JP2012127321A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the problem in a high pressure shell type compressor having a delivery valve mechanism wherein refrigerating machine oil is also sent out to an external refrigerant circuit side along with high pressure refrigerant gas, and the compressor becomes short of refrigerating machine oil when carrying out pressure equalization with a suction space via an oil supply mechanism provided in a main shaft since a discharge opening is closed by a delivery valve when equalizing a high pressure space and a low pressure space of a refrigerant circuit via a compressor.SOLUTION: The delivery valve mechanism of the high pressure shell type scroll compressor includes an opening larger than a cross sectional area in a direction perpendicular to an axial direction of the main shaft of a bearing clearance between a rocking part of the main shaft and a rocking bearing of a swing scroll, and smaller than an opening area of the discharge opening.

Description

  The present invention relates to prevention of refrigerating machine oil outflow from a sealed container when operation of a high-pressure shell type scroll compressor is stopped.

The scroll compressor includes a fixed scroll and a swing scroll having plate-like spiral teeth on a base plate, a frame provided with a stationary base, and an Oldham mechanism for preventing the rotation of the swing scroll in a sealed container or shell. The compression mechanism is configured, and the fixed scroll and the swing scroll are combined so as to mesh with each other's plate-like spiral teeth, thereby forming a plurality of compression chambers for compressing the refrigerant gas. The swing scroll is held by the fixed scroll and the frame, and swings by a swing shaft supported by the frame via a bearing provided on the back surface of the frame. The frame that supports the swing shaft is fixed to the sealed container.
In addition, in order to suppress wear of the compression mechanism by sliding of the compression mechanism due to swinging motion, refrigerating machine oil to be supplied to the compression mechanism is stored in the bottom of the sealed container, and the swing scroll is swung by connecting an electric motor. An oil supply mechanism for supplying refrigerating machine oil stored in a main shaft provided integrally with the swing shaft for movement is provided, and the oil supply mechanism always supplies oil to the compression mechanism during compressor operation.

  For example, in a low-pressure shell type scroll compressor disclosed in Patent Document 1, an upper discharge space in which a discharge pipe is provided by a fixed scroll and a frame and a lower intake in which a suction pipe and an electric motor are arranged are provided in a sealed container. It is partitioned into a space. The refrigerant gas sucked from the suction pipe is compressed in the compression chamber and discharged to the discharge space on the upper surface of the fixed scroll through the discharge valve, and the discharged refrigerant gas is again sucked into the compression chamber. The discharge valve prevents it.

  However, when the compressor stops, the refrigerant gas leaks and flows in from a slight gap between the compression mechanisms and a few gaps between the compression chambers divided into a plurality from the discharge space toward the compression chamber. The pressure in the discharge space and the pressure in the compression chamber are gradually equalized. When the pressure difference between the pressure in the discharge space and the pressure in the compression chamber becomes small, the discharge valve is not completely closed, and the refrigerant gas flows into the compression chamber from the gap between the discharge valves, causing problems such as abnormal noise. As a countermeasure, a passage that bypasses the discharge valve and communicates the discharge space and the compression chamber is provided near the discharge valve, and the refrigerant gas in the discharge space is introduced from the communication passage to equalize the discharge space and the compression chamber of the compressor. To avoid problems. However, if a large amount of refrigerant gas flows in from this communication path, the compression mechanism is reversed and damaged. Therefore, the communication path is a capillary path formed of a capillary tube having a very small diameter and a long length with a large flow resistance. The pressure is then gradually equalized, and the reverse of the compression mechanism is prevented while avoiding problems such as abnormal noise.

JP 2009-162077 A (page 3-5, FIG. 1-2)

  In the case of a high-pressure shell type scroll compressor that has a discharge valve mechanism at the discharge port and the entire inside of the sealed container of the compressor is a discharge space and becomes a high-pressure space by high-pressure refrigerant gas compressed by the compression mechanism, the low-pressure shell type compressor Unlike the high-pressure space in the closed container, the high-pressure space in the refrigerant circuit and the low-pressure space, which is the suction space connected to the compressor suction port, try to equalize the pressure through the compressor. Since it is closed by the discharge valve, it tries to equalize pressure with the low-pressure space via the oil supply path provided in the main shaft. Therefore, the refrigerating machine oil present at the bottom of the sealed container together with the high-pressure refrigerant gas is also discharged to the outside refrigerant circuit side, and the compressor has a problem that the refrigerating machine oil is insufficient.

  In a scroll compressor having a compliant mechanism for improving reliability or efficiency, an orbiting scroll or the like moves in the axial direction when the compressor is stopped, and an axial gap is formed between the fixed scroll and the orbiting scroll. As a result, the compression chamber divided into a plurality of compression mechanisms is connected at once, and also communicated with the low-pressure space of the refrigerant circuit connected to the compressor through the suction pipe, so that the high-pressure refrigerant gas is low-pressure at a time. Since it is going to flow into the space side, the refrigerating machine oil which is going to be discharged together also has a problem of being discharged in large quantities at a time.

  In addition, in the capillary passage that is a communication passage that bypasses the discharge valve, which is a conventional pressure equalization method for a scroll compressor, in order to prevent the compression mechanism from reversing, the flow resistance is large, and it takes too much time for the refrigerant gas to flow. In a scroll compressor having a compliant mechanism, there is a problem that high-pressure refrigerant gas and refrigerating machine oil cannot be prevented from being discharged together into the low-pressure space through the oil supply path of the main shaft.

  Further, in the conventional communication path, in order to increase the flow resistance, it is necessary to make a very small diameter hole (for example, an inner diameter of 0.5 mm and a length of 115 mm) with a long communication path, which is difficult to process. As a countermeasure, a hole with an appropriate size was made and a capillary tube and bushing were put in it. In addition to processing the communication path, the diameter and length of the additional parts and capillary tube were adjusted. Such work was necessary.

  In addition, the communication passage that bypasses the discharge valve has a problem in that the refrigerant gas is re-inhaled and re-compressed from the communication passage during normal compression operation, causing a decrease in performance. In addition, when a long communication path is provided, there is a problem in that it interferes with parts such as a discharge valve on the fixed scroll and other bypass paths.

  The present invention has been made to solve the above-described problems, and is connected to a compressor through a hermetic container of a high-pressure shell type compressor without changing the components on the fixed scroll and the bypass path. When the high-pressure space and low-pressure space of the refrigerant circuit are equalized, high-pressure refrigerant gas flows into the low-pressure space from the discharge valve or discharge port, and the high-pressure refrigerant gas flows into the low-pressure space along with the refrigerating machine oil from the main oil supply path. The purpose is to obtain a scroll compressor that is suppressed.

  According to the present invention, the discharge valve or the discharge port of the high-pressure shell type scroll compressor discharges larger than the cross-sectional area in the direction perpendicular to the axial direction of the main shaft of the bearing clearance between the main shaft's rocking shaft and the rocking scroll's rocking bearing. An opening smaller than the opening area of the outlet is provided.

  According to the present invention, the discharge valve or the discharge port of the high-pressure shell type scroll compressor discharges larger than the cross-sectional area in the direction perpendicular to the axial direction of the main shaft of the bearing clearance between the main shaft's rocking shaft and the rocking scroll's rocking bearing. Since it has an opening smaller than the opening area of the outlet, the high-pressure space of the refrigerant circuit connected to the compressor via the hermetic container of the high-pressure shell type compressor without changing the parts on the fixed scroll or the bypass path High-pressure refrigerant gas flows into the low-pressure space from the discharge valve or outlet, and the high-pressure refrigerant gas is prevented from flowing into the low-pressure space along with the refrigerating machine oil from the oil supply path of the main shaft. A highly efficient scroll compressor can be obtained.

It is sectional drawing of the scroll compressor which concerns on Embodiment 1 of this invention. It is a refrigerant circuit whole figure concerning Embodiment 1 of this invention. It is sectional drawing of the discharge valve mechanism which concerns on Embodiment 1 of this invention. It is explanatory drawing of the discharge path | route of the refrigerating machine oil which concerns on Embodiment 1 of this invention. It is explanatory drawing of the discharge valve which concerns on Embodiment 1 of this invention. It is a figure showing the characteristic of the compressor which concerns on Embodiment 1 of this invention. It is sectional drawing of the discharge valve mechanism which concerns on Embodiment 2 of this invention. It is sectional drawing of the discharge valve mechanism which concerns on Embodiment 3 of this invention.

Embodiment 1 FIG.
FIG. 1 is a longitudinal sectional view of a scroll compressor 100 according to Embodiment 1 of the present invention. The outer peripheral portion of the fixed scroll 1 is fastened to the guide frame 4 by bolts (not shown), and a plate-like spiral tooth 1b is formed on one surface (lower surface in FIG. 1) of the base plate portion 1a of the fixed scroll 1. In addition, a pair of Oldham guide grooves 1c are formed in a substantially straight line on the outer periphery, and a pair of fixed-side keys 9a of the Oldham mechanism 9 are reciprocally slid in the Oldham guide groove 1c. It is freely engaged.

  The orbiting scroll 2 is formed with spiral teeth 2b having the same shape as the plate-like spiral teeth 1b of the fixed scroll 1 on one surface (the upper surface in FIG. 1) of the base plate portion 2a. The plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the swing scroll 2 are combined so as to mesh with each other, and the refrigerant gas separated by the combined plate-like spiral teeth 1b and plate-like spiral teeth 2b A plurality of compression chambers for compression are formed. Further, in the base plate portion 2a, a hollow cylindrical boss portion 2d is formed at the center of the surface (the lower surface in FIG. 1) opposite to the surface on which the plate-like spiral teeth 2b are formed. A rocking bearing 2e is formed on the inner surface of the portion 2d. A thrust surface 2f is formed on the outer peripheral portion of the surface on the same side as the boss portion 2d. The thrust surface 2f is slidable against the thrust bearing 3a of the compliant frame 3. A pair of Oldham guide grooves 2c having a phase difference of about 90 degrees with the Oldham guide groove 1c of the fixed scroll 1 are formed on the outer peripheral portion of the base plate portion 2a of the orbiting scroll 2 in a substantially straight line. The Oldham guide groove 2c is engaged with a pair of two swinging side keys 9b of the Oldham mechanism 9 so as to be reciprocally slidable. Further, in FIG. 1, the base plate portion 2a is formed with a thin bleed hole 2g in which the surface on the swing scroll 2 side (upper surface in FIG. 1) and the surface on the compliant frame 3 side (lower surface in FIG. 1) communicate. Has been. The opening of the bleed hole 2g on the side of the compliant frame, that is, the lower opening 2h is arranged so that the circular locus always fits inside the thrust bearing 3a of the compliant frame 3 during normal operation. .

  On the outer side of the thrust bearing 3a of the compliant frame 3, a surface 3b on which the Oldham mechanism annular portion 9c reciprocates is formed. At the center of the compliant frame 3, a main bearing 3c and an auxiliary main bearing 3d that support the main shaft 6 that is rotationally driven by the electric motor 5 in the radial direction are formed. The compliant frame 3 is formed with a communication hole 3e that communicates from the thrust bearing 3a to the frame lower space 4b at a position facing the lower opening 2h of the swing scroll. Further, on the surface 3b of the Oldham mechanism annular portion 9c of the compliant frame 3 that reciprocally slides, a communication hole 3f that communicates the base plate outer peripheral space 2k and the frame upper space 4a communicates with the inner side of the Oldham mechanism annular portion 9c. It is formed as follows. The compliant frame 3 is a compliant frame space surrounded by the outer peripheral surface of the boss portion 2 d of the orbiting scroll 2, the base plate portion 2 a surface, the outer surface of the main shaft 6, and the inner surface of the compliant frame 3. An intermediate pressure adjusting valve space 3n for accommodating an intermediate pressure adjusting valve 3g for adjusting the pressure of the boss outer diameter space 2n, an intermediate pressure adjusting valve spring 3h, and an intermediate pressure adjusting spring 3k is provided. The intermediate pressure adjusting spring 3k is retracted from the natural length and stored.

  As shown in FIG. 1, an upper fitting cylindrical surface 4 c is formed on the inner side surface of the guide frame 4 on the fixed scroll 1 side (upper side in FIG. 1), and the upper surface formed on the outer peripheral surface of the compliant frame 3. It is engaged with the fitting surface 3p. On the other hand, a lower fitting cylindrical surface 4 d is formed on the inner side of the guide frame 4 on the electric motor side (lower side in FIG. 1), and the lower fitting cylindrical surface 3 s formed on the outer peripheral surface of the compliant frame 3. Is engaged.

  A frame lower space 4b formed by the inner surface of the guide frame 4 and the outer surface of the compliant frame 3 is partitioned by ring-shaped sealing materials 7a and 7b at the top and bottom. Here, two ring-shaped seal grooves for accommodating the ring-shaped sealing materials 7 a and 7 b are formed on the inner peripheral surface of the guide frame 4, but these seal grooves are formed on the outer peripheral surface of the compliant frame 3. It may be. The space on the outer peripheral side of the thrust bearing 3a surrounded by the base plate part 2a of the orbiting scroll 2 and the compliant frame 3, that is, the base plate outer peripheral part space 2k, is a low pressure space of the intake gas atmosphere (intake pressure). It has become.

  At the end of the main shaft 6 on the side of the orbiting scroll 2 (upper side in FIG. 1), an orbiting shaft portion 6a that is rotatably engaged with the orbiting bearing 2e of the orbiting scroll 2 is formed. Is formed with a main shaft portion 6b rotatably engaged with the main bearing 3c and the auxiliary main bearing 3d of the compliant frame 3. The other end portion of the main shaft is formed with a sub shaft portion 6c that is rotatably engaged with the sub bearing 8a of the sub frame 8, and the motor rotor 5a is interposed between the sub shaft portion 6c and the main shaft portion 6b. Is shrink-fitted. In addition, there is a sump in which the refrigerating machine oil 11 is stored at the bottom of the sealed container 10, and the refrigerating machine oil 11 is sucked up from the lower end surface of the main shaft 6, that is, the oil supply port 6 d by an oil supply mechanism provided on the main shaft 6.

As shown in FIG. 2, the scroll compressor 100 includes a refrigerant circuit connected to an external condenser, evaporator, expansion valve, and the like via a pipe, and is used for an air conditioner and a refrigerator. For example, the refrigerant gas compressed by the scroll compressor 100 as shown in FIG. 2A is discharged from the discharge pipe 12 and flows into the condenser 101 connected through the pipe. In the condenser 101, the discharged high-pressure and high-temperature refrigerant gas exchanges heat with external air blown by the fan 104, etc., and releases heat to the external air, resulting in a temperature drop. The high-pressure refrigerant gas whose temperature has fallen flows into the expansion valve 102 connected via the pipe and is decompressed. The decompressed low-pressure refrigerant gas flows into the evaporator 103 connected via the pipe, exchanges heat with the external air blown by the fan 105 again, takes heat from the external air, and rises in temperature. The low-pressure refrigerant gas whose temperature has risen is returned to the scroll compressor 100 from the suction pipe 13 connected through the pipe and compressed again. By repeating such a cycle, the refrigerant gas circulates in the refrigerant circuit, and the air conditioner air-conditions the room with the heat-exchanged air, or the refrigerator cools the food with the heat-exchanged air or directly exchanges heat with the food. Or do.
Therefore, the sealed container 10 and the discharge pipe 12 from which the high-pressure refrigerant gas is directly discharged from the compression chamber becomes a high-pressure space by the high-pressure refrigerant gas from the inlet of the expansion valve 102, and the low-pressure refrigerant gas from the outlet of the expansion valve 102 to the suction pipe 13 This creates a low pressure space. That is, the discharge space from which the high-pressure refrigerant gas is discharged from the compression chamber is a high-pressure space, and the entire inside of the sealed container 10 is the discharge space. Further, the suction space sucked into the compression chamber is a low pressure space.
In the case of an air conditioner or a refrigerator, the condenser 101 and the evaporator 103 exchange heat with air. However, as shown in FIG. Some air conditioning and hot water supply are provided through piping.

Next, the discharge valve mechanism will be described. FIG. 3 is a view for explaining the discharge valve mechanism. The discharge valve mechanism is composed of the discharge valve 20 and the discharge valve spring 21, and the compression chamber and the sealed container 10 provided in the back and center of the fixed scroll 1. Are attached to the discharge port 1d. The discharge valve 20 is provided so as to block the discharge port 1d, and the discharge valve presser 21 provided above the discharge valve 20 is for regulating the movement amount of the discharge valve 20. The discharge valve 20 and the discharge valve presser 21 Is fixed to the back of the fixed scroll 1 with bolts. The discharge port 1d does not always communicate with the compression chamber, but communicates at the final stage of the compression process. The discharge valve 20 prevents the high-pressure refrigerant gas once discharged into the discharge space in the hermetic container, that is, the high-pressure space, from being re-inhaled from the discharge space into the compression chamber through the discharge port 1d and recompressed during the operation of the compressor. Yes.
A compression chamber that sucks refrigerant from a suction space that is a low-pressure space through a suction port 1e that is provided on the outer peripheral side of the fixed scroll 1 and is connected to a suction pipe 13 causes the vicinity of the suction port 1e by the swinging motion of the swing scroll 2. The refrigerant gas in the compression chamber is compressed by moving from the outer periphery to the inner periphery. When the compression chamber is connected to the discharge space and the discharge port 1d in the final stage, the refrigerant gas can be smoothly discharged from the compression chamber to the discharge space via the discharge port 1d if the pressure in the compression chamber is higher than the pressure of the discharge space. However, when there is no discharge valve, when the compression chamber is connected to the discharge port 1d, if the pressure in the compression chamber is lower than the pressure in the discharge space, the refrigerant gas flows backward from the discharge space into the compression chamber, that is, re-sucks and is compressed again. It will be recompressed in the room. Even if the gas once compressed and re-compressed is not circulated in the refrigerant circuit, it does not affect the air conditioning capacity of the air conditioner or the cooling capacity of the refrigerator. Loss. The discharge valve prevents this loss.
For example, in an air conditioner equipped with this compressor operating normally with a 410A refrigerant (discharge pressure of about 2.0 MPa), if there is no discharge valve mechanism, the refrigerant gas flows back from the discharge space to the compression chamber. As a result, the compression performance is reduced by about 4%. The performance drop value varies depending on the type of refrigerant, the operating state of the compressor, the volume of the compression chamber, and the compression rate, but the discharge valve plays a role of suppressing the performance drop under any conditions.

  Next, the oil supply path of the oil supply mechanism of the scroll compressor 100 and the operation of the compliant mechanism will be described. In FIG. 1, during the steady operation, the sealed container space 10 a becomes a high pressure of the discharge gas atmosphere, and the refrigerating machine oil 11 at the bottom of the sealed container 10 flows in from the oil supply port 6 d and is provided through the main shaft 6 in the axial direction. 6e flows upward. The refrigerating machine oil 11, which is high-pressure oil introduced into the boss shaft space 2 p between the oscillating shaft 6 a upper surface and the boss 2 d, is the narrowest oscillating shaft 6 a in the oil supply path. The pressure is reduced in the oscillating shaft side boss part space 2r, which is a bearing gap between the oscillating bearing 2e, becomes an intermediate pressure higher than the suction pressure and lower than the discharge pressure, and flows into the boss part outer space 2n. Separately, the high-pressure oil in the high-pressure oil supply hole 6e is led from the lateral hole provided in the main shaft 6 to the high-pressure side end surface (the lower end surface in FIG. 1) of the main bearing 3c. The pressure is reduced in the space 3u between the bearing 3c and the main shaft portion 6b to become an intermediate pressure, which also flows into the boss portion outer space 2n. The refrigerating machine oil 11 (injection of refrigerant dissolved in refrigerating machine oil, which is generally a two-phase flow of gas refrigerant and refrigerating machine oil) having an intermediate pressure in the boss outer space 2n is stored in the intermediate pressure regulating valve. Overcoming the force applied by the intermediate pressure adjustment spring 3k when passing through the space 3n, the intermediate pressure adjustment valve 3g is pushed up to flow into the frame upper space 4a, and then discharged to the inside of the Oldham mechanism annular portion 9c through the communication hole 3f. Is done.

Further, even after the oil is supplied to the thrust surface 2 f of the orbiting scroll 2 and the sliding portion of the thrust bearing 3 a of the compliant frame 3, it flows inside the Oldham mechanism annular portion 9 c. Then, after the refrigerating machine oil 11 flowing out of these oils is supplied to the sliding surface and the key sliding surface of the Oldham mechanism annular portion 9 c, the refrigeration oil 11 enters the base plate outer peripheral space 2 k in the outer peripheral portion of the compliant frame 3 and the swing scroll 2. Opened. As described above, the intermediate pressure Pm1 in the boss portion outer space 2n is
With a predetermined pressure α that is substantially determined by the spring force of the intermediate pressure adjusting spring 3k and the intermediate pressure exposure area of the intermediate pressure adjusting valve 3g,
Pm1 = Ps + α (Ps is the suction atmosphere pressure, that is, low pressure)
It is controlled by.

In FIG. 1, a lower opening 2h of the bleed hole 2g provided in the base plate portion 2a of the orbiting scroll 2 is a thrust bearing opening, that is, an upper opening 3t of the communication hole 3e provided in the compliant frame 3. The upper opening in FIG. 1 communicates constantly or intermittently. For this reason, the refrigerant gas having an intermediate pressure higher than the suction pressure during compression from the compression chamber formed by the fixed scroll 1 and the orbiting scroll 2 and equal to or lower than the discharge pressure becomes the bleed hole 2g of the orbiting scroll 2 and compliant. It is guided to the frame lower space 4b through the communication hole 3e of the frame 3. However, although it is guided, the frame lower space 4b is a closed space sealed by the upper ring-shaped sealing material 7a and the lower ring-shaped sealing material 7b. The frame lower space 4b has a slight flow in both directions, that is, it is in a breathing state. As described above, the intermediate pressure Pm2 in the frame lower space 4b is determined by the predetermined magnification β substantially determined by the position of the compression chamber that communicates.
Pm2 = Ps × β (Ps is the suction atmosphere pressure, that is, low pressure)
It is controlled by.

  Now, although the sum of the force resulting from the intermediate pressure Pm1 of the boss outer space 2n and the pressing force from the orbiting scroll 2 via the thrust bearing 3a acts on the compliant frame 3 as a downward force, The sum of the force caused by the intermediate pressure Pm2 in the lower space 4b and the force caused by the high pressure acting on the portion exposed to the high-pressure atmosphere at the lower end surface acts as an upward force, and this upward force is It is set to be larger than the downward force described above.

  For this reason, the compliant frame 3 is guided by the upper fitting surface 3p of the guide frame 4 to the upper fitting cylindrical surface 4c and the lower fitting cylindrical surface 3s of the guide frame 4 by the lower fitting cylindrical surface 4d. The client frame 3 is movable in the axial direction with respect to the guide frame 4 and floats on the fixed scroll side (upward in FIG. 1). The orbiting scroll 2 pressed against the compliant frame 3 via the thrust bearing 3a is also lifted upward. As a result, the tooth tip and the tooth bottom of the orbiting scroll 2 are respectively connected to the tooth bottom and tooth of the fixed scroll 1 respectively. Touch first and slide. However, since the refrigerant gas does not flow into the frame lower space 4b and the intermediate pressure Pm2 cannot be secured during an excessive period such as when the compressor is started up, the swing scroll 2 and the compliant frame 3 do not rise and fall to the guide frame 4 side. When the internal pressure of the compression chamber rises abnormally, a phenomenon may occur in which the orbiting scroll 2 and the compliant frame 3 are pressed toward the guide frame 4 due to the pressure in the compression chamber.

  On the other hand, when the scroll compressor 100 stops, the refrigerant gas does not flow from the compression chamber to the frame lower space 4b and the intermediate pressure Pm2 cannot be maintained together with the stop of the compression mechanism such as the fixed scroll 1 and the swing scroll 2. The compliant frame 3 is lowered in the axial direction. That is, it will be in the state lowered to the guide frame 4 side. At the same time, since the refrigerant gas does not flow into the boss outer space 2n and the intermediate pressure Pm2 cannot be maintained, the swing scroll 2 that has been pushed up together with the compliant frame 3 is also lowered so as to be engaged with each other. The spiral spiral teeth 1b and the plate spiral spiral teeth 2b are separated from each other, and a gap is generated at the tooth tip. That is, a plurality of compression chambers formed by being separated by the plate-like spiral teeth 1b and the plate-like spiral teeth 2b become one, and the compression chamber communicates with the suction pipe 13 through the suction port 1e. The low pressure space communicated with the low pressure space of the refrigerant circuit. Note that the space filled with the intermediate pressure, such as the frame lower space 4b, also communicates with the compression chamber, and thus becomes a low pressure space.

On the other hand, the inside of the sealed container 10 communicates with the high-pressure space of the refrigerant circuit via the discharge pipe 12 to form one high-pressure space.
In this state, when the high pressure space and the low pressure space try to equalize pressure, the space separating the compression chamber and the high pressure space, that is, the clearance of the compression mechanism, the clearance of the discharge valve mechanism, or the sealing provided on the main shaft 6 is used. The high-pressure refrigerant gas tends to flow from the container 10 through the oil supply path that is connected to the compression mechanism. However, the gap of the compression mechanism and the gap of the discharge valve mechanism, particularly the discharge valve mechanism, prevents the high pressure refrigerant gas in the sealed container 10 from flowing back to the compression chamber side through the discharge port 1d at the discharge valve 20. The high-pressure refrigerant gas cannot flow in, and the high-pressure refrigerant gas is encouraged to flow in another path. That is, the high-pressure refrigerant gas flows through the oil supply mechanism of the main shaft 6 to equalize the pressure.

That is, as shown by the arrow in FIG. 4, the high-pressure refrigerant gas passes through the high-pressure oil supply hole 6e (a in FIG. 4) and the boss portion space 2p, 2r (a in FIG. 4) on the upper and side surfaces of the swing shaft. 2n is reached. The high-pressure refrigerant gas that has reached the boss outer space 2n passes through the intermediate pressure regulating valve storage space 3n, the frame upper space 4a, the communication hole 3f (c in FIG. 4), or is in compression with the thrust surface 2f of the orbiting scroll 2. It reaches the Oldham mechanism annular portion 9c via the gap (D in FIG. 4) of the sliding portion of the thrust bearing 3a of the client frame 3, and flows into the suction port 1e from the Oldham mechanism annular portion 9c (O in FIG. 4). . However, since the high-pressure refrigerant gas passes through the refrigerating machine oil 11 stored at the bottom of the hermetic container 10, the refrigerating machine oil 11 as well as the refrigerant gas rises through the high-pressure oil supply hole 6e of the main shaft 6 and is discharged to the suction port 1e. Then, it flows out to an external refrigerant circuit via 13. As a result, the refrigerating machine oil 11 is insufficient in the sealed container 10, and sliding parts such as bearings are damaged by friction.
Furthermore, since the high-pressure space and the low-pressure space to be equalized are large, the momentum of the refrigerant gas to be equalized is strong, and a large amount of the refrigerating machine oil 11 is lost from the sealed container 10.

In particular, the refrigeration oil 11 may be mixed with the refrigerant gas and flow out even during normal operation, but there is no problem because it circulates in the refrigerant circuit together with the refrigerant gas and returns to the compressor 100. However, since the refrigerant gas does not circulate when the compressor is stopped, the refrigeration oil 11 that has flowed out of the hermetic container 10 does not return to the compressor 100, and is likely to be damaged at the next start-up. Become.
Therefore, in order to suppress this phenomenon, a method of quickly equalizing pressure in another path is required before equalizing pressure in the oil supply path on the main shaft 6 side.

  In the conventional scroll compressor not provided with the discharge valve, there is no phenomenon that the refrigerating machine oil 11 flows out when the pressure is equalized. This is because the high pressure refrigerant gas flows from the discharge port 1d side, so that the pressure equalization was completed before the refrigerating machine oil 11 moved up the high pressure oil supply hole 6e of the main shaft 6 and reached the suction port 1e.

For the above countermeasures, in FIG. 5A, the pressure is not equalized in the oil supply path of the main shaft 6, and the discharge is performed without adding new parts or crafting to the compression mechanism, which is the path closest to the suction port. The thing provided with the opening part into which a high pressure refrigerant gas flows in into a compression chamber from a valve mechanism is demonstrated.
The compressor is stopped, the plate-like spiral teeth 1b of the fixed scroll 1 and the plate-like spiral teeth 2b of the orbiting scroll 2 are separated from each other, and a plurality of compression chambers communicate with each other, through the high-pressure oil supply hole 6e of the main shaft 6. Before the refrigerating machine oil 11 rises and reaches the suction port 1e, a small-diameter communication hole 22 is provided in the discharge valve 20 so that high-pressure refrigerant gas flows into the compression chamber from the communication hole 22 (in FIG. 4). The high-pressure refrigerant gas that has flowed into the compression chamber passes through the gap between the tip of the plate-like spiral tooth 1b of the fixed scroll 1 or the gap of the tip of the plate-like spiral tooth 2b of the orbiting scroll 2 (in FIG. 4) and sucks it. The mouth 1e is reached (in FIG. 4). When high-pressure refrigerant gas is introduced from the discharge valve mechanism side, there is a risk of reverse rotation because the high-pressure refrigerant gas pushes the orbiting scroll 2, but when the compressor 100 stops, the intermediate pressure in the outer space 2n of the boss part Since the intermediate pressure in the frame lower space 4b cannot be maintained, the orbiting scroll 2 and the compliant frame 3 are lowered to the guide frame 4 side, and the plurality of compression chambers become one, so there is no possibility of reverse rotation. However, the time required for the refrigerating machine oil 11 to rise from the high pressure oil supply hole 6e of the main shaft 6 to reach the suction port 1e is short, and a communication hole 22 having a somewhat large diameter is required. On the other hand, when the communication hole 22 is provided in the discharge valve 20, the high-pressure refrigerant gas discharged from the compression chamber during normal operation returns to the compression chamber from the communication hole 22 again and generates a loss that causes recompression. It is necessary to select the diameter of the communication hole 22.

FIG. 6 shows that while using 410A as the refrigerant, the stroke volume is about 30 to 70 cc, the high pressure is about 0.5 to 4.2 MPa, and the low pressure is about 0.2 to 1.6 MPa. A compressor is described as an example.
Graph A in FIG. 6 shows the amount of the refrigerating machine oil 11 that reaches the inlet 1e through the high-pressure oil supply hole 6e of the main shaft 6 when the compressor is stopped with respect to the area of the opening provided in the discharge valve mechanism. When the discharge valve 20 is not provided with the communication hole 22, that is, when the opening area is 0, the amount of the refrigerating machine oil 11 flowing out from the suction port 1 e is 100%, and relative to the diameter of the communication hole 22 of the discharge valve 20, that is, the opening area Amount.
Further, a graph B in FIG. 6 shows the compressor performance with respect to the area of the opening provided in the discharge valve mechanism under a heavy load condition in which the differential pressure between the high pressure and the low pressure is about 3.5 MPa under the operating conditions of the compressor. This shows a relative decrease, and the performance when the communication hole 22 is not provided in the discharge valve 20, that is, when the opening area is 0, is defined as 100%, and relative to the diameter of the communication hole 22 of the discharge valve 20, that is, the opening area. The amount of performance degradation is shown.

Here, 100% of the refrigerating machine oil 11 is discharged, which means that the oil level of the refrigerating machine oil 11 stored in the bottom of the hermetic container 10 is lowered from the oil supply port 6d of the main shaft 6 and cannot be sucked up. The remaining amount of the refrigerating machine oil 11 is still in 10. Since the refrigerating machine oil 11 is discharged when the compressor is stopped, the refueling mechanism cannot suck up the refrigerating machine oil 11 at the next start-up of the compressor, and cannot supply oil to the sliding portion. Therefore, the sliding part is damaged.
On the other hand, even if it is discharged up to about 80% of the discharge amount, there remains a remaining amount that allows the fueling mechanism to suck up the fueling port 6d at the next activation. In addition, since the refrigerating machine oil 11 from the previous operation remains in the compression mechanism, the refrigerating machine oil 11 that has flowed out circulates through the refrigerant circuit and returns because the refrigerating machine oil 11 is not sucked up from the bottom of the sealed container upon activation. It is also the amount of oil that can be refueled until it comes.

  Further, although the amount of the refrigerating machine oil 11 that is circulated differs depending on the amount of the refrigerant that circulates in the refrigerant circuit, during normal operation, the refrigerating machine oil 11 is mixed with the refrigerant gas by about 30% to 40% and circulates through the external refrigerant circuit. Yes. However, since the circulating refrigerating machine oil 11 does not contribute to the heat exchange performance of the refrigerant circuit and is lost, the refrigerating machine oil 11 and the refrigerant gas are separated as much as possible by, for example, a separation mechanism provided in a sealed container of the compressor. It isolate | separates and is returned in the airtight container 10 of a compressor. Therefore, even when the compressor is stopped, if the mixing / circulation amount of the refrigerating machine oil 11 temporarily increases, the heat exchange performance of the refrigerant circuit deteriorates at the start of the next operation and the processing capacity of the separation mechanism is in time. Because there is no, it circulates through the refrigerant circuit for a long time and continues to deteriorate the performance. Therefore, since measures for separation are required, it is better that the outflow amount is as small as possible.

In addition, according to FIG. 6, the communication hole 22 if a diameter phi ₃ of about i.e. about the opening area A ₃ (= same area as the opening area σ of the discharge port), it is same as when not installed discharge valve 20, The refrigeration oil 11 is excessively discharged from the sealed container 10 and the refrigeration oil becomes insufficient, so that the oil supply mechanism cannot be refueled at the next start-up. However, this does not provide the effect of the discharge valve 20, that is, the effect of preventing the loss of the compression process of re-inhaling and re-compressing the high-pressure refrigerant gas once discharged.
Therefore, it is necessary to provide the communication hole 22 that can cope with these points.

  First, the relationship between the refrigerating machine oil and refrigerant gas flowing in from the oil supply port side and the refrigerant gas flowing in from the discharge port side will be described. When the high-pressure space and the low-pressure space are equalized, the high-pressure refrigerant gas rises from the oil supply port 6d at the lower part of the main shaft 6 through the high-pressure oil supply hole 6e and exits to the intake port 1e in a low-pressure atmosphere. On the other hand, the same applies to the case where an opening is provided on the discharge port 1d side, and the high-pressure refrigerant gas passes from the opening to the discharge port 1d side through the compression chamber to the suction port 1e in a low-pressure atmosphere. Therefore, if the refrigerant gas flowing in from the refueling port side and the discharge port side is refrigerant gas, if the area of the opening on the discharge port 1d side, that is, the communication hole 22 of the discharge valve 20 is larger than the refueling port 6d, the high-pressure refrigerant gas is The amount flowing from the discharge port 1d side through the oil supply port 6d is superior, and the pressure is equalized by the high-pressure refrigerant gas flowing from the discharge port 1d side.

However, although the high-pressure refrigerant gas flowing in from the refueling port 6d is actually mixed with the refrigerating machine oil 11, the high-pressure refrigerant gas reaches the suction port 1e while pushing up the refrigerating machine oil 11, so that the refrigerating machine oil 11 and the refrigerant gas Then, the mass ratio / specific gravity is different by 300 times, the refrigerating machine oil 11 is viscous, the high pressure oil supply hole 6e rises against gravity while causing pressure loss, and the rocking shaft portion 6a in the oil supply path And the rocking shaft side boss part space 2r, which is the bearing gap between the rocking bearing 2e, restricts the flow rate of the oil supply, so that it is perpendicular to the axial direction of the rocking shaft part 6a of the rocking shaft side boss part space 2r. By adjusting the cross-sectional area in any direction, that is, the passage area of the refrigerating machine oil or refrigerant gas, the flow rate or flow rate of the refrigerating machine oil or refrigerant gas can be adjusted. That is, the refrigerant that flows in from the communication hole 22 side due to the relative relationship between the cross-sectional area of the swing shaft side surface boss space 2r perpendicular to the axial direction of the swing shaft portion 6a and the opening area of the communication hole 22 of the discharge valve 20. The amount of gas can be made larger than the amount of refrigerant gas flowing in from the fuel filler opening 6d side. Specifically, ρ is the cross-sectional area perpendicular to the axial direction of the swing shaft portion 6a of the swing shaft side boss space 2r that is the bearing clearance, and the opening area of the communication hole 22 is A. When the opening area of the communicating hole 22 of the a _0, by providing the a ₀ = 0.1 × [rho i.e. a ₀ or more communicating holes, come to inflowing high-pressure gas discharge ports 1d preferentially. As can be seen from FIG. 6, if the opening area of the communication hole 22 is A ₀ or more, that is, 10% of the cross-sectional area ρ of the rocking shaft side boss space 2r, the refrigerating machine oil 11 discharged from the suction port 1e is communicated. Since it is suppressed to about 80% of the case where there is no hole 22, there is no case where the refrigerating machine oil 11 is insufficient at the next start-up and cannot be sucked up from the oil supply mechanism. That is, the pressure equalization between the high pressure space and the low pressure space can be terminated by the communication hole 22 before the refrigerating machine oil 11 is discharged from the suction port 1e until the refrigerating machine oil becomes insufficient.

The refrigerating machine oil 11 and the refrigerant gas pass through the main shaft main bearing space 3u in addition to the rocking shaft side boss part space 2r, but the refrigerating machine oil 11 and the refrigerant gas passing through the rocking shaft side boss part space 2r from the direction of gravity. In many cases, there is no influence even if the main shaft main bearing space 3u is ignored.
In addition, 0.1 is the eigenvalue / coefficient of the correlation between the two fluids obtained by calculating and simulating the difference in specific gravity and viscosity of the two fluids, refrigerant gas and refrigerating machine oil, and the flow velocity and flow rate due to the different paths. It is. That is, the difference in time and amount reaching the suction port due to the difference between the refrigerant gas, the refrigerating machine oil, and the discharge port side and the oil supply port side represents a difference of about 10%.
Note that the diameter of the communication hole 22 that realizes the cross-sectional area of A ₀ is φ ₀ .

On the other hand, when a larger communication hole 22 is provided in the discharge valve 20 to reduce the discharge amount, the compressor is greatly reduced in efficiency due to re-suction and re-compression. According to the graph B of FIG. 6, the efficiency of the compressor is reduced by about 1% when the communication hole 22 is 4% of the opening area σ of the discharge port, that is, about A ₂ . However, the graph B shows that the compressor efficiency is reduced by about 1% under a heavy load where the differential pressure between the high pressure and the low pressure is about 3.5 MPa under the operating conditions of the compressor, and this compressor is actually included. For example, in an air conditioner using a refrigerant circuit, the frequency and usage time of such a high differential pressure condition are extremely low, and 0.05% even when converted to annual energy consumption efficiency (AFP). It is only a decrease in the degree, and the influence on the entire air conditioner is extremely small. Further, according to the graph A, the refrigerant discharge amount at that time is about 40%, which is almost the same as the opening area A ₃ when the discharge valve 20 is not attached, and the amount of refrigerating machine oil circulated during normal operation is 30-40%. There is no difference. Therefore, even if the opening area is further increased, the amount of circulating refrigeration oil does not change from the normal state, so there is no need to provide an opening area larger than this.

Therefore, if the communication hole 22 is 4% of the opening area σ of the discharge port, that is, A ₂ or less, the compressor is re-sucked / recompressed, so that the heat exchange performance of the refrigerant circuit is not deteriorated by the communication hole 22 for high pressure. The pressure equalization between the space and the low pressure space can be terminated.
Note that the diameter of the communication hole 22 that realizes the cross-sectional area of A ₂ is φ ₂ .

From the above, the opening area of the communication hole 22 of the discharge valve 20 is A ₀ or more and A ₂ or less, that is, 10% or more of the cross-sectional area ρ in the direction perpendicular to the axial direction of the swing shaft portion 6a of the swing shaft side boss space 2r. If the opening area σ of the discharge port is 4% or less, the refrigerating machine oil 11 is discharged from the communication hole 22 of the discharge valve 20 before the refrigerating machine oil 11 is discharged from the suction port 1e until the refrigerating machine oil 11 runs short when the compressor is stopped. The high-pressure refrigerant gas can be introduced to equalize the high-pressure space and the low-pressure space, and the efficiency of the compressor by re-intake / recompression of the high-pressure refrigerant gas during normal operation can be suppressed to less than 1%. Further, there is no possibility that the refrigerating machine oil stored in the sealed container is insufficient at the next start-up and the oil supply mechanism cannot be supplied.

A compressor with 5 to 10 horsepower will be specifically described with reference to FIG. At this time, the cross-sectional area ρ in the direction perpendicular to the axial direction of the swing shaft portion 6a of the swing shaft side surface boss space 2r is about 1.96 mm ² , and the opening area of the communication hole 22 of the discharge valve 20 is shown in the graph A. Is 10% of the cross-sectional area ρ of the oscillating shaft side boss space 2r, that is, about 0.196 mm ² or more, the high-pressure refrigerant gas so that the amount of the refrigerating machine oil 11 discharged from the suction port 1e is suppressed to about 80%. Flows in from the communication hole 22 side from the oil supply port 6d side. In order to realize the opening area of about 0.196 mm ^{2 with} the communication hole 22 being circular, a hole having a diameter of about 0.5 mm (φ _{0 in} FIG. 6) may be used. In consideration of the productivity and assemblability of the discharge valve 20 and its life, machining accuracy is required when the diameter of the communication hole 22 is 0.5 mm, and production takes time. Further, in the press or the like, in order to repeatedly open a small hole of 0.5 mm, it takes time for maintenance of the apparatus, and the productivity is poor. On the other hand, when the diameter of the communication hole 22 of the discharge valve 20 is 1.0 mm, the apparatus may be a general processing apparatus, and the durability is good for repeated processing. Thus, the compressor size 5-10 horsepower, for better diameter of the communication hole 22 of the discharge valve 20 which has the above 1.0mm (in FIG. 6 phi ₁₎ good productivity, the phi ₁ i.e. 1.0mm A communication hole 22 is provided as a lower limit. That is, if the diameter of the communication hole 22 of the discharge valve 20 is 1.0 mm or more, before the compressor oil 11 is discharged from the suction port 1e until the refrigerator oil becomes insufficient when the compressor is stopped, the communication hole 22 and the high-pressure space are formed. The effect of terminating the pressure equalization in the low pressure space is sufficiently obtained.

Further, the opening area σ of the discharge port is about 72.382 mm ² (= port diameter 9.6 mm), and the opening area of the communication hole 22 of the discharge valve 20 is about 4% of the discharge port, that is, about 3 from the graph B of FIG. If it is 142 mm ² or less, the amount of the refrigerating machine oil 11 discharged from the suction port 1e is about 40% and the efficiency of the compressor is suppressed to less than 1%. In order to realize an opening area of about 3.142 mm ² , the communication hole may have a diameter of about 2.0 mm (φ _{2 in} FIG. 6). As a result, if the diameter of the communication hole 22 of the discharge valve 20 is 2.0 mm or less, the efficiency of the compressor due to re-suction / recompression of the high-pressure refrigerant gas during normal operation can be suppressed to less than 1%, and the communication hole 22 The pressure equalization between the high pressure space and the low pressure space can be terminated by

  Therefore, in a compressor of about 5 to 10 horsepower, if the diameter of the communication hole 22 of the discharge valve 20 is set to 1.0 mm or more and 2.0 mm or less, the refrigerating machine oil 11 flows from the suction port 1e when the compressor stops. Before being discharged until the refrigeration oil becomes insufficient, the high pressure refrigerant gas can be flowed in from the communication hole 22 of the discharge valve 20 to equalize the high pressure space and the low pressure space, and the high pressure refrigerant gas can be recirculated during normal operation. The efficiency of the compressor by suction and recompression can be suppressed to less than 1%.

Depending on the type of refrigerant and the amount of refrigeration oil enclosed, the amount and speed of high-pressure refrigerant gas flowing in when the compressor is stopped are expected to differ between the inlet and outlet sides. Only the pressure balance, that is, the differential pressure between the high-pressure space and the low-pressure space in the container is different, the refrigerant gas flowing in from the oil supply port side and the discharge port side has the same pressure, and there is no significant difference in the opening area condition.
In addition, the amount of refrigeration oil can be increased as the scale of the refrigerant circuit increases, but this is because it takes time to circulate through the refrigerant circuit and return to the compressor again during normal operation. Since the amount of refrigeration oil stored in the sealed container is an amount that is expected to flow out even if it flows into the refrigerant circuit due to an increase in the amount of refrigeration oil enclosed, there is room for refrigeration oil shortage. There is no end. Therefore, the amount of the refrigerating machine oil is not significantly different from the opening area condition.
Therefore, the opening area is not affected by these conditions, and a sufficient effect can be achieved by relatively changing the opening area according to the design conditions of the compressor outlet and the compressor of the oil supply path.

From the above, the communication hole 22 of the discharge valve 20 is 10% or more of the cross-sectional area ρ in the direction perpendicular to the axial direction of the swing shaft portion 6a of the swing shaft side surface boss portion space 2r and 4% of the opening area σ of the discharge port. If the opening area is as follows, that is, the opening area A ₀ or more and A ₂ or less in FIG. 6 or the diameter φ ₀ or more and φ ₂ or less, the refrigerating machine oil 11 reaches the suction port 1e and is discharged to the external refrigerant circuit when the compressor is stopped. High pressure refrigerant gas can be flowed in from the discharge valve mechanism before the pressure equalization between the high pressure space and the low pressure space is completed, and the high pressure refrigerant gas discharged during normal operation is re-inhaled and recompressed, Decreasing the efficiency of the can be suppressed.
As a result, the refrigeration oil 11 rises from the high-pressure oil supply hole 6e of the main shaft 6 and flows out from the suction port 1e by the pressure equalizing action that occurs when the compressor stops without reducing the efficiency of the refrigeration cycle during normal operation. It is possible to avoid running out of machine oil.

The communication hole 22 on the discharge valve 20 does not need to be arranged so as to correspond to the center of the discharge valve 20, that is, the center of the opening of the discharge port 1d, and may be biased toward the peripheral portion. The communication hole 22 is described as a circle. However, the communication hole 22 is not necessarily a circle, and may be an ellipse or the like as long as the same opening area is secured.
Further, as shown in FIG. 5B, the same opening area may be ensured as the gap 23 lacking a part of the periphery of the discharge valve 20. Thereby, the discharge valve 20 is a simple process that does not worry about the strength of the discharge valve 20 rather than the process of making a hole. Further, if the discharge valve 20 is manufactured in a part process such as pressing, the process of punching holes at the same time in the part process can be performed, so that the manufacture is further facilitated.

  Further, as shown in FIG. 5C, the discharge valve 20 may be attached in a state where the closing portion of the discharge valve 20 and the opening of the discharge port 1d are shifted so that the gap 24 is opened even when the discharge valve 20 is closed. I do not care. If the opening area is equally secured, the same role and effect can be obtained by changing the mounting dimensions without adding any processing to the discharge valve 20 by such processing and assembly.

  Moreover, although the example which provided the clearance gap which lets high pressure refrigerant gas pass on the discharge valve 20 has been demonstrated, it does not necessarily need to be provided on the discharge valve 20. For example, FIG. 5D is provided on the fixed scroll 1 side, and a communication groove 25 is provided on the inner periphery of the discharge port 1d. Even if it is the communication groove 25, it does not change that it is a gap through which the high-pressure refrigerant gas passes, so that the effect does not change if the opening area is the same. Further, since the communication groove 25 may be connected to the discharge port 1d, the groove may not be provided to the vicinity of the compression chamber. That is, it is a groove that ends in the middle of the discharge port 1d as shown in (f) with respect to FIG. 5 (e), or that the groove near the discharge valve 20 becomes deeper and shallower as it approaches the compression chamber. It doesn't matter. As a result, the fixed scroll 1 having a high strength is processed in contrast to processing a weak component such as the discharge valve 20, so that the strength of the discharge valve 20 may be reduced due to the strength and processing during the processing. Is no longer needed.

A plurality of communication holes 22 on the discharge valve 20 and communication grooves 25 of the discharge port 1d may be provided. For example, as shown in FIG. 5G, the communication groove 25 may be divided into a plurality of communication grooves 25a and 25b. Moreover, you may have both the communicating hole 22a on the discharge valve 20, and the communicating groove 22b of the discharge outlet 1d. In any case, the total of the opening area penetrating the discharge port 1d is not less than the opening area A _{0 to} A ₂ shown in FIG. 6, that is, 10% or more of the cross-sectional area ρ of the oscillating shaft side boss space 2r. If the opening area σ is 4% or less of the opening area of the outlet, the same effect can be obtained.

  Therefore, when pressure equalization is performed in a scroll compressor having a compliant mechanism, the high-pressure refrigerant gas is passed from the high-pressure space via the discharge port by the closed container provided in the discharge valve mechanism and the opening communicating with the discharge port. Since it is made to flow into low pressure space, it can control that high pressure refrigerant gas and refrigerating machine oil are discharged from the oil supply path by the side of a main axis at the time of a compressor stop. Furthermore, it is possible to prevent the refrigerating machine oil stored in the sealed container from being insufficient at the next start-up and the oil supply mechanism from being unable to supply oil.

  On the other hand, the opening provided in the discharge valve mechanism during normal operation is configured to prevent the discharged high-pressure refrigerant gas from being sucked into the compression chamber again, so that the high-pressure refrigerant gas is re-sucked into the compression chamber and recompressed. This can be suppressed. That is, it is possible to prevent the compression performance of the compressor from being lowered.

  In addition, the combination with a compliant mechanism does not reverse the compression mechanism even when high-pressure refrigerant gas flows from the discharge port side. Therefore, a capillary tube that restricts the flow rate like a capillary passage of a conventional scroll compressor is used. Used without the need for processing and additional parts such as complex processing of the capillary tube to obtain the length of the capillary passage. Also, since it is difficult to drill a long hole with a small length that communicates with an end mill, etc., a work method and additional parts such as opening a large communication hole in advance and filling it with a bush that communicates with a capillary tube are added. do not need.

  Further, by being provided in the discharge valve or the discharge port, the scroll compressor can have the same function as the conventional one without interfering with other parts on the fixed scroll, the bypass path, and the like.

  Depending on the scroll compressor, a check valve is provided at the suction port so that the refrigerant gas does not flow backward from the compression chamber to the external refrigerant circuit via the suction port and suction pipe even if the swing scroll is reversed. There are also things. Even with this check valve, the refrigerant gas can be prevented from flowing from the high-pressure space in the sealed container to the low-pressure space due to the equalized pressure when the compressor is stopped, so that the refrigerating machine oil can also be prevented from flowing out. If the closing operation is delayed or incomplete, the refrigeration oil will flow out even with a slight gap, so the communication hole provided in the discharge valve will operate effectively and prevent the refrigeration oil from flowing out. . That is, there is no problem even if the check valve of the suction port, the discharge valve of the discharge port, and the communication hole of the discharge valve are provided side by side.

  Further, since the opening is realized by a hole, a groove, a gap, or the like, complicated and special processing can be realized without necessity. Also, there is no need to worry about the strength of parts during processing. For example, in the case of a discharge valve, a hole can be provided at the same time as the punching press. Since the groove does not need to be a deep groove having a large area, the machining is complicated, but the machining does not take much time compared to a long communication path having a small diameter.

  Furthermore, since the speed at which the high pressure and the low pressure are equalized is increased without worrying about the outflow of the refrigeration machine oil and the deterioration of the compression performance, the interval until the compressor is restarted can be increased. That is, if the compressor is restarted in a state where there is a differential pressure between high pressure and low pressure, it will wait until the differential pressure disappears because a large load is applied to the spindle and breaks, but the time to wait because the pressure equalizing speed is fast Less.

  As described above, with a simpler structure, it is possible to suppress the outflow of the refrigeration oil to the outside of the compressor caused by pressure equalization, and to obtain a highly reliable scroll compressor that does not cause a shortage of refrigeration oil.

Embodiment 2. FIG.
FIG. 7 is a diagram showing the second embodiment, which is realized by a bypass hole that bypasses the opening of the first embodiment to the discharge valve mechanism. In FIG. 7, the discharge valve 20, the discharge valve spring 21, and the discharge port 1d are the same as in FIG. On the other hand, the fixed scroll 1 is provided with a bypass hole 26 communicating with the discharge port 1d. Similar to the communication hole 22 of the discharge valve 20 and the communication groove 25 of the discharge port 1d, the bypass hole 26 circulates the refrigerant gas.

In the case of the bypass hole 26, pressure loss occurs as compared with the first embodiment, so that the opening area needs to be increased. That is, while passing through the bypass hole 26, the refrigerant is subjected to pressure loss, so that the flow velocity is lost in proportion to the passing time, that is, the passing distance. It is the range of the cross-sectional area of the swing shaft side boss space 2r, which is the reference range of the opening of the first embodiment, and the opening area of the discharge port, which is about twice that of the thickness of the base of the fixed scroll. If it is a distance, a loss of about 2 (%) is caused with respect to the distance through which the refrigerant passes.
Therefore, if the opening area is increased by about 2 × 1 (%) with respect to the length l (mm) of the bypass hole 26, the same effect as in the first embodiment is obtained. That is, by increasing the opening area of the bypass hole by 2 × l (%) with respect to the opening area of 10% or more of the cross-sectional area of the oscillating shaft side boss space 2r and 4% or less of the opening area of the discharge port, Before the refrigerating machine oil 11 rises from the high pressure oil supply hole 6e and is discharged from the suction port 1e, the pressure can be sufficiently equalized in the bypass hole 26.
More specifically, when the opening area opening area hole in the hole length of the bypass holes 26 and 10mm against 0.196Mm ² more 3.142Mm ² less necessary conditions, 20% large 0.235 mm ² If the opening area is 3.770 mm ² or less, the same effect can be obtained.

  Note that the number of bypass holes 26 is not limited to one, and a plurality of bypass holes 26 may be provided. At that time, if the total opening area is the same, before the refrigerating machine oil 11 rises from the high-pressure oil supply hole 6e of the main shaft 6 and is discharged from the suction port 1e without reducing the performance, the bypass hole 26 To equalize pressure.

Therefore, by adding the processing to the fixed scroll 1 without adding any processing to the discharge valve, it is possible to ensure the component strength at the time of processing or after processing.
Further, in the communication hole 22 of the discharge valve 20 and the communication groove 25 of the discharge port 1d, there is a possibility that high-pressure refrigerant gas discharged from the compression chamber during normal operation may be directly sucked from the communication hole 22 or the communication groove 25. Since the opening can be provided in the bypass hole 26 at a location away from the discharge port 1d, the high-pressure refrigerant gas after discharge is not directly sucked. Therefore, loss of recompression due to the backflow of the discharge gas can be suppressed.

Embodiment 3 FIG.
In the third embodiment, as shown in FIG. 8, a chamber 28 serving as an intermediate chamber 29 is provided on the back surface of the fixed scroll 1, and a discharge valve 20 is provided on the upper surface of the chamber 28. On the other hand, the communication hole 27 is provided so as to communicate between the sealed container 10 and the intermediate chamber 29 in the chamber 28. If an opening area similar to that of the first embodiment can be ensured, the communication hole 27 is not formed before the refrigerating machine oil 11 rises from the high-pressure oil supply hole 6e of the main shaft 6 and is discharged from the suction port 1e without lowering the performance. Equalize

  In FIG. 8, the communication holes 27 are provided vertically, but may be provided horizontally or may be inclined holes. One communication hole 27 is provided, but a plurality of communication holes 27 may be provided as long as the total opening area can secure the same opening area as in the first embodiment.

According to the above configuration, since the intermediate chamber 29 and the discharge port 1d have substantially the same pressure, the discharge valve 20 causes the high-pressure refrigerant gas to flow backward between the sealed container 10 and the intermediate chamber 29 during normal operation. It is preventing. On the other hand, since the communication hole 27 can be provided at a location away from the discharge valve mechanism, as in the second embodiment, the performance deterioration is caused such that the high-pressure refrigerant gas discharged from the discharge valve mechanism during normal operation is again sucked and recompressed. Will not cause.
Further, since pressure loss does not occur unlike the bypass hole of the second embodiment, it is not necessary to redesign the opening area, and the position to be provided can be set freely. No free design is possible.
In addition, it is difficult to make a hole in the fixed scroll 1 or to adjust the diameter of the hole so as not to deteriorate the performance. On the other hand, since the thickness of the chamber 28 does not have to be so thick, the processing is easy. Moreover, if it is manufactured in a part process such as pressing, it is not necessary to make a hole later, so that the processing is further simplified.

  In addition, even if it uses the chamber 28, the method of providing a communicating hole in the discharge valve 20 may be used, or the method of providing a bypass hole that bypasses the intermediate chamber 29 of the chamber 28 from the discharge port 1d and leads to the sealed container 10 may be used. Absent.

DESCRIPTION OF SYMBOLS 1 Fixed scroll 1a Fixed scroll base plate part 1b Fixed scroll plate-shaped spiral tooth 1c Oldham guide groove 1d Discharge port 1e Suction port 2 Swing scroll 2a Swing scroll base plate part 2b Swing scroll plate-shaped spiral tooth 2c Oldham guide groove 2d Boss part 2e Oscillating bearing 2f Thrust surface 2g Extraction hole 2h Lower opening part of extraction hole 2k Base plate outer peripheral space 2n Outer diameter space of boss part 2p Oscillating shaft upper surface boss part space 2r Oscillating axis side boss part space 3 Compliant Frame 3a Thrust bearing 3b Reciprocating sliding surface 3c Main bearing 3d Auxiliary main bearing 3e Communication hole 3f Communication hole 3g Intermediate pressure adjustment valve 3h Intermediate pressure adjustment valve 3e Intermediate pressure adjustment spring 3n Intermediate pressure adjustment valve space 3p Upper fitting surface 3s Lower fitting cylindrical surface 3t Thrust bearing opening 3u Main shaft main bearing space 4 Guide frame 4a Flexible Upper space 4b Lower frame space 4c Upper fitting cylindrical surface 4d Lower fitting cylindrical surface 5 Electric motor 5a Motor rotor 6 Main shaft 6a Oscillating shaft portion 6b Main shaft portion 6c Sub shaft portion 6d Oil supply port 6e High pressure oil supply hole 7a Upper ring Sealing material 7b Lower ring-shaped sealing material 8 Subframe 8a Sub bearing 9 Oldham mechanism 9a Oldham mechanism fixed key 9b Oldham mechanism swinging key 9c Oldham mechanism ring 10 Sealed container 10a Sealed container space 11 Refrigerating machine oil 12 Discharge Pipe 13 Suction pipe 20 Discharge valve 21 Discharge valve feed 22 Communication hole 23 Cavity 24 Cavity 25 Communication groove 25a Communication groove 25b Communication groove 26 Bypass hole 27 Communication hole 28 Chamber 100 Compressor 101 Condenser 102 Expansion valve 103 Evaporator

Claims (13)

A sealed container having a sump in which refrigerator oil is stored at the bottom;
A plate-like spiral tooth of the fixed scroll and a plate-like spiral tooth of the rocking scroll, each comprising a fixed scroll and a rocking scroll provided with a hollow cylindrical boss having a rocking bearing. A compression chamber formed by combining
A frame having a boss portion outer diameter space fixed to the hermetic container and formed between the swing scroll and a communication passage communicating from the boss portion outer diameter space to the outer peripheral portion of the swing scroll, and the main shaft portion swing. A main shaft having an oil supply path that is supported by the frame and supported by the frame and rotatably supports the rocking scroll via the rocking shaft and the rocking bearing. When,
A suction port provided on an outer peripheral portion of the fixed scroll for sucking refrigerant from a low-pressure space outside the hermetic container into the compression chamber;
A discharge port for discharging the refrigerant compressed in the compression chamber provided in a central portion of the fixed scroll to a high-pressure space in the sealed container;
A discharge valve provided at the discharge port for opening and closing the discharge port;
An opening that is provided in the discharge valve or the discharge port and communicates the high-pressure space and the discharge port when the discharge valve closes the discharge port;
The main shaft oil supply path enters from the high pressure space through the oil sump, passes through the bearing clearance between the swing shaft portion and the swing bearing, and communicates with the boss portion outer diameter space through the communication path of the boss portion outer diameter space. A first communication passage that communicates with the suction port through an outer peripheral portion of the orbiting scroll,
From the high-pressure space, passes through the discharge port, enters the compression chamber, and communicates with the suction port via the clearance of the tip of the plate-like spiral teeth of the fixed scroll or the clearance of the tip of the plate-like spiral teeth of the orbiting scroll. A second communication path;
With
An opening area of the opening of the second communication path is larger than a cross-sectional area of the bearing gap forming the first communication path in a direction perpendicular to the axial direction of the main shaft. A scroll compressor characterized by being smaller than the opening area of the outlet. 2. The scroll compressor according to claim 1, wherein a cross-sectional area of the bearing gap in a direction perpendicular to the swinging shaft portion is the smallest in the first communication path. The scroll compressor according to claim 2, wherein an opening area of the discharge port is the largest in the second communication path. 4. The scroll compressor according to claim 3, wherein the compression chamber is formed by allowing a refrigerant to flow between the compression chamber and the frame space to press the swing scroll toward the fixed scroll. The scroll compressor according to claim 3 or 4, wherein a chamber for forming an intermediate chamber is provided between the discharge mechanism and the discharge port. The scroll compressor according to any one of claims 3 to 5, wherein the opening is a communication hole provided in the discharge valve. 5. The scroll compressor according to claim 3, wherein the opening is a communication groove that connects the discharge port provided in the discharge port and the high-pressure space. 6. The scroll compressor according to claim 3, wherein the opening is a bypass hole that communicates the discharge port provided in the fixed scroll and the high-pressure space. The scroll compressor according to claim 5, wherein the opening is a communication hole provided in the chamber and communicating the inside of the chamber and the high-pressure space. The opening is an opening area that is not less than 10% of a clearance cross-sectional area between the swing shaft and the swing bearing and not more than 4% of an opening area of the discharge port. Scroll compressor described in 1. The scroll compressor according to claim 6, wherein the communication hole is a hole having a diameter of 1 mm or more and 2 mm or less. 12. A suction check valve for preventing the refrigerant from flowing backward from the compression chamber to the low pressure space outside the sealed container through the suction port at the suction port. The scroll compressor in any one of. A scroll compressor according to any one of claims 1 to 12, a condenser that condenses the refrigerant compressed by the scroll compressor, a decompressor that depressurizes the refrigerant condensed by the condenser, A refrigerating and air-conditioning apparatus, comprising: a refrigerant circuit that connects the evaporator that evaporates the refrigerant decompressed by the decompressor with a pipe and circulates the refrigerant.

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