WO2014196314A1

WO2014196314A1 - Scroll compressor and air conditioner using same

Info

Publication number: WO2014196314A1
Application number: PCT/JP2014/062650
Authority: WO
Inventors: 近野　雅嗣; 柳瀬　裕一; 土屋　豪
Original assignee: 日立アプライアンス株式会社
Priority date: 2013-06-03
Filing date: 2014-05-13
Publication date: 2014-12-11
Also published as: JP6143862B2; JPWO2014196314A1

Abstract

　Oil flowing from a rear pressure chamber to an intake chamber or a compression chamber via a rear pressure valve is sufficiently supplied not only to a lap tooth tip of a fixed scroll, but also to gaps between fixed scroll tooth bottoms and lap tooth tips of an orbiting scroll. A scroll compressor is provided with a fixed scroll (7), an orbiting scroll (8) that forms an intake chamber (20) or a compression chamber by meshing with the fixed scroll and undergoing an orbiting motion, a rear pressure chamber (18) for applying pressure to the orbiting scroll toward the fixed scroll, a rear pressure valve (61) for adjusting the rear pressure of the rear pressure chamber, a rear pressure valve inflow channel (61a) for connecting an inlet side of the rear pressure valve and the rear pressure chamber, and a rear pressure valve outflow channel (61b) for connecting an outlet side of the rear pressure valve and either the intake chamber or the compression chamber. At least part of a flow channel outlet part (61g) leading to the intake chamber or compression chamber of the rear pressure valve outflow channel is formed nearer the tooth bottoms (7c) than the positions of the lap teeth tips of the fixed scroll.

Description

Scroll compressor and air conditioner using the same

The present invention relates to a scroll compressor and an air conditioner using the scroll compressor, and is particularly suitable as a scroll compressor used in an air conditioner that emphasizes low speed and low load operation.

Examples of scroll compressors used in refrigeration cycle apparatuses for refrigeration and air conditioning include those described in Japanese Patent Application Laid-Open No. 2005-163655 (Patent Document 1). The thing of this patent document 1 has a fixed scroll (non-orbiting scroll) which has a base plate (end plate) and a wrap (vortex body) standing upright on it, an end plate (end plate) and a wrap (vortex body) upright on it. ), And a revolving scroll that engages with the fixed scroll and forms a suction chamber or a compression chamber with the fixed scroll, and applies a pressing force to the fixed scroll to the revolving scroll. Back pressure chamber, back pressure chamber fluid inflow means for allowing fluid to flow into the back pressure chamber in order to maintain the pressure (back pressure) of the back pressure chamber, at least one of the fluid flowing into the back pressure chamber There is described a scroll compressor provided with back pressure chamber fluid outflow means and the like for allowing a part to flow out into the suction chamber or the compression chamber.

Further, in Patent Document 1, the back pressure chamber fluid outflow means controls a differential pressure across the back pressure chamber fluid outflow path that connects the back pressure chamber and the suction chamber or the compression chamber. A structure is described in which a (back pressure control valve), a throttle channel portion, and an intermittent channel portion that communicates intermittently by the orbiting motion of the orbiting scroll member are arranged in series.

JP 2005-163655 A

In the thing of the said patent document 1, since the said throttle flow path part is formed in the end-plate surface of the said fixed scroll, from this back pressure chamber via the said throttle flow path part, the said suction chamber or the compression chamber Oil (lubricating oil, refrigerating machine oil) that flows into the fixed scroll is supplied only to the wrap tooth tip side of the fixed scroll, such as a gap between the wrap tooth tip of the fixed scroll and the orbiting scroll tooth bottom. Therefore, there is a problem that the refrigerating machine oil in the back pressure chamber cannot be sufficiently supplied to the gap between the bottom of the fixed scroll and the lap tooth tip of the orbiting scroll through the back pressure chamber fluid outflow means.

The object of the present invention is to allow oil flowing into the suction chamber or the compression chamber from the back pressure chamber via the back pressure valve not only between the wrap tooth tip side of the fixed scroll but also between the fixed scroll tooth bottom and the wrap tooth tip of the orbiting scroll. The object is to obtain a scroll compressor capable of sufficiently supplying gaps and an air conditioner using the scroll compressor.

In order to solve the above-described problems, the present invention provides a fixed scroll in which a spiral wrap is erected on a base plate, and a spiral wrap is erected on an end plate and meshed with the fixed scroll to perform a turning motion. A revolving scroll that forms a suction chamber or a compression chamber; a back pressure chamber that applies a pressing force to the revolving scroll toward the fixed scroll; a back pressure valve for adjusting the back pressure of the back pressure chamber; A scroll compressor comprising a back pressure valve inflow passage that communicates the inlet side of the pressure valve and the back pressure chamber, and a back pressure valve outflow passage that communicates the outlet side of the back pressure valve and the suction chamber or the compression chamber. At least a part of a flow path outlet portion of the pressure valve outflow passage to the suction chamber or the compression chamber is formed on the tooth bottom side with respect to the position of the wrap tooth tip of the fixed scroll.

Another feature of the present invention is an air conditioner configured by sequentially connecting a compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger with a refrigerant pipe, and the compressor includes the scroll This scroll compressor is to be operated at a low speed of at least 10 to 30 Hz.

According to the present invention, the oil flowing from the back pressure chamber into the suction chamber or the compression chamber via the back pressure valve is not limited to the fixed scroll lap tooth tip side but also between the fixed scroll tooth bottom and the orbiting scroll lap tooth tip. There is an effect that a scroll compressor that can be sufficiently supplied to the gap and an air conditioner using the scroll compressor can be obtained.

The longitudinal cross-sectional view explaining the basic structure of a scroll compressor. The top view explaining the meshing state of the fixed scroll and turning scroll in FIG. The expanded sectional view of the back pressure valve periphery shown in FIG. FIG. 4 is a diagram illustrating the first embodiment of the scroll compressor according to the present invention and corresponding to FIG. 3. The perspective view which looked at the fixed scroll shown in FIG. 4 from the downward direction. FIG. 4 is a diagram illustrating a scroll compressor according to a second embodiment of the present invention and corresponding to FIG. 3. FIG. 6 is a diagram showing a third embodiment of the scroll compressor according to the present invention and corresponding to FIG. 3. The refrigeration cycle block diagram explaining an example of the air conditioner using the scroll compressor of this invention.

Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. Note that, in each drawing, the portions denoted by the same reference numerals indicate the same or corresponding portions.

The basic structure of the scroll compressor to which this embodiment is applied will be described with reference to FIGS. 1 is a longitudinal sectional view illustrating the basic structure of a scroll compressor, FIG. 2 is a plan view illustrating the meshing state of the fixed scroll and the orbiting scroll in FIG. 1, and FIG. 3 is a view around the back pressure valve shown in FIG. It is an expanded sectional view.

First, the overall configuration of the scroll compressor will be described with reference to FIG. The scroll compressor 1 is configured by housing a compression mechanism section 2 and a motor section 16 in a case (sealed container) 9.

In the compression mechanism section 2, the orbiting scroll 8 is meshed with the fixed scroll 7 fixed to the frame 17 to form a compression chamber 13, and the rotation of the motor section 16 causes the above-described operation via the crankshaft (rotating shaft) 10. By orbiting the orbiting scroll 8, the volume of the compression chamber 13 is reduced and the compression operation is performed. With this compression operation, the working fluid is sucked into the suction chamber 20 (see FIG. 2) from the suction port 14, and the sucked working fluid is discharged from the discharge port 15 into the case 9 through the compression stroke in the compression chamber 13. It is discharged into the space 54. The working fluid discharged into the discharge space 54 flows into the motor chamber 52 through a passage (not shown) formed in the outer periphery of the fixed scroll and the outer periphery of the frame 17, and then from the discharge pipe 6 to the case 9. It is configured to be discharged outside.

The fixed scroll 7 is a disc-shaped base plate 7a, a wrap 7b provided upright in a spiral shape on the base plate 7a, and is positioned on the outer peripheral side of the base plate 7a, and is continuous with the front end surface of the wrap 7b. And a cylindrical support portion 7d that surrounds the wrap 7b. The surface of the base plate 7a on which the wrap 7b is erected is called a tooth bottom 7c because it is between the wraps 7b.

The surface where the support portion 7d of the fixed scroll 7 is in contact with the end plate 8a of the orbiting scroll 8 is the end plate surface 7e of the fixed scroll 7. The fixed scroll 7 has the support portion 7d fixed to the frame 17 with bolts or the like, and the frame 17 integrally coupled with the fixed scroll 7 is fixed to the case (sealed container) 9 by fixing means such as welding. Has been.

The orbiting scroll 8 is disposed so as to face the fixed scroll 7, and the fixed scroll wrap 7 b and the orbiting scroll wrap 8 b are engaged with each other so that the orbiting scroll 8 is provided within the frame 17. The orbiting scroll 8 includes a disc-shaped end plate 8a, a spiral wrap 8b erected from a tooth bottom 8c which is the surface of the end plate 8a, and a boss portion (orbiting boss portion) provided at the center of the rear surface of the end plate 8a. ) 8d. Further, the surface of the outer peripheral portion of the end plate 8 a that contacts the fixed scroll 7 is the end plate surface 8 e of the orbiting scroll 8.

The tip (wrap tooth tip) of the wrap 8b of the orbiting scroll 8 is in a state of facing the tooth bottom 7c of the fixed scroll 7 with a minute gap. Similarly, the tip end portion (wrap tooth tip) of the wrap 7b of the fixed scroll 7 is also in a state of facing the tooth bottom 8c of the orbiting scroll 8 with a minute gap.

An oil sump 53 for storing lubricating oil (refrigerating machine oil) is provided at the bottom of the case 9 having a sealed container structure that accommodates the compression mechanism section 2 and the motor section 16. The motor section 16 is composed of a rotor 16a and a stator 16b, and a crankshaft (rotary shaft) 10 is integrally fixed to the rotor 16a. The crankshaft 10 is rotatably supported by the frame 17 via the main bearing 5 and is coaxial with the central axis of the fixed scroll 7.

An eccentric crank portion 10a is provided at the tip of the crankshaft 10, and this crank portion 10a is inserted into the orbiting bearing 11 provided in the boss portion 8d of the orbiting scroll 8, and the orbiting scroll 8 is It is configured to be able to turn with the rotation of the shaft 10. The center axis of the orbiting scroll 8 is decentered by a predetermined distance with respect to the center axis of the fixed scroll 7. The wrap 8b of the orbiting scroll 8 is overlapped with the wrap 7b of the fixed scroll 7 while being shifted by a predetermined angle (generally 180 degrees) in the circumferential direction. Reference numeral 12 denotes an Oldham ring for relatively rotating the orbiting scroll 8 with respect to the fixed scroll 7 while restraining it from rotating.

FIG. 2 is a plan view for explaining the meshing state of the fixed scroll 7 and the orbiting scroll 8. The wrap 8b of the orbiting scroll 8 is shown in a sectional view, and the outer periphery of the end plate 8a of the orbiting scroll is shown by an phantom line of a two-dot chain line. Show. As shown in FIG. 2, a plurality of crescent-shaped compression chambers 13 (orbiting inner line side compression chambers 13a and orbiting outer line side compression chambers 13b) are formed between the fixed scroll wrap 7b and the orbiting scroll wrap 8b. When the is swung, the volume of each compression chamber 13 is continuously reduced as it moves to the center. Reference numeral 20 denotes a suction chamber, which is a space in the middle of sucking fluid. The suction chamber 20 becomes the compression chamber 13 when the phase of the orbiting motion of the orbiting scroll 8 advances and the closing of the fluid is completed.

The suction port 14 is provided in the fixed scroll 7 as shown in FIGS. 1 and 2. The suction port 14 is formed on the outer peripheral side of the base plate 7 a of the fixed scroll 7 so as to communicate with the suction chamber 20.
The discharge port 15 is formed near the spiral center of the base plate 7a of the fixed scroll 7 so as to communicate with the compression chamber 13 on the innermost peripheral side.

When the crankshaft 10 is rotated by the motor unit 16, the orbiting scroll 8 orbits around the central axis of the fixed scroll 7 with an orbiting radius of a predetermined distance. It is restrained by the Oldham ring 12 so that the turning scroll 8 does not rotate during this turning movement.

The revolving motion of the orbiting scroll 8 causes the compression chamber 13 formed between the

laps

7b and 8b to continuously move to the center, and the volume is continuously reduced accordingly. Thus, the working fluid sucked from the suction port 14 (for example, refrigerant gas circulating in the refrigeration cycle, hereinafter also simply referred to as fluid) is sequentially compressed in each compression chamber 13, and the compressed working fluid is It is discharged from the discharge port 15 into the discharge space 54 and supplied from the discharge pipe 6 to, for example, a refrigeration cycle outside the compressor as described above.

A positive-displacement or centrifugal oil pump 21 is provided at the lower end of the crankshaft 10, and the oil pump 21 is rotated along with the rotation of the crankshaft 10, and is stored in an oil sump 53 at the bottom of the case 9. Lubricating oil is drawn in from a lubricating oil suction port 25 provided in the oil supply pump case 22 and discharged from a discharge port 28 of the oil supply pump 21. The discharged lubricating oil is sent to the upper end of the crank portion 10a through a through hole (oil supply hole) 3 formed in the crankshaft 10 in the axial direction.

At this time, a part of the lubricating oil flowing through the through hole 3 is sent to the auxiliary bearing 23 through the lateral hole 24 provided in the crankshaft 10, and after lubricating the auxiliary bearing 23, the oil reservoir at the bottom of the case 9 is Return to 53. Most of the other lubricating oil flowing through the through hole 3 of the crankshaft 10 reaches the upper end of the crank portion 10a, and lubricates the slewing bearing 11 through an oil groove 57 provided in the crank portion 10a. Thereafter, the lubricating oil further lubricates the main bearing 5 provided at the lower portion of the slewing bearing 11, and then returns to the bottom of the case 9 through the oil drain hole 26a and the oil drain pipe 26b.

Here, a space formed by the oil groove 57 and the slewing bearing 11, and a space for housing the main bearing 5 (the frame 17, the crankshaft 10, the frame seal 56, the collar portion 34 provided on the slewing boss portion 8d, the seal member). The space formed by 32) is collectively referred to as a first space 33. The first space 33 is a space having a pressure close to the discharge pressure.

Most of the lubricating oil flowing into the first space 33 for lubrication of the main bearing 5 and the slewing bearing 11 passes through the oil drain hole 26a and the oil drain pipe 26b and is stored in the bottom of the case 9. Returning to 53, a part of the lubricating oil is necessary for the lubrication of the Oldham ring 12, the lubrication of the sliding portion between the fixed scroll 7 and the orbiting scroll 8, and the seal (sealing) such as the clearance between the tips of each lap. A minimum amount enters the back pressure chamber 18 which is the second space through an oil leakage means provided between the upper end surface of the seal member 32 and the end surface of the collar portion 34 of the turning boss portion.

The seal member 32 is inserted together with a wave spring (not shown) into an annular groove 31 provided on a surface of the frame 17 facing the collar portion 34, and the first pressure which is a discharge pressure. The space 33 is partitioned from the back pressure chamber (second space) 18 which is an intermediate pressure between the suction pressure and the discharge pressure. The oil leakage means includes, for example, one or a plurality of slits 60 provided in the collar portion 34 of the turning boss portion and the seal member 32, and the slit 60 is disposed so as to straddle the seal member 32. . As a result, due to the pressure difference between the first space 33 and the back pressure chamber 18, oil flows from the first space 33 into the back pressure chamber 18 through the slit 60, which is a minute gap.

The back pressure chamber 18 and the suction chamber 20 (or the compression chamber 13) are connected (communicated) by a back pressure chamber fluid outflow passage provided in the support portion 7d of the fixed scroll 7. The back pressure chamber A back pressure valve (back pressure control valve) 61 for controlling the differential pressure across the front and rear is provided in the middle of the fluid outflow path. As a result, when the back pressure increases, the lubricating oil that has entered the back pressure chamber 18 flows into the suction chamber 20 (or the compression chamber 13) through the back pressure valve 61, and the lap sliding surface and the lap tip clearance. Are used for sealing between the compression chambers and the like, and then discharged from the discharge port 15 into the discharge space 54. A part of the discharged oil is discharged together with the refrigerant gas from the discharge pipe 6 to the refrigeration cycle, for example, and the rest is separated from the refrigerant gas in the case 9 and stored in the oil reservoir 53 at the bottom of the case.

As described above, by providing the first space 33, the back pressure chamber 18, and the oil leakage means, the amount of oil required for each bearing portion and the amount of oil required for the compression chamber 13 are independently controlled. Therefore, the amount of oil supplied to the compression chamber 13 can be optimized, and a highly efficient scroll compressor can be obtained.

As another configuration, the oil pump 21, the first space 33, and the oil leakage means are not provided, and the oil in the oil pool 53, which is a discharge pressure, is used by using a restriction in a minute gap of the bearing portion. The pressure may be reduced and introduced into the back pressure chamber 18. In this case, since all the oil that has passed through the bearing portion flows into the back pressure chamber 18, the amount of oil supplied to the bearing portion and the compression chamber cannot be controlled independently. However, since parts such as the oil pump 21 and the seal member 32 are not required, a scroll compressor having a simple structure and a low cost can be obtained.

Next, the function of the back pressure chamber 18 will be described. In the scroll compressor 1, an axial force (separation force) that causes the fixed scroll 7 and the orbiting scroll 8 to be separated from each other is generated by the compression action. When the so-called orbiting scroll 8 separation phenomenon occurs in which the two scrolls are separated by this axial force, the sealing performance of the compression chamber 13 deteriorates and the compressor efficiency is lowered. Therefore, a back pressure chamber 18 which is a pressure between the discharge pressure and the suction pressure is provided on the back side of the end plate 8 a of the orbiting scroll 8, and the pulling force is canceled by the pressure (back pressure) of the back pressure chamber 18. The orbiting scroll 8 is pressed against the fixed scroll 7.

If the pressing force at this time is too large, sliding loss between the end plate surface 8e of the orbiting scroll 8 and the end plate surface 7e of the fixed scroll 7 increases, and the compressor efficiency decreases. In other words, there is an optimum value for the back pressure. If the back pressure is too small, the sealing performance of the compression chamber is deteriorated and the thermal fluid loss increases. Therefore, maintaining the back pressure at an optimum value is important in improving the performance and reliability of the compressor.

In order to obtain the optimum back pressure value, the scroll compressor shown in FIG. 1 includes the back pressure chamber fluid outflow passage having the back pressure valve 61 for adjusting the back pressure of the back pressure chamber 18. . The configuration around the back pressure valve 61 shown in FIG. 1 will be described with reference to an enlarged view shown in FIG.
The back pressure chamber fluid outflow path includes a back pressure valve inflow path (a space communicating with the back pressure chamber 18) 61a communicating the back pressure chamber 18 and the back pressure valve 61, the back pressure valve 61 and the suction chamber 20 (or It is constituted by a back pressure valve outflow passage (a space communicating with the suction chamber 20 (or the compression chamber 13)) 61b communicating with the compression chamber 13) and a space 61c for accommodating the back pressure valve 61. Further, the back pressure valve outflow passage 61b opens on the back pressure valve 61 side to the hole-shaped upstream outflow passage 61ba and the suction chamber 20 (or the compression chamber 13), and is formed on the end plate surface 7e of the fixed scroll 7. It is comprised by the downstream side outflow path 61bb of the groove shape.

The back pressure valve 61 is accommodated in the space 61c, and communicates with the back pressure valve inflow path (space communicating with the back pressure chamber 18) 61a and the back pressure valve outflow path (suction chamber 20 (or compression chamber 13)). A valve 61d is arranged so as to partition the space 61b. The valve 61d is pressed against an opening communicating with the back pressure valve inflow passage 61a by a spring 61f fixed to the stopper 61e.

The valve 61d is configured such that the pressure in the back pressure valve inflow passage 61a, that is, the pressure in the space 61c through which the back pressure is introduced through the back pressure valve outflow passage 61b (the pressure in the suction chamber 20 (or the compression chamber 13)). ) And the total pressure corresponding to the pressing force of the spring 61f, the back pressure valve inflow path 61a and the back pressure valve outflow path 61b are communicated with each other. That is, the back pressure valve 61 allows the fluid in the back pressure chamber 18 to escape to the suction chamber 20 or the compression chamber 13 when the pressure in the back pressure chamber 18 becomes higher than a certain value. The back pressure of the pressure chamber 18 is adjusted to an appropriate value.

The oil released to the suction chamber 20 or the compression chamber 13 through the back pressure valve outflow passage 61b has a function of sealing and lubricating the compression chamber 13, so that the amount of this oil is set to an appropriate value. As a result, the compressor can be improved in performance and reliability.

The above is the basic structure of the scroll compressor. By using the scroll compressor having such a structure, the back pressure value of the back pressure chamber 18 can be properly maintained by the back pressure valve 61, and By adjusting the oil leakage means, the amount of oil that flows into the back pressure chamber 18 from the first space 33 and reaches the suction chamber 20 or the compression chamber 13 via the back pressure valve 61 is set appropriately. It is also possible to do.

However, in the scroll compressor having the above-described structure, the oil flowing out to the back pressure valve outflow passage 61b via the back pressure valve 61 flows from the downstream outflow passage 61bb formed in the end plate surface 7e of the fixed scroll 7 from the downstream outflow passage 61bb. Since it is configured to flow into the suction chamber 20 (or the compression chamber 13), the outlet portion 61g of the downstream outflow passage 61bb is positioned close to the tooth bottom 8c of the orbiting scroll 8 or its end plate surface 8e. Therefore, although the oil is supplied between the lap tooth tip of the fixed scroll 7 and the tooth bottom 8c of the orbiting scroll 8, the gap between the tooth bottom 7c of the fixed scroll 7 and the lap tooth tip of the orbiting scroll 8 is provided. It was difficult for oil to be supplied. Therefore, in the scroll compressor described above, only the lap tooth tip side of the fixed scroll 7 to which oil is easily supplied is mainly sealed, and the clearance between the tooth bottom 7c of the fixed scroll 7 and the wrap tooth tip of the orbiting scroll 8 is sealed. Insufficient oil could not be supplied, and the compression chamber 13 could not be said to have high sealing performance.

Therefore, in this embodiment, oil flows from the back pressure chamber 18 into the suction chamber 20 or the compression chamber 13 via the back pressure valve 61, that is, flows into the suction chamber 20 or the compression chamber 13 from the back pressure valve outflow passage 61b. The oil can be sufficiently supplied not only to the lap tooth tip side of the fixed scroll 7 but also to the gap between the tooth bottom 7 c of the fixed scroll 7 and the wrap tooth tip of the orbiting scroll 8.

Hereinafter, a specific configuration of the scroll compressor according to the first embodiment will be described with reference to FIGS. 4 and 5. 4 is a view corresponding to FIG. 3, and FIG. 5 is a perspective view of the fixed scroll shown in FIG. 4 as viewed from below. In FIGS. 4 and 5, the same reference numerals as those in FIGS. 1 to 3 are the same or corresponding parts, and the description of the same parts is omitted. The basic structure of the scroll compressor is the same as that shown in FIGS. 1 to 3 except for the back pressure valve outflow passage 61b shown in FIGS.

As shown in FIG. 4, in the present embodiment as well, as in the scroll compressor shown in FIGS. 1 to 3, a back pressure chamber 18 that applies a pressing force to the orbiting scroll 8 toward the fixed scroll 7, and the back pressure chamber The back pressure chamber fluid outflow passage having the back pressure valve 61 for adjusting the back pressure of 18 is provided. The back pressure chamber fluid outflow path includes the back pressure valve inflow path 61a communicating the back pressure chamber 18 and the inlet side of the back pressure valve 61, the outlet side of the back pressure valve 61, and the suction chamber 20 (or the compression chamber). 13), the back pressure valve outflow passage 61b communicating with the back pressure valve 61, and the space 61c in which the back pressure valve 61 is accommodated. Further, the back pressure valve outflow passage 61b opens on the upstream pressure outflow passage 61ba having a hole shape on the back pressure valve 61 side and the suction chamber 20 (or the compression chamber 13), and is formed on the end plate surface 7e of the fixed scroll 7. It is comprised by the downstream side outflow path 61bb of the groove shape.

In this embodiment, the configuration of the back pressure valve inflow passage 61a, the back pressure valve 61, and the space 61c that accommodates the back pressure valve 61 is the same as that shown in FIG. Further, the shape of the upstream side outflow passage 61ba constituting the back pressure valve outflow passage 61b is also a hole shape (the cross section is a hole shape such as a circle, an ellipse, or a rectangle) as shown in FIG. .

However, in this embodiment, the configuration of the downstream side outflow passage 61bb in the back pressure valve outflow passage 61b is greatly different from the configuration shown in FIG. That is, as shown in FIG. 4, the flow passage inlet 61h side of the downstream outflow passage 61bb has a flow passage sectional area similar to that of the downstream outflow passage 61bb shown in FIG. Alternatively, the flow passage cross-sectional area on the flow passage outlet 61g side of the downstream outflow passage 61bb opened to the compression chamber 13) is configured to be larger than that on the flow passage inlet 61h side. As shown in FIGS. 4 and 5, such a configuration can be realized by forming a bottom 61i on the outlet side of the downstream outflow passage 61bb into a tapered shape.

By setting it as the said structure, at least one part of the said flow-path exit part 61g to the said suction chamber 20 (or compression chamber 13) of the said back pressure valve outflow path 61b is made rather than the position of the lap tooth tip of the said fixed scroll 7. It can be formed on the tooth bottom 7c side. In the present embodiment shown in FIG. 4, the position of the flow passage outlet 61g on the tooth bottom 7c side of the fixed scroll 7 is near the intermediate position in the height direction of the fixed scroll wrap 7b (or the orbiting scroll wrap 8b). It is configured.

Note that the position of the flow path outlet 61g on the tooth bottom 7c side is not limited to the example shown in FIG. 4, and is closer to the tooth bottom 7c side than the intermediate position in the height direction of the wrap 7b (8b). If so, more oil can be supplied to the tooth bottom side. Further, if the position on the tooth bottom 7c side of the flow path outlet portion 61g is located closer to the tooth bottom 8c side of the orbiting scroll 8 than the intermediate position in the height direction of the wrap 7b (8b), the downstream outflow path 61bb. The groove processing becomes easier.

Since the first embodiment has the above-described configuration, the oil flowing into the back pressure valve outflow passage 61b from the back pressure valve 61 is sucked into the suction chamber 20 (or the compression chamber 13) from the flow passage outlet 61g of the downstream outflow passage 61bb. Since the oil flows into the direction of the fixed scroll tooth bottom 7c as well as the direction of the orbiting scroll tooth bottom 8c, the oil flows between the lap tooth tips and the tooth bottom gaps of the

scrolls

7, 8. Can supply.

As described above, according to this embodiment, the oil flowing from the back pressure chamber into the suction chamber or the compression chamber via the back pressure valve is fixed not only in the gap between the fixed scroll wrap tooth tip and the orbiting scroll tooth bottom 8c. Since the gap between the scroll tooth bottom 7c and the orbiting scroll wrap tooth tip can be sufficiently supplied and the oil can be distributed almost uniformly to the suction chamber 20 (or the compression chamber 13), the oil suction chamber 20 and the compression chamber are made of oil. Thus, a highly efficient scroll compressor with a small leakage loss can be obtained.

Embodiment 2 of the scroll compressor according to the present invention will be described with reference to FIG. FIG. 6 is a diagram corresponding to FIG. 3, and the portions denoted by the same reference numerals as those in FIGS. 3 and 4 indicate the same or corresponding portions. The basic structure of the scroll compressor is the same as that shown in FIGS. 1 to 3 except for the back pressure valve outflow passage 61b shown in FIGS.

In the second embodiment, the upstream side outflow passage 61ba constituting the back pressure valve outflow passage 61b is the same as that in the first embodiment. In the present Example 2, the structure of the downstream outflow path 61bb which comprises the said back pressure valve outflow path 61b differs from the said Example 1. FIG. That is, as shown in FIG. 6, the flow passage inlet 61h side of the downstream outflow passage 61bb has a flow passage sectional area similar to that of the downstream outflow passage 61bb shown in FIG. 4, and the suction chamber 20 (or the compression chamber 13). This is also the same in that the flow passage cross-sectional area on the flow passage outlet portion 61g side of the downstream outflow passage 61bb that is open to the flow passage) is larger than that on the flow passage inlet portion 61h side.

However, in the second embodiment, the bottom 61i on the outlet side of the downstream outflow passage 61bb is not linearly tapered as shown in FIG. 4, but the bottom 61i is formed in an arc shape. The shape of the bottom 61i is not limited to a circular arc, but may be a curve other than an arc such as a parabola, or a combination of a curve and a straight line. Alternatively, the edge portions on the flow channel inlet portion 61h side and the flow channel outlet portion 61g side of the tapered bottom portion 61i shown in FIG. 4 may be rounded or formed in an arc.

That is, the flow path outlet 61g side in the back pressure valve outflow path 61b is formed in a shape that combines a curve or a curve and a straight line so that the flow area increases toward the flow path outlet. What is necessary is just to form so that the cross-sectional area of a flow-path exit may become larger than a cross-sectional area.

If the back pressure valve outflow passage 61b is configured in this way, the same effect as in the first embodiment described above can be obtained, and separation of the oil flow along the wall surface of the bottom portion 61i of the downstream outflow passage 61bb can be suppressed. Since the oil flowing into the suction chamber 20 or the compression chamber 13 can be diffused more smoothly and efficiently, the hermetic sealing of the suction chamber 20 and the compression chamber 13 with oil is further improved, and a highly efficient scroll compressor with less leakage loss is obtained. be able to.

Embodiment 3 of the scroll compressor according to the present invention will be described with reference to FIG. FIG. 7 is also a view corresponding to FIG. 3, and the portions denoted by the same reference numerals as those in FIGS. 3, 4, and 6 indicate the same or corresponding portions. The basic structure of the scroll compressor is the same as that shown in FIGS. 1 to 3 except for the back pressure valve outflow passage 61b shown in FIGS.

In the third embodiment, the upstream outflow passage 61ba constituting the back pressure valve outflow passage 61b is the same as in the first and second embodiments. In the third embodiment, the downstream side outflow passage 61bb constituting the back pressure valve outflow passage 61b is different from the first and second embodiments. That is, in the third embodiment, the downstream outflow passage 61bb shown in the first and second embodiments is formed in the groove 61k on the flow path inlet 61h side and the hole 61j formed obliquely on the flow outlet 61g side. It is characterized in that it consists of Further, in the example shown in FIG. 7, the position of the hole 61j on the outlet side (outlet part 61g side) is closer to the fixed scroll tooth bottom 7c than the position on the inlet side (groove part 61k side). It is composed.

With this configuration, the oil flows into the suction chamber 20 (or the compression chamber 13) in the same manner as the downstream outflow passage 61bb described in the first embodiment, that is, the bottom 61i having a tapered groove shape. When it flows in, it can be diffused not only on the orbiting scroll tooth bottom 8c side but also on the fixed scroll tooth bottom 7c side, and the gap between the lap tooth tip and the tooth bottom of both scrolls can be well sealed. . Further, in this embodiment, the hole 61j of the downstream outflow passage 61bb can be manufactured by a simple hole processing, so that the processing becomes easy and the time required for the processing can be shortened.

The hole 61j is upward (shape facing the fixed scroll tooth bottom 7c side), and the shape is such that oil is easily supplied to the fixed scroll tooth bottom 7c side, so the outlet of the hole 61j The side opening position may be slightly closer to the orbiting scroll tooth bottom 8c side than the center position in the height direction of the

wraps

7b and 8b. In addition, when the scroll compressor 1 is of a vertical type (the crankshaft is in the vertical direction), the outlet of the hole 61j is considered in consideration of the fact that it easily flows to the orbiting scroll tooth bottom 8c side due to gravity acting on the oil. You may comprise a side opening position so that it may become the height direction center position vicinity of the

wraps

7b and 8b.

Furthermore, the shape of the hole portion 61j is not limited to a circular hole, and may be a hole having another shape such as an elliptical shape. The hole portion 61j has a cross-sectional area on the outlet side larger than that on the inlet side. If the shape is a tapered hole, the oil can be more easily diffused.
In the embodiment shown in FIG. 7, the hole 61j is formed upward. However, the structure in which the hole 61j is formed obliquely upward from the end plate surface of the fixed scroll 7 to the suction chamber 20 or the like is as follows. There is an advantage that the hole 61j can be easily processed from the end face side. However, the hole 61j does not necessarily have to face upward, and may have a horizontal hole shape, for example. In this case, the outlet side opening position of the hole 61j may be set near the center position in the height direction of the

wraps

7b and 8b.

An embodiment of an air conditioner using the scroll compressor of the present invention will be described with reference to FIG. FIG. 8 is a refrigeration cycle configuration diagram illustrating an example of the fourth embodiment.
In FIG. 8, 1 is a scroll compressor, 43 is a four-way valve, 40 is an outdoor heat exchanger (condenser during cooling operation, evaporator during heating operation), and 41 is an electronic expansion valve. An expansion valve 42 is an indoor heat exchanger (an evaporator during cooling operation and a condenser during heating operation), and these devices are sequentially connected by refrigerant piping to form a refrigeration cycle of the air conditioner. Has been. As the scroll compressor 1, any one of the scroll compressors described in the first to third embodiments is used, and the scroll compressor 1 uses an inverter and has a wide operating range of, for example, 10 to 110 Hz. It is configured to be driven by. In particular, in order to improve the year-round energy consumption efficiency (APF) of the air conditioner, the air conditioner emphasizes operation in a low speed, low load operation region at 10 to 30 Hz.

When the scroll compressor 1 is operated at a low speed such as 10 to 30 Hz as described above, the suction chamber 20 or the compression chamber 13 is transferred from the back pressure chamber 18 via the back pressure valve 61 as shown in FIGS. Since the flow of the working fluid in the suction chamber 20 or the compression chamber 13 is relatively gentle, the oil that has flowed into the portion close to the outlet of the downstream outflow passage 61bb (the portion on the orbiting scroll tooth bottom 8c side in FIG. 3). The supply amount is particularly large, and the supply amount to a portion far from the outlet on the downstream side outflow passage 61bb (the portion on the fixed scroll tooth bottom 7c side in FIG. 3) is particularly small. For this reason, when the scroll compressor 1 is operated at a low speed such as 10 to 30 Hz, the sealing performance of the compression chamber 13 is particularly lowered, and the efficiency of the scroll compressor is particularly lowered.

However, by combining the air conditioner as shown in FIG. 8 with the scroll compressor according to the first to third embodiments of the present invention as described with reference to FIGS. 4 to 7, the low-speed and low-load operation region at 10 to 30 Hz. The air conditioner's operating efficiency, which emphasizes the operation of the air conditioner, can be greatly improved, so the energy consumption efficiency of the air conditioner can be greatly improved throughout the year, and the air consumption is low and the operating range is wide. A harmony machine can be obtained.

As described above, according to each embodiment of the scroll compressor of the present invention, at least a part of the flow path outlet 61g to the suction chamber 20 or the compression chamber 13 of the back pressure valve outflow passage 61b is connected to the fixed scroll 7. Since it is formed on the tooth bottom 7c side from the position of the wrap tooth tip, not only the gap between the fixed scroll wrap tooth tip and the orbiting scroll tooth base 8c, but also the gap between the fixed scroll tooth base 7c and the orbiting scroll wrap tooth tip The oil can be supplied sufficiently. Thereby, the airtightness of the suction chamber 20 and the compression chamber 13 by oil can be improved, and a highly efficient scroll compressor with small leakage loss can be obtained.
In addition, by adopting the scroll compressor of the present invention in an air conditioner, an effect of significantly improving the year-round energy consumption efficiency of the air conditioner can be obtained.

In the above-described embodiment, the refrigerant scroll compressor used in the refrigeration cycle apparatus for refrigeration and air conditioning has been described. However, the same applies to the scroll compressor that compresses air or other gas as a working fluid. Is applicable.

In addition, this invention is not limited to the above-mentioned Example, Various modifications are included. The above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Furthermore, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

1: scroll compressor, 2: compression mechanism, 3: through hole (oil supply hole), 5: main bearing, 6: discharge pipe, 7: fixed scroll, 7a: base plate, 7b: wrap, 7c: tooth bottom, 7d: support portion, 7e: end plate surface, 8: orbiting scroll, 8a: end plate, 8b: wrap, 8c: tooth bottom, 8d: boss portion (revolving boss portion), 8e: end plate surface, 9: case (sealed container) DESCRIPTION OF SYMBOLS 10: Crankshaft (rotary shaft), 10a: Crank part, 11: Slewing bearing, 12: Oldham ring, 13: Compression chamber, 13a: Swivel extension side compression chamber, 13b: Swivel outer side compression chamber, 14: Suction port 15: Discharge port, 16: Motor unit, 16a: Rotor, 16b: Stator, 17: Frame, 18: Back pressure chamber, 20: Suction chamber, 21: Oil pump, 22: Oil pump case, 23: Deputy Bearing, 24: side hole, 25: lubricating oil absorption 26a: oil discharge hole, 26b: oil discharge pipe, 28: oil supply pump discharge port, 31: annular groove, 32: seal member, 33: first space, 34: swivel boss member, 40: outdoor heat Exchanger, 41: Expansion valve, 42: Indoor heat exchanger, 43: Four-way valve, 52: Motor chamber, 53: Oil reservoir, 54: Discharge space, 56: Frame seal, 57: Oil groove, 60: Slit, 61: Back pressure valve, 61a: Back pressure valve inflow path (space communicating with back pressure chamber), 61b: Back pressure valve outflow path (space communicating with suction chamber or compression chamber), 61ba: Upstream outflow path, 61bb: Downstream side outflow path, 61c: space, 61d: valve, 61e: stopper, 61f: spring, 61g: flow path outlet, 61h: flow path inlet, 61i: bottom, 61j: hole, 61k: groove.

Claims

A fixed scroll in which a spiral wrap is erected on the base plate, and a orbiting scroll in which a spiral wrap is erected on the end plate and meshed with the fixed scroll to form a suction chamber or a compression chamber, A back pressure chamber that applies a pressing force to the orbiting scroll toward the fixed scroll, a back pressure valve for adjusting the back pressure of the back pressure chamber, and an inlet side of the back pressure valve and the back pressure chamber communicate with each other. A scroll compressor having a back pressure valve inflow path, a back pressure valve outflow path communicating with the outlet side of the back pressure valve and the suction chamber or the compression chamber;
Scroll compression, wherein at least a part of a flow path outlet portion of the back pressure valve outflow path to the suction chamber or the compression chamber is formed on the tooth bottom side of the position of the wrap tooth tip of the fixed scroll. Machine.
2. The scroll compressor according to claim 1, wherein a cross-sectional area on the flow path outlet side is larger than a cross-sectional area on the flow path inlet side in the back pressure valve outflow path. A scroll compressor characterized in that a part of the outlet portion is configured to be on the tooth bottom side with respect to the position of the lap tooth tip of the fixed scroll.
2. The scroll compressor according to claim 1, wherein the back pressure valve outflow path includes a hole-shaped upstream flow path and a groove-shaped downstream flow path, and a flow path outlet portion in the downstream flow path. By forming the side in a tapered shape, the cross-sectional area on the flow channel outlet side is larger than the cross-sectional area on the flow channel inlet portion side in the downstream flow channel, and thereby the flow channel outlet of the back pressure valve outflow channel A scroll compressor characterized in that a part of the portion is configured to be on the tooth bottom side with respect to the position of the lap tooth tip of the fixed scroll.
2. The scroll compressor according to claim 1, wherein the back pressure valve outflow path includes a hole-shaped upstream flow path and a groove-shaped downstream flow path, and a flow path outlet portion in the downstream flow path. By making the side into a shape that combines a curve or a curve and a straight line so that the flow channel area expands toward the flow channel outlet, the flow channel is larger than the cross-sectional area on the flow channel inlet side in the downstream flow channel. The cross-sectional area on the outlet side is formed to be large so that a part of the flow path outlet of the back pressure valve outflow passage is on the tooth bottom side with respect to the position of the wrap tooth tip of the fixed scroll. Scroll compressor characterized by.
2. The scroll compressor according to claim 1, wherein the back pressure valve outflow path includes an upstream flow path and a downstream flow path, and the flow path outlet side of the downstream flow path has a hole shape. A scroll compressor characterized in that the opening position on the side of the channel outlet portion of the shape is formed closer to the tooth bottom side than the position of the lap tooth tip of the fixed scroll.
6. An air conditioner configured by sequentially connecting a compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger with refrigerant piping, wherein the compressor is any one of claims 1 to 5. An air conditioner characterized in that the scroll compressor is operated at a low speed of at least 10 to 30 Hz.