Therefore, the lubricating oil 13 in the turning outer chamber 11a leaks through a clearance gap to the virtual turning inner chamber 11 'in the compression stroke, and further seals the turning inner chamber.

In addition, since the turning outer chamber 11a 'shown in FIG. 6 (b) communicates with the discharge port 5e, the turning outer chamber 11a' is not strictly already a compression chamber, but is a relationship with the crank angle before and after. In order to facilitate understanding in the description as described above. Since the swing outer chamber 11a 'starts compression 180 degrees ahead of the crank angle with the turning inner chamber 11b', when the pressure of the turning outer chamber 11a 'and the turning inner chamber 11b' is compared, it turns. The pressure side of the outer chamber 11a 'is high. In addition, since the turning outer chamber 11a 'starts compression by 360 degrees at the crank angle of the turning inner chamber 11b and 180 degrees ahead of the turning inner chamber 11b', the turning outer chamber 11a 'is started. The pressure side of the is high. In the swinging outer chamber 11a 'shown in FIG. 6B itself, the pressure in the swinging outer chamber 11a' becomes discharge pressure. As described above, the swinging outer chamber 11a 'is in communication with the discharge port 5e. Therefore, since the pressure side of the turning outer chamber 11a 'is high like these, the lubricating oil 13 in the turning outer chamber 11a' carries out the turning inner chamber 11b 'and the turning inner chamber 11b in a compression stroke. Is leaked through the gap, and the leaked lubricating oil 13 seals the gap between the swinging inner chamber 11b 'and the gap between the swinging inner chamber 11b.

In addition, since the turning internal chamber 11b 'shown in FIG.6 (b) starts compression 180 degrees ahead of the turning outer chamber 11a by the crank angle, the turning outer chamber 11a and the turning internal chamber ( When the pressure of 11b ') is compared, the pressure side of the turning station 11b' becomes high. Therefore, the lubricating oil 13 in the turning internal chamber 11b 'leaks through the clearance to the turning outer chamber 11a in a compression stroke, and the leaked lubricating oil 13 of the gap of the turning outer chamber 11a is leaked. Sealing is performed.

In addition, since the turning outer chamber 11a shown in FIG.6 (b) starts compression 180 degree ahead with the crank angle than the turning inner chamber 11b, the turning outer chamber 11a and the turning volume 11a of the same volume are turning inside. When the pressure of the cabin 11b is compared, the pressure side of the swinging outer chamber 11a is high. Therefore, the lubricating oil 13 in the turning outer chamber 11a leaks through the clearance to the turning inner chamber 11b in the compression stroke, and the leaked lubricating oil 13 seals the gap between the turning inner chamber 11b. Is done.

In addition, since the turning internal chamber 11b shown in FIG.6 (b) starts compression ahead of the virtual turning outer chamber 11A, the pressure side of the turning internal chamber 11b is high. Therefore, the lubricating oil 13 in the turning inner chamber 11b leaks through the clearance gap to the virtual turning outer chamber 11A in a compression stroke, and also seals the turning outer chamber.

In addition, although the release valve 15 was described as not opening in the above description, depending on actual operating conditions, the release valve 15 may be open, and if it does so, it will not necessarily follow the above description. When the release valve 15 is opened, the pressure of the compression chamber 11 exposed thereon becomes equal to the discharge pressure. Leakage is eliminated between compression chambers at the same pressure, and lubricating oil 13 leaks from the compression chamber with high pressure to the compression chamber with low pressure between compression chambers with different pressures.

In the virtual swinging cabin 11A, the suction is completed, the swinging outer room a, and the phase of which is 360 ° shifted from the swinging outer room as the swinging outer room a '. The turning-in internal chamber (b) and the rotational interior (b ') of which the phase advanced 360 degree from the said turning-in internal chamber are set to have completed suction. If the number of compression chambers is increased by increasing the number of laps, a ″, a ′ ′ ′,... , B ″ ， b ′ ′ ′ ，… It can be similarly described as, etc.

In this way, the lubricating oil 13 supplied through the communication hole 18 and the release valve hole 15a1 is used to seal the gap until the end of the discharge, and the remaining lubricating oil is discharged from the discharge port 5e to the discharge pressure chamber 2f. do.

In consideration of the above leakage and the rest, it is more advantageous to lubricate the compression chamber on the outer diameter side as much as possible before and after the compression chamber formation so that it can be surely compressed from the start of compression. In addition, as the pressure in the compression chamber 11 increases, the oil supply amount due to the end oil supply decreases. When the pressure in the compression chamber 11 becomes equal to or greater than the back pressure, the end oil supply from the back pressure chamber 14 cannot be performed. Therefore, it is more advantageous to lubricate the compression chamber on the outer diameter side as much as possible from this point of view. Lubrication to the suction chamber by the back pressure control valve 16 and lubrication to the swinging outer chamber 11a by the tip end lubrication can be performed with a more efficient compressor.

Here, in this embodiment, the back pressure chamber 14 and the turning outer chamber 11a are communicated through the communication hole 18 and the release valve hole 15a1 for the turning outer chamber 11a, and the turning outer chamber 11a is made. Although the tip lubrication was performed in the form of lubricating the tip only by), the tip can be lubricated also in the turning station 11b, whereby the efficiency can be further improved. At that time, similarly to the communication hole 18, the communication hole 18-2 is provided in the lap of the swing scroll 6, and the turning stationary room (through the release valve hole 15a2 for the swinging stationary chamber 11b) is provided. What is necessary is just to make it the structure which performs end lubrication also in 11b). At this time, the opening on the opposite side of the communication hole 18-2 may be shared with that of the communication hole 18. The turning inside and outside cabins 11a and 11b which perform this end lubrication are the inside and outside cabin of the outermost diameter side.

The configuration in which tooth tip lubrication is performed to both the swinging outer chamber 11a and the swinging inner chamber 11b has a unique effect particularly in the case of the symmetrical lap type. Fig. 14 is a diagram of the timing at which the swinging outer chamber 11a and the swinging inner chamber 11b of the symmetrical lap are suctioned together. In the case of the symmetrical lap type, since the turning outer chamber 11a and the turning inner chamber 11b start compression at the same timing, if the volume of the turning outer chamber 11a is the same as the volume of the turning inner chamber 11b, the pressure is also the same. Become. Therefore, in the case of the symmetrical lap type, since the leakage of the lubricating oil 13 between the same volume of turning internal and external cabins, that is, the second type of leakage between the same volume of turning internal and external cabins, disappears, the turning outer chamber 11a and the turning interior chamber ( 11b) It is preferable to provide communication holes 18 and 18-2 in communication with the release valve holes 15a1 and 15a2, respectively.

If the above-mentioned imbalance seems to have little suction to the virtual swinging stationary chamber 11b, this end oil supply may be performed only to the swinging stationary chamber 11b.

In the above description, all have been explained on the premise of the vertical scroll compressor 1 shown in FIG. 1, but the same effect can be obtained even on the assumption of the horizontal scroll compressor as shown in FIG. 15.

16 shows the efficiency of the scroll compressor 1 of the present embodiment. In (a) and (b), the said figure has shown volumetric efficiency in ratio, and the following figure has shown compressor efficiency in ratio. (a) is the figure which compared the left figure which shows (theta) b = 270 degrees (9 o'clock position) of this embodiment, and the right figure which shows the conventional (theta) b = 210 degrees (11 o'clock position). (b) is a drawing which compared the left figure which has the communication hole 18, and the right figure which does not have the communication hole 18 at (theta) b = 270 degrees. Here, (a) shows the efficiency of the right figure which shows (theta) b = 210 degree at 100%, and (b) shows the efficiency of the right figure which does not have the communication hole 18 at the ratio which made 100%. Doing. The operating conditions are conditions for boiling hot water at 65 ° C when the scroll compressor 1 is mounted on an Ecocute (registered trademark). The volumetric efficiency may be represented by Equation 3 and the compressor efficiency by Equation 4.

η _v = Γ / (V0? ρ _s ? ｆ) [Equation 3]

η _c = Γ? Δh / w [Equation 4]

Where η _v is the volumetric efficiency, η _c is the compressor efficiency, Γ is the refrigerant circulation, V0 is the exhaust volume, ρ _s is the inlet gas density, f is the motor rotation frequency, and Δh is the enthalpy difference between the inlet and outlet gases, w Indicates motor input.

As can be seen from (a), the back pressure control valve position θb = 270 ° (9 o'clock position) has improved volumetric efficiency and compressor efficiency by 1.5 to 2% with respect to θb = 210 ° (11 o'clock position). . In addition, as can be seen from (b), the volume efficiency and the compressor efficiency are improved by 2 to 2.5% in the case of having the communication hole 18 without having the communication hole 18. In particular, it can be seen that since the volumetric efficiency is increased, the sealability of the compression chamber is improved, and the amount of refrigerant circulation in the equations (3) and (4) is increased.

Due to the above, it is possible to balance oil supply to the virtual swinging outer chamber 11A and the virtual swinging inner chamber 11k, and to improve the sealing property of each compression chamber and to reduce the leakage loss. In addition, the communication hole 18 and the release valve hole 15a1 communicate with each other to supply oil from the back pressure chamber 14 to the swing outer chamber 11a, thereby passing through the back pressure control valve 16 to intake the space 10, The flow rate flowing into the suction chamber can be reduced, so that the heating loss of the suction gas can be reduced.

Next, a case will be described in which the scroll compressor 1 is mounted on a bottom pump water heater and eco cute (registered trademark) to form a unit. 17 is a unit configuration diagram. Since the same code | symbol as the said Example shows the same effect, it abbreviate | omits description.

When a certain time (for example, 3:00 am) is reached at midnight, the scroll compressor 1 is started, and the high temperature and high pressure refrigerant compressed from the discharge pipe 2e is discharged. The discharged refrigerant is heat-exchanged with the water of the water storage tank 32 in the water-refrigerant heat exchanger 29 to be cooled. As the water-cooling heat exchanger 29, the above-described first heat exchanger can be used. The refrigerant exiting the water-refrigerant heat exchanger (29) is depressurized by the expansion valve (33), enters the evaporator (34), and absorbs atmospheric heat to evaporate. The refrigerant exiting the evaporator 34 is sucked into the scroll compressor 1 from the suction pipe 2d and compressed again here. The refrigeration cycle apparatus equipped with the scroll compressor 1 of this embodiment also becomes a highly efficient refrigeration cycle apparatus only as the efficiency of the scroll compressor 1 increases.

On the other hand, the water of the water storage tank 32 is conveyed to the water circulation pump 31, and guide | induced to the water-cooling heat exchanger 29. As shown in FIG. Water derived from the bottom of the water storage tank 32 is heated in the water-refrigerant heat exchanger 29, and the heated water is returned to the top of the water storage tank 32.

Next, the control method will be described. The remote controller 30 sets the temperature of the hot water stored in the water storage tank 32 by the user. The signal from the tapping temperature sensor 35 and the discharge gas temperature sensor 36 is input to the control unit 25. If the temperature detected by the tapping temperature sensor 35 or the discharge gas temperature sensor 36 is lower than the temperature of the hot water set by the remote controller 30, the rotation speed of the scroll compressor 1 is increased to increase the refrigerant circulation amount. The expansion valve 33 is narrowed to increase the discharge pressure or control to increase the temperature of the hot water.

By the above method, a refrigeration cycle is controlled so that the temperature of the hot water of the storage tank 32 becomes a desired temperature, for example, operation will be stopped by 7:00 in the morning. In the daytime, the hot water of the water storage tank 32 and the tap water from the water pipe are mixed, and hot water is supplied from the shower 27 or the faucet 28 which is a use terminal according to a user's request. In addition, when reheating the hot water of the bathtub 24, the hot water in the bathtub and the hot water in the storage tank 32 are heat-exchanged by the reheating heat exchanger 26 provided in the storage tank 32.

Such a scroll compressor is mounted in a room air conditioner, a package air conditioner for business use, a bottom pump water heater, and the like. As an index showing the performance of the room air conditioner and the bottom pump hot water heater annually, there is one called energy consumption efficiency (YANN). For example, in the case of a bottom pump hot water heater, this APF is determined according to how much electric power the apparatus consumed with respect to the hot water load according to the outside temperature specified by the specification, and is represented by hot water load ÷ consumption power. Here, the hot water load is represented by the following formula.

Lw = (θo-θi)? Cw? Ｖ? Ｄ [Equation 5]

Here, Lw is a hot water load, θo is a hot water temperature, θ i is a water acquisition temperature, Cw is a specific heat of water, v is a hot water supply amount, d is the number of days.

Here, the hot water supply temperature θo and the water acquisition temperature θi are determined by the outside air temperature. The number of days (d) is determined by how many days of the year the outside temperature is. Integrating the hot water load Lw annually yields an annual hot water load. The improvement in the compressor efficiency means that the power consumption is reduced, and the device in which the scroll compressor of the present embodiment is mounted improves the Ap. That is, energy saving can be aimed at. Or, when the power consumption as before can be used, the heating capacity can be increased. For example, even if it is cold, the heating capacity can be increased, so that the temperature for boiling water can be increased, and the amount of hot water that can be used substantially can be increased without changing the capacity of the boiling water tank 32.

<Example 2>

18 shows a second embodiment. The scroll compressor shown in FIG. 18 has substantially the same configuration as the first embodiment, and the same name and the same reference numerals can obtain the same effects. The difference between the second embodiment and the first embodiment is that the communication hole 18 is not formed with the release valve hole 15a, but rather a recess formed at the bottom of the wrap bottom of the fixed scroll 5, i.e., deeper than the root. To communicate with (20). That is, the end opening communicates with the recess 20 and the opposite wrap side opening communicates with the back pressure chamber 14. This concave portion 20 can also be said to be a space provided at a position deeper than the root of the fixed scroll 5.

As described in the first embodiment, the release valve 15 operates when the pressure in the compression chamber 11 becomes equal to or higher than the pressure P2f of the discharge pressure chamber 2f or when the liquid refrigerant is sucked in immediately after starting. As the main purpose, the installation position is defined to some extent. However, as in the present embodiment, the recess 20 allows the installation position to be free, and the timing at which the back pressure chamber 14 and the compression chamber 11 communicate through the communication hole 18 and the recess 20. The degree of freedom of setting increases.

 <Example 3>

19 shows a third embodiment. The scroll compressor 1 shown in FIG. 19 has substantially the same configuration as that of the first embodiment, and the same name and the same reference numerals can obtain the same effects. The difference from the first embodiment is that the communication hole 18 communicates with the upper space of the crankshaft 7 in the swing bearing 6c, that is, the discharge pressure oil supply chamber 51. This end opening communicates with the release valve hole 15a1, and the opposite wrap side opening communicates with the discharge pressure oil supply chamber 51, which is a space having a pressure higher than the back pressure, which is formed on the opposite wrap side of the swing scroll 6.

Since the discharge pressure oil supply chamber 51 is almost discharge pressure Pd, the communication hole 18 and the release valve hole 15a communicate with each other, so that the discharge pressure oil supply chamber 51 from the discharge pressure oil supply chamber 51 to the compression chamber 11 is used. Refueling is possible. However, as compared with the first embodiment, since the differential pressure supplied is increased, it is necessary to reduce the supply amount of the lubricating oil 13 by shortening the communication section between the communication hole 18 and the release valve hole 15a. Therefore, it is conceivable to make the cross-sectional area of the communication hole 18 smaller than in the first and second embodiments. Here, the communication hole 18 penetrates the hole from the outer peripheral surface of the bottom plate 6b of the turning scroll 6 toward the discharge pressure oil supply chamber 51, and processes the hole from this end of the turning scroll 6 toward this through hole. The stopper can be formed by tightly inserting the stopper into the hole penetrated through the outer circumferential surface of the base plate 6b by press fitting or screwing.

 <Example 4>

20 shows a fourth embodiment. The flow of the refrigerant and the flow of the lubricating oil of this embodiment are the same as those of the embodiment shown in FIG. The difference from the embodiment of FIG. 1 is that the swing bearing 6c is a so-called shaft through type scroll compressor, which penetrates the swing scroll 6. The gas compression load due to the pressure in the compression chamber 11 acts on the center of the lap height. This gas compression load acts in the swing bearing 6c direction and acts as a bearing load on the swing bearing 6c. Therefore, the operating point of the gas compression load and the bearing load coincide with each other, and the moment of trying to overturn the turning scroll 6 is eliminated.

<Example 5>

21 shows a fifth embodiment. The flow of the refrigerant in this embodiment is almost the same as the embodiment shown in FIG. The difference from the embodiment of Fig. 1 is the oil supply method, a so-called forced oil supply method. The lower end part of the crankshaft 7 is provided with oil supply pump 103, such as a trocoid pump. This oil supply pump 103 is linked with the rotation of the crankshaft 7. As shown in FIG. Oil is supplied to the revolving bearing 6c and the main bearing 9a by the oil supply pump 103. The space around the crankshaft 7 and the back pressure chamber 14 are partitioned by the seal ring 102. The oil is supplied to the back pressure chamber 14 by the space around the crankshaft 7 and the oil pocket 101 which travels to the back pressure chamber 14. The coming and going uses the revolution movement of the turning scroll 6. When oil is supplied to the oil supply pump, only the volume of the oil supply pump can be supplied irrespective of the pressure condition, and the bearing oil supply amount can be reduced when the pressure difference between the discharge pressure and the suction pressure is large.

As described above, the technology described in each embodiment can increase the efficiency of a compressor, a refrigeration cycle device, and the like. In addition to the configuration described in these embodiments, the same operation and effect can be obtained even when the vertical scroll compressor is a horizontal scroll compressor. Similar effects can be obtained even with a configuration in which the configurations are appropriately combined.

Although the foregoing description has been made with respect to the examples, it is apparent to those skilled in the art that various changes and modifications can be made within the spirit of the invention and the scope of the appended claims.

1: scroll compressor
2: sealed container
２ａ: Case
２ｂ: Cover chamber
2c: bottom chamber
2d: suction pipe
２ｄ１: Suction port
２ｅ: discharge pipe
２ｆ: Discharge pressure chamber
3: compression mechanism
４: electric motor
４a: Stator
４ｂ: Rotor
5: fixed scroll
5c: Wrap
5d: Bottom plate
５ｅ: discharge port
５ｆ: Spring Storage Hole
5 g: through hole
５ｈ: RM home
５ｉ: Through road
５Ｘｉ: The winding end of the extension wrap on the fixed scroll 5
５Ｘｏ: Winding end of the outer line wrap of the fixed scroll 5
6: scroll scroll
６ a: Wrap
６ｂ: Bottom plate
６c: Slewing Bearing
６Ｘｉ: winding end of the inner side wrap of the turning scroll 6
６Ｘｏ: Winding end part of outer side lap of turning scroll 6
7: crankshaft
７ a: Main axis
７ｂ: Eccentricity
７c: oil supply passage
7d: Refueling pipe
７ｚ: Hole
８: Bolt
９: Frame
９ａ: Main bearing
10: suction space
11: compression chamber
１ＡＡ: Virtual turning cabin
11a: Turning Outer Cabin
11 a ': Turning outside room
１１Ｂ: Virtual turning station
１１ｂ: Turning station
11 ': Turning station
12: Oldham Ring
13. Lubricant
14. Back pressure chamber
１５: Release valve
15a: release valve hole
１６: Back pressure control valve
16 a: piece
１６ｂ: Communication hole
16c: Valve body
16d: spring
１６ｅ: sealing member
１７: Lower bearing
１８: communication hole
１１１１１１２: Gap
20: concave
25: control unit
２６: Reheating Heat Exchanger
２９: Water-Refrigerant Heat Exchanger
30: remote controller
３１: water circulation pump
３２: Storage tank
３３: expansion valve
３４: Evaporator
35: tapping temperature sensor
36: discharge gas temperature sensor
50: oil supply part
５１: discharge pressure oil supply room
110: Oil Pocket
110: Sealing
10: Refueling pump

Claims (15)

In the scroll compressor of the intermittent communication structure which presses a turning scroll to a fixed scroll by the back pressure controlled by the back pressure control valve, and compresses a refrigerant | coolant in the compression chamber formed by both scrolls,
When the volume of both the suction chamber on the inner side of the swing scroll and the suction chamber on the outer side of the swing scroll increases, the back pressure control valve is arranged at a position at which communication start of intermittent communication is performed. compressor. The virtual line which connected the winding end part of the inner side wrap of the said fixed scroll, and the winding end part of the outer side wrap of the said turning scroll, the outer side wrap of the said turning scroll, and the inner side wrap of the said fixed scroll. The back pressure control valve and the back pressure chamber communicate with each other when the volume of the virtual swinging outer chamber, which is one of the suction chambers, is increasing.
Of the suction chamber surrounded by an imaginary line connecting the winding end of the outer wrap of the fixed scroll and the winding end of the wrapping of the inner wrap of the turning scroll, the inner wrap of the turning scroll, and an outer wrap of the fixed scroll. And the back pressure control valve is disposed at a position where the back pressure control valve and the back pressure chamber communicate with each other when the volume of one virtual swinging interior chamber increases. 2. The volume of both the suction chamber on the inner side of the swing scroll and the suction chamber on the outer side of the swing scroll is up to the respective volumes when the respective compression chambers are closed spaces. And the back pressure control valve is disposed at a position where communication start of intermittent communication is performed when increasing. The swing chamber according to claim 1, wherein the compression chamber is a swing inner chamber and a swing outer chamber formed on the inner side of the swing scroll and the outer side of the swing scroll, and the suction chamber on the inner side of the swing scroll is the swing inner chamber. When it increases until it becomes the same volume as when it became, and also when it increases until it becomes the same volume as when it became the said turning outer chamber, the suction chamber of the outer side of the said turning scroll intermittently A scroll compressor, wherein the back pressure control valve is disposed at a position at which communication start of communication is performed. The scroll compressor according to claim 1, wherein the back pressure control valve is disposed at a position of 270 ° to 330 ° in the rewinding direction of the wrap of the wrap of the fixed scroll. In a scroll compressor having a two end oil supply structure for pressurizing the swing scroll against a fixed scroll by back pressure, which is the pressure of the back pressure chamber provided on the side opposite to the swing scroll, and compressing the refrigerant in the compression chamber formed by both scrolls. And lubricating the tip end portion of the compression chamber via a space provided at a position deeper than the root of the fixed scroll. The said turning scroll has a communication hole in the said wrap which has a tooth opening which is provided in the end which is an end surface of a wrap, and the opposite wrap side opening provided in the opposite wrap side with respect to the base plate of the said scroll scroll, By the orbital movement of the scroll, the space and the tip opening are intermittently connected, and the space is provided on the opposite wrap side of the swing scroll, and the space which becomes the pressure above the back pressure and the opening on the opposite wrap side communicate with each other. The end of lubrication to the said compression chamber from the space which becomes, and a scroll compressor. The said fixed scroll has a release valve which releases the pressure of the said compression chamber in the airtight container of the said scroll compressor, The space provided in the position deeper than the root of the said fixed scroll has The space | pressure which is a release valve hole, and becomes the pressure more than the said back pressure is the said scroll pressure chamber. The scroll compressor according to claim 7, wherein the space provided at a position deeper than the root of the fixed scroll is a recess provided in the fixed scroll, and the space at which the pressure is equal to or greater than the back pressure is the back pressure chamber. The scroll compressor according to claim 7, wherein the space at which the pressure is equal to or greater than the back pressure is on the side opposite to the swing scroll, and is a discharge pressure oil supply chamber into which oil at a pressure in the sealed container of the scroll compressor is introduced. In a sealed container,
Fixed scroll with vortex wrap,
A swinging scroll having a spiral wrap and at the same time engaged with the wrap of the fixed scroll to form a compression chamber for compressing the refrigerant, and an orbiting motion relative to the fixed scroll based on the rotation of the crankshaft;
A back pressure control valve for controlling the pressure of the back pressure chamber formed on the side of the lap opposite to the swing scroll;
A release valve disposed in the fixed scroll, and having a release valve for discharging the refrigerant in the compression chamber into the hermetic container when the pressure in the compression chamber is greater than the pressure in the hermetic container,
A scroll compressor in which the back pressure control valve and the back pressure chamber intermittently communicate,
A virtual turning cabin surrounded by an imaginary line connecting the winding end portion of the inner side wrap of the fixed scroll and the winding end portion of the outer side wrap of the turning scroll, the outer side wrap of the turning scroll, and the inner side wrap of the fixed scroll. Is a position where the back pressure control valve and the back pressure chamber communicate when the volume of the crank shaft increases with the rotation of the crankshaft, and the winding end of the outer wrap of the fixed scroll and the inner wrap of the swing scroll. The back pressure control valve and the valve when the volume of the imaginary swivel inner space surrounded by the imaginary line connecting the winding end, the inner lap of the swing scroll, and the outer lap of the fixed scroll increases with the rotation of the crankshaft. The back pressure control valve is arranged at a position where the back pressure chamber communicates,
The pivoting scroll has a communication hole in the wrap having an end opening provided at the end of the wrap, which is an end face of the wrap, and an opposite wrap side opening provided at the side opposite to the bottom plate of the swinging scroll,
By the orbital movement of the said revolving scroll, the tooth opening and the release valve hole of the release valve intermittently communicate,
The back pressure chamber and the opposite wrap side opening communicate with each other,
And the back pressure chamber communicates with the compression chamber. The scroll compressor according to claim 8 or 11, wherein the compression chamber is a swing outer chamber which is a compression chamber formed on an outer diameter side of a wrap of the swing scroll. The said fixed scroll has a 2nd release valve which releases the pressure of the turning internal chamber formed in the inner diameter side of the lap of the said rotating scroll in the compression container among the said compression chambers,
The pivoting scroll has a second communication hole in the wrap having a second tip opening provided at the end of the wrap, and a second counter wrap opening at the opposite wrap side with respect to the bottom plate of the swing scroll,
By the orbital motion of the turning scroll, the second tooth opening and the release valve hole of the second release valve intermittently communicate,
The back pressure chamber communicates with the second opposite wrap side opening;
A scroll compressor, wherein the back pressure chamber and the swinging station chamber communicate with each other. In the refrigeration cycle apparatus that sequentially connected the discharge pipe of the scroll compressor, the first heat exchanger, the expansion device, the second heat exchanger, and the suction pipe of the scroll compressor,
The scroll compressor according to any one of claims 1, 6 and 11 is used as the scroll compressor.
A refrigeration cycle apparatus, wherein a supercritical refrigeration cycle in which the refrigerant is carbon dioxide is configured. A refrigeration cycle apparatus according to claim 14, a water storage tank, a water-refrigerant heat exchanger, a water circulation pump,
The first heat exchanger is used as the water-refrigerant heat exchanger, and the water is heated to the water-refrigerant heat exchanger by driving water from the water storage tank by operating the water circulation pump, and the heated water is returned to the water storage tank. Become,
The bottom pump water heater is hot water stored in the storage tank is hot water supply to the terminal.

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