JP2006329208A - Scroll compressor - Google Patents

Abstract

In a scroll compressor, the amount of oil flow between a high-pressure hydraulic chamber and a low-pressure chamber formed on the back surface of a revolving scroll end plate and sealed is optimized to reduce the performance and reliability of the compressor. To solve.
A sealing means (34) for sealing a back pressure chamber (36) and a high pressure hydraulic chamber (41) at the upper peripheral portion on the main shaft (14) side is provided with a boss of the orbiting scroll (6) having an orbiting scroll bearing portion. A small amount of oil is passed over the sealing means by providing a hole (58) for retaining oil on the inner peripheral surface of the frame (11) facing the front end surface of the portion (6c) and holding the oil on the front end surface of the boss portion. An oil supply passage that leaks from the high pressure chamber to the low pressure chamber is configured. The amount of oil flowing from the high-pressure chamber to the low-pressure chamber is optimized, so that the performance of the compressor can be greatly improved and the reliability of the compressor can be improved.
[Selection] Figure 5

Description

  The present invention relates to a scroll compressor used as a refrigerant compressor for refrigeration and air conditioning, a refrigerator, and the like.

In the conventional scroll compressor, for example, as disclosed in Patent Document 1 below, the refrigerant gas compressed by the scroll compression mechanism portion reaches the motor chamber from the upper discharge chamber via the communication passage. Next, the refrigerant gas flows out from the discharge pipe of the compressor through the periphery of the electric motor. The back pressure chamber on the back of the end plate of the orbiting scroll has a structure in which the lubricating oil discharged from the seal ring can be easily stored.
Japanese Patent Laid-Open No. 2-9973 (Japanese Patent Publication No. 7-51950)

In the prior art reference example, the back pressure chamber is filled with lubricating oil discharged from the hydraulic chamber, which is a high pressure chamber, through the throttle passage provided in the seal ring, and all the oil is sucked through the thrust bearing surface. It is an oil path that flows into the chamber. The oil amount is adjusted by the size of the oil film thickness of the throttle passage provided in the seal ring and the thrust bearing surface provided on the back surface of the outer periphery of the end plate of the orbiting scroll. In such a configuration, since there is only a single oil amount adjustment function, a large amount of oil tends to flow out even at a small throttle part, the oil amount adjustment is unstable, and further, the value of the intermediate pressure Furthermore, there is a problem that the volume efficiency of the compressor is lowered due to the heating action of the suction refrigerant gas due to the oil path through which the high pressure oil flows into the suction chamber side.
An object of the present invention is to make it possible to easily adjust the amount of oil leakage from the high-pressure hydraulic chamber to the low-pressure chamber to prevent the performance of the compressor from deteriorating.

  In order to achieve the above object, a scroll compressor according to the present invention is provided so as to face the fixed scroll and the orbiting scroll formed by erecting a spiral wrap on a disc-shaped end plate, and the back side of the orbiting scroll. In a scroll compressor including a stationary frame, a seal portion is provided between the orbiting scroll back side and the frame, thereby forming a high-pressure hydraulic chamber formed on the inner side and an outer side of the seal portion. And an oil supply passage that intermittently communicates the high-pressure hydraulic chamber and the low-pressure chamber by the orbiting motion of the orbiting scroll.

  Similarly, a scroll compressor according to the present invention includes a fixed scroll and a turning scroll formed by uprighting a spiral wrap on a disk-shaped end plate, and a stationary frame provided so as to face the back side of the turning scroll. A scroll compressor provided with a pedestal portion of the frame which is a stationary member facing the orbiting scroll, and a sealing means for partitioning into a high pressure hydraulic chamber and a low pressure chamber, the orbiting motion of the orbiting scroll, and the An oil supply path that communicates the high-pressure hydraulic chamber and the low-pressure chamber intermittently with a sealing means is provided so that oil in the high-pressure hydraulic chamber flows intermittently into the low-pressure chamber. It is.

  In such a configuration, the amount of oil leakage from the sealing means to the low pressure chamber or the back pressure chamber can be adjusted to a minute amount or an appropriate amount, and the oil can lubricate sliding portions such as the Oldham portion. By adopting such a configuration means, the amount of oil flowing from the high pressure hydraulic chamber 41 to the low pressure chamber or the back pressure chamber can be optimized, and the low pressure chamber of the oil flowing out of the bearing gap with respect to the conventional machine can be optimized. Alternatively, the amount of inflow into the back pressure chamber can be controlled appropriately. For this reason, an oil pool phenomenon is avoided in the low pressure space.

  In the case where oil is injected into the compression chamber through the pores provided in the end plate of the orbiting scroll, the oil is discharged smoothly from the back pressure chamber, and the intermediate pressure of the conventional machine fluctuates. The phenomenon is avoided. In addition, if the amount of oil is small, stirring loss does not occur. Further, the trace amount of oil moves to the Oldham chamber 51 and is used for oil lubrication in the Oldham sliding portion, and oil is accumulated in the Oldham key groove portion and lubrication in the peripheral portion is reliably performed. As shown in FIG. 26, the amount of oil leaked into the back pressure chamber is within an appropriate range, thereby improving the performance and reducing the noise of the entire compressor. Further, since the amount of oil circulating in the compressor is kept to a minimum, the amount of oil rising from the compressor to the outside is reduced, and the oil is always held in the compressor.

  Further, as a specific oil leakage structure added to the sealing means, as shown in FIGS. 13 to 15, it is provided in the annular groove on the end surface of the center portion of the frame at the tip surface of the orbiting boss portion having the orbiting scroll bearing portion. Provided with a hole having a hole diameter equal to or smaller than the seal ring width, and as the turning boss part having the orbiting scroll bearing part having the hole makes a turning circular motion, the oil in the hydraulic chamber around the spindle accumulates in the hole, There is an embodiment in which an oil leakage means is formed such that the oil is discharged on the back pressure chamber side across the seal ring.

  The transfer by this structure is hereinafter referred to as “oil pocket type transfer method”. As shown in FIG. 27, the amount of leaked oil (Qob) by the oil pocket type transfer method is not determined by the differential pressure between the high pressure hydraulic chamber and the back pressure chamber, but the number of rotations of the crankshaft and the total volume of the holes. As a result, the oil leakage amount can be kept constant regardless of the operating pressure conditions, and can be improved including the problems of performance degradation and performance variation caused by the oil of the conventional machine. There is an action and an effect that can prevent the lowered reliability.

In the case of the conventional machine, as shown by the two-dot chain line (straight line (a)) and broken line (straight line (b)) in FIG. 27, the oil leakage amount characteristic proportional to the differential pressure between the high pressure hydraulic chamber and the back pressure chamber. Therefore, when it is desired to suppress the pressure to a pressure of 100 cm ³ / min or less under the necessary seal differential pressure condition of a few tens of kg / cm ² , the passage area of the throttle portion in the above cited example is set to a very small value of about 0.05 mm ^2. In addition, there is a problem or problem that the oil leakage amount characteristic has a large variation as shown in the straight line (a) and the straight line (b) in FIG.

  Furthermore, as another minute oil leakage structure added to the sealing means, for example, a swivel boss having a recess (oil supply passage) having an opening equal to or larger than the seal ring width on the tip surface of the swivel boss, and having the recess As the part makes a swiveling circular motion, oil in the hydraulic chamber around the main shaft accumulates in the recessed part, and constitutes an oil leakage means that drains oil on the back pressure chamber side across the seal ring, the recessed part The center position may be set to be deviated from the center diameter of the annular seal ring fitted in the annular groove at the end face of the center portion of the frame to the inside or outside.

  By doing so, the hydraulic chamber and the back pressure chamber around the spindle are intermittently communicated via the recess. The larger the eccentric dimension, the shorter the communication period between the two chambers, and the oil leakage amount can be adjusted. Further, as another oil leakage structure added to the sealing means, a dimple-shaped fine hole may be provided on the tip surface of the orbiting boss portion having the orbiting scroll bearing portion. The dimple-like micropore structure on the tip surface of the swivel boss has the effect of reducing the deformation of the sliding surface of the resin seal ring, and has the effect of extending the life of the resin seal ring. In addition, a minute gap (abutment gap) provided in the circumferential direction of the seal ring can prevent creep deformation due to thermal expansion.

  Furthermore, in this structure, the amount of high-temperature oil leaking into the suction chamber can be reduced, so that the internal heating amount of the suction gas in the suction chamber can be reduced. For this reason, the overall heat insulation efficiency can be greatly improved by improving the volumetric efficiency and reducing the stirring loss by reducing the internal heating amount of the suction gas. In addition, this effect and action are significant in the present invention under the operating conditions in the high pressure ratio region of the conventional machine in which the bearing oil amount increases and the internal heating amount of the suction gas increases.

  According to the present invention, an oil supply path (oil supply path) such as a recess that intermittently communicates the high pressure hydraulic chamber and the low pressure chamber by the orbiting motion of the orbiting scroll is provided. The amount of leakage can be easily adjusted, and as a result, there is an effect of preventing the performance of the compressor from being deteriorated.

  Embodiments of the present invention will be described with reference to FIGS.

  FIGS. 1 and 2 show a structure in which a seal portion 220 is provided that seals a high-pressure hydraulic chamber 215 and a low-pressure hydraulic chamber 216 on a frame base portion 202 of a stationary member facing the end plate back surface portion 200a of the orbiting scroll 200. 1 illustrates an embodiment of the invention. The low pressure hydraulic chamber 216 means a space in an atmosphere of suction pressure, or means a space that is an intermediate pressure between the suction pressure and the discharge pressure.

The end plate rear portion 200a of the orbiting scroll 200 is in position within the longitudinal size of the distance range of the turning radius epsilon _th substantially orbiting scroll with respect to the radial position of the seal ring 220a of the seal portion 220, the seal portion A hole or recess 205 having a hole diameter d ₁ equal to or smaller than the width L ₁ of the seal ring 220a is provided, and the cross-sectional shape of the hole is preferably circular, but may be other polygonal shapes. In FIG. 1, the center-to-center distance between the seal ring 220a and the hole 205 is indicated by Lr, and there is a relationship of Lr≈εth. In FIG. 1, as the orbiting scroll 200 having the hole 205 moves in a circular motion, the oil 22 a in the hydraulic chamber 215 enters the hole 205 and fills up.

Next, as shown in FIG. 2, as the orbiting scroll 200 performs the orbiting circular motion, the position of the hole moves from the position of the broken line 205a to the position of the solid line 205b. Since the position of the hole 205b is in the atmosphere of the low pressure chamber 216, the oil 22a accumulated in the hole is discharged downward. In this manner, the hole 205 (so-called “oil pocket”) provided in the end plate back surface portion 200a of the orbiting scroll 200 replenishes oil in the high-pressure hydraulic chamber 215 along with the orbiting circular motion, and the low pressure across the seal ring. The oil leakage means is configured to be discharged on the chamber side. With the dimensional relationship of Lr ≒ epsilon _th mentioned above, intermittently tighten equally made a replenishing action and discharge action of the oil as described above is performed, in which most efficiently obtained.

3 and 4, an annular seal portion 220 that seals the high-pressure hydraulic chamber 215 and the low-pressure chamber 216 is formed on the end plate back surface portion 200 a of the orbiting scroll 200, and a frame of a stationary member that faces the seal portion 220. An embodiment in which the oil transfer hole 206 is installed in the pedestal portion 202 is shown. The hole 206 is a hole 206 having a hole diameter d ₁ equal to or smaller than the width L ₁ of the seal ring 220 a of the seal portion 220. Sealing ring 220a serving as a seal portion 220 provided in the end plate back surface portion 200a of the orbiting scroll 200, with respect to the radial position of the oil transfer holes 206 of the frame base portion 202, the front and rear sizes distance of the turning radius epsilon _th It is in a position within the range. I.e. the dimensional relationship of Lr ≒ epsilon _th as shown in FIG.

  As shown in FIG. 3, as the orbiting scroll 200 performs the orbiting circular motion, the oil 22 a in the hydraulic chamber 215 enters and fills the hole 206, and then, as shown in FIG. As the orbiting scroll 200 performs the orbiting circular motion, the position of the hole is in the atmosphere of the low pressure chamber 216, and therefore the high pressure oil 22a accumulated in the hole is discharged and discharged. Thus, the hole 206 provided in the frame pedestal portion 202 becomes the atmosphere of the high pressure hydraulic chamber 215 as the seal ring rotates, and then the atmosphere of the low pressure chamber 216. As a result, the oil replenishing action and discharging action of the hole 206 can be made to function intermittently.

  5 and the subsequent embodiments show specific embodiments of a small amount of oil leakage means by the oil pocket transfer method described above.

  FIG. 5 is a longitudinal sectional view showing the entire configuration of the hermetic scroll compressor. As shown in FIG. 5, the compressor unit 100 is accommodated in the upper part of the sealed container 2, and the electric motor part 3 is accommodated in the lower part. The sealed container 2 is partitioned into an upper chamber 1a (discharge chamber), an upper motor chamber 1b, and a lower motor chamber 1c. The compressor unit 100 forms a compression chamber 8 by meshing the fixed scroll 5 and the orbiting scroll 6 with each other.

  The fixed scroll 5 is composed of a disc-shaped end plate 5a and a wrap 5b which is formed upright on the involute curve or an approximate curve thereof, and has a discharge port 10 at the center and a suction port 16 at the outer periphery. I have. As shown in FIG. 6, the frame 11 forms a bearing portion 40 in the center portion, and the rotating shaft 14 is supported on the bearing portion 40, and the eccentric shaft 14 a at the tip of the rotating shaft is connected to the boss portion 6 c of the orbiting scroll 6. The oil chamber 6k is formed between the rotating boss bottom 29 and the rotating boss bottom 29.

  Further, the fixed scroll 5 is fixed to the frame 11 by a plurality of bolts, and the orbiting scroll member 6 is supported on the frame 11 by an Oldham ring 38 comprising an Oldham ring portion and an Oldham key portion as shown in FIG. The scroll 6 is formed to rotate with respect to the fixed scroll 5 without rotating. A perspective view showing the entire structure of the Oldham ring 38 is shown in FIG. An electric motor shaft 14b fixed to the rotor 3b is integrally connected to the lower portion of the rotating shaft 14, and the electric motor unit 3 is directly connected thereto.

  A vertical suction pipe 17 is connected to the suction port 16 of the fixed scroll 5 through the hermetic container 2, and the upper chamber 1a in which the discharge port 10 is opened is connected to the upper motor via a passage 18 (18a, 18b). It communicates with the chamber 1b. The upper motor chamber 1b communicates with the lower motor chamber 1c through a passage 25 between the motor stator 3a and the side wall 2a of the sealed container 2. The upper motor chamber 1 b communicates with a discharge pipe 20 that penetrates the sealed container 2. Reference numeral 22 denotes an oil reservoir at the bottom of the sealed container, and the lubricating oil 22 a is stored as an oil reservoir 22 in the lower part of the sealed container 2. Reference numeral 15 denotes a check valve portion of the suction portion, which is urged by a check valve spring 5h.

  The upper end of the rotary shaft 14 is provided with an eccentric shaft portion (crank pin) 14a, and the eccentric shaft portion 14a is a scroll compression element portion which is a scroll compression element portion via a swing bearing 32 in a boss portion 6c of the end plate 6a of the swing scroll 6. 6 is engaged. The rotating shaft 14 is formed with an eccentric vertical hole 13 for supplying oil to each bearing portion from the lower end to the upper end surface of the rotating shaft 14. An oil pumping pipe 23 connects the lower end of the rotating shaft 14 and the bottom oil sump 22. Below the eccentric shaft portion 14a is a main bearing (sliding bearing type with thrust rod) 40, and on the outer periphery thereof, there is a back pressure chamber 36 on the back of the end plate of the orbiting scroll and a high pressure hydraulic chamber 41 on the periphery of the main shaft side. The frame end surface 11c is provided with a sealing means 34 for sealing the frame.

  A first balance weight 9a that cancels the centrifugal force accompanying the orbiting motion of the orbiting scroll 6 is fixed to the main shaft 14 on the lower side of the frame 11 on the motor chamber 1b side. Since the first balance weight 9a that cancels the centrifugal force associated with the orbiting motion of the orbiting scroll 6 is disposed on the main shaft 14 on the lower side of the frame 11 on the electric motor chamber 1b side, the space is a refrigerant gas region. Is not an oil atmosphere, the agitation loss due to the rotation of the balance weight 9a can be greatly reduced.

  The lower end of the oil pumping pipe 23 immersed in the oil reservoir 22 of the lubricating oil 22a receives a high discharge pressure Pd. The lubricating oil 22 a in the oil reservoir 22 at the bottom of the container rises in the eccentric vertical hole 13 by the centrifugal pump action in the eccentric vertical hole 13. In addition, the periphery of the slewing bearing 32 and the main bearing (slide bearing 40) is in a state of an intermediate pressure Pm that is a pressure during compression by the sealing means 34 by the pore 6d (see FIG. 8) provided in the slewing end plate 6a. Therefore, it is in an atmosphere of approximately discharge pressure. The lubricating oil 22 a that has moved up in the eccentric vertical hole 13 is supplied to the main bearing 40 and the swivel bearing 32. A small amount of oil supplied to the bearing portions 32 and 40 flows into the back pressure chamber 36 through the sealing means 34.

  As shown in FIG. 6, the oil that has flowed into the back pressure chamber 36 flows into the Oldham chamber 51 via the communication channel groove 11 m and lubricates the periphery of the Oldham ring portion 38. Further, as shown in FIG. 7, a part of the minute amount of oil leaks from the outer periphery of the swivel end plate through the end plate sliding surface 5k to the suction chamber 5f and mixes with the suction refrigerant gas.

  On the other hand, the oil in the back pressure chamber also flows out into the compression chamber 8 through the back pressure hole 6d. The oil that has reached the compression chamber 8 is pressurized together with the refrigerant gas while preventing the leakage between the compression chambers while sealing the gap between the scroll wraps, and the discharge chamber 1 a above the fixed scroll 5 via the discharge port 10. It moves to the motor room 1b. In the discharge chamber 1a and the electric motor chamber 1b, the refrigerant gas and the oil are mainly separated, and the oil falls into the oil sump 22 at the lower part of the hermetic container 2 and is supplied again to the sliding portions. By using such an oil flow, lubrication is reliably performed in each part of the compressor.

  A self-aligning spherical guide bearing 44 a is applied to the lower bearing portion 44 to prevent strong contact between the main shaft 14, the main bearing portion 40, and the lower bearing portion 44. In the figure, solid arrows indicate the direction of refrigerant gas flow, and broken arrows indicate the direction of oil flow.

  In FIG. 5, the main shaft 14 is configured to be supported by the hooked portion of the hooked sliding bearing portion 41, but if the main shaft moves upward, the upper end surface of the main shaft stepped portion 14 m turns. The main shaft 14 is set so that the upper end surface of the eccentric shaft 14a comes into contact with the rotating boss bottom surface 6p first so that the boss end surface (seal surface) 6n is not damaged. The amount of thrust movement of the main shaft 14 is determined by an axial gap between the upper end surface of the eccentric shaft 14a and the bottom surface 6p of the turning boss, and the clearance is determined by the upper end surface of the stepped portion 14m of the main shaft and the end surface of the rotating boss (seal Surface) is set smaller than the gap with 6n.

  In FIG. 5, the oil rising from the eccentric hole 13 is supplied to the main bearing 40 and the swivel bearing 32 and then reaches the high-pressure hydraulic chamber 41. The oil in the hydraulic chamber 41 is guided from the oil drain hole 37 to the oil drain pipe 60 and reaches the inner wall surface 2c of the sealed container. Next, the discharged oil falls downward along the container side wall surface 2c.

  FIG. 6 is a partial longitudinal sectional view showing the structure of the periphery of the frame 11 and the sealing means 34. An end plate support seat 11f that supports the rear portion of the end plate portion of the orbiting scroll is formed in the middle upper portion of the frame that supports the central spindle 14, and the Oldham ring main body portion 38a and Oldham key portion 38b are used as rotation preventing members for the orbiting scroll. An Oldham ring 38 is arranged between the orbiting scroll 6 and the frame 11. There is a frame pedestal surface 11p in which the Oldham ring main body 38a faces in the axial direction.

  In FIG. 6, a seal means 34 for sealing the back pressure chamber 36 on the back surface of the end plate of the orbiting scroll and the high pressure hydraulic chamber 41 in the vicinity of the main shaft side is provided on the end surface 11c of the center portion of the frame. The oil flowing out of the bearing gap is prevented from flowing into the back pressure chamber 36 by the sealing means 34 as much as possible, but a small amount of oil is mixed in to ensure the performance and reliability of the compressor and to reduce noise. The oil supply path constitutes an oil supply path according to the “oil pocket transfer method” as shown in FIGS. 13, 14, and 18, for example. The trace amount of oil mixed in the back pressure chamber 36 moves to the Oldham chamber 51 and is used for oil lubrication at the Oldham sliding portion.

  Further, regardless of the axial movement and tilt of the orbiting scroll 6 of several tens of microns, the axial clearance δc is formed between the tip surface 6n of the orbiting boss portion 6c and the frame inner peripheral surface 11c except for the seal portion of the sealing means. Secured. That is, the height Lm of the turning boss is set to be several hundred microns smaller than the height Lf of the frame base 11f. Practically, the gap in the axial direction δc = 0.3 mm to around 0.5 mm. As a result, the tip surface 6n is not damaged, damage to the seal surface of the seal portion 34 can be avoided, and the life of the seal portion mechanism can be extended and the reliability can be improved.

  That is, irrespective of the axial movement and tilting of the orbiting scroll 6, except for the seal portion of the sealing means, as shown in FIG. Since the depth Lf has a dimensional relationship of Lf> Lm, an axial gap δc can be secured between the tip end surface 6n of the orbiting boss portion 6c and the frame end surface 11c even when moving from the orbiting scroll to the frame side. The tip surface 6n is not damaged. In other words, the dimensional relationship of Lf> Lm is used to restrict the axial movement of the rear plate portion of the orbiting scroll at the upper end surface portion of the frame base portion.

  In FIGS. 7 and 16, the space formed by the rear surface of the end plate 6a of the orbiting scroll and the frame 11 is turned around the rotating boss portion 6c by the annular frame base portion 11f that restricts the axial movement of the end surface of the end surface of the orbiting scroll. Is divided into a back pressure chamber 36 and an Oldham chamber 51 provided with an Oldham mechanism portion outside the frame pedestal portion, and a groove 11m communicating the back pressure chamber and the Oldham chamber is formed at the upper end surface of the frame pedestal portion. However, the bottom surface of the communication groove 11m is set to a position above the position of the bottom surface 11p of the Oldham chamber 51 outside the frame pedestal portion 11f.

  That is, the bottom surface of the communication groove 11m has a structure projecting by an amount L5 from the bottom surface 11p of the Oldham chamber 51. With such a configuration, the Oldham chamber serving as the outer peripheral portion of the end plate support seat 11f functions as an oil reservoir at the projection 59. Inevitably, oil also accumulates in the Oldham key groove 57a.

  Further, the oil 22a accumulated in the Oldham chamber 51 scatters to the peripheral portion as the Oldham ring main body portion 38a reciprocates, and becomes oil droplets for lubrication of the back pressure chamber and the sliding portion of the Oldham chamber 51. For this reason, even if the compressor is stopped, oil remains in that portion, and the oil is always present in the Oldham key groove portion 57a on which the rotation load acts. When the compressor is restarted, there is no longer a shortage of oil as in the conventional machine. Further, the loss of the lubrication performance of the sliding portion of the Oldham mechanism due to insufficient oil amount is also eliminated, and the reliability of the Oldham mechanism can be improved.

  As shown in FIG. 7, the end plate 6a of the orbiting scroll is sandwiched between the fixed scroll end plate surface and the upper end surface of the frame pedestal portion 11f with a minute gap δh (back gap) of several tens of microns. This gap is on the back side of the swivel mirror. The minute gap δh is about 1/10 of the axial gap δc described above.

  8 and 9 are a plan view and a longitudinal sectional view of the orbiting scroll. A plurality of small holes 58 are provided on the tip surface 6 n of the orbiting boss portion having the orbiting bearing portion 32 of the orbiting scroll 6. The tip end portion 6c of the turning boss portion is set larger than the housing diameter of the central portion 6h of the turning bearing portion 32. 6 m is an Oldham key groove on the orbiting scroll side. The pore 6d provided in the swivel end plate 6a is located in the end plate portion 6a in the vicinity of the wrap side wall 6b within one turn from the scroll end portions 6j and 6i toward the wrap center. For example, the wrap winding angle of the scroll winding end 6i, that is, the wrap winding end angle on the swirling outer line chamber side, is the position of λe = 16.0 rad as the involute extension angle of the involute curve. On the other hand, the pore 6d has an involute extension angle of λb = 12.3 rad. With such a positional relationship, the intermediate pressure Pm, which is a pressure during compression during the suction process, can be guided to the back pressure chamber 36, and the lubricating oil in the back pressure chamber 36 can be passed through the hole 6d. Thus, the discharge operation toward the compression chamber 8 can be performed smoothly.

  10 to 12 are a plan view, a longitudinal sectional view, and a partial perspective view of the seal ring portion 34a of the sealing means 34. FIG. The seal ring portion 34a may be made of cast iron, aluminum, or a fluororesin material. In order to avoid creep deformation due to thermal expansion, the seal ring part 34a is provided with a stepped cut 34h in the resin ring 34a and an initial gap (for example, a minute gap of several tens of microns) L9 in the circumferential direction. This L9 is referred to as “abutt gap”. When an internal pressure is applied to the inner side of the seal ring 34a by providing stepped cuts (notches), as shown by the broken line in FIG. 34m comes into close contact with the outer surface 33m of the annular groove to improve the sealing performance. The ΔL dimension and the deformed joint gap L9 'have the following relationship.

L9 ′ = L9 + 2 × 3.14 × ΔL (1)
What seals the space 34c between the upper and lower joint gaps is the linear portion (curved portion) of the circumferential seal portion 34h. The seal length L10 is practically a seal length of about 1.5 times to about twice the seal width L1 and the seal height L1. As a result, the size of the annular groove, the outer diameter of the seal ring, etc. will be determined so that L9 ′ = 0.2 or less. Thus, by providing the resin sealing means 34, for example, a Teflon (registered trademark) soft resin sealing ring, it is possible to secure sealing performance and relax the dimensional accuracy of the peripheral portion of the seal ring groove. . As a circumferential clearance, L8 = L9 = 0 to 0.1 mm is experimentally good in terms of sealing performance.

  As shown in the solid line arrow in FIG. 12, the resin seal ring 34a provided with a stepped cut (cut portion) is a belt-like seal ring in which the circumferential gap is cut into a minute gap. Even with a slight pressure difference, the belt-like seal ring can be finely moved in two directions, the circumferential direction and the radial direction, so that it can be brought into close contact with the entire peripheral area of the outer peripheral surface 33m of the ring groove 33. However, the sealing performance of the portion can be exhibited by the above-described operation.

FIGS. 13 to 15 show an embodiment in which a plurality of small holes 58 are provided on the tip surface 6n of the orbiting boss portion having the orbiting bearing portion 32 of the orbiting scroll 6 as a fine oil leakage structure added to the sealing means. The plurality of small holes 58 have a hole diameter d1 equal to or smaller than the seal ring width L1 at a position having a center diameter D2 substantially equal to the center diameter D1 of the seal ring 34a provided in the annular groove 33 of the end surface 11c at the center of the frame. Have. By adopting such a configuration, the plurality of small holes 58 allows the oil in the hydraulic chamber 41 around the main shaft to accumulate in the small holes as the turning boss part of the orbiting scroll having the holes makes a turning circular motion. From the state of FIG. 13, the oil is intermittently drained to the back pressure chamber 36 side of the state of FIG. 14 across the seal ring 34 a, so that the oil replenishing action and the draining action function efficiently. be able to. The bottom hole for improving the loss of oil from the hole 58 and a conical shape, is substantially equal to the pore depth H ₁ and hole diameter d _1.

  In FIG. 13, 14 g is a flange portion provided to support the main shaft 14 with a thrust receiving surface portion 40 a of the main bearing 40 and to be able to slide in contact. Along with the rotational movement of the flange portion 14g, the oil around the flange portion 14g in the hydraulic chamber 41 is pushed upward, and the pushed-up oil easily enters the small hole 58 as indicated by the arrow. A reliable oil replenishment action is obtained. In FIG. 14, the area inside the groove outer diameter D4 of the annular groove 33 is a discharge pressure region, and the oil pressure in this portion occupies most of the axial pressing force toward the orbiting scroll.

As shown in FIG. 15, each of the plurality of small holes 58 arranged on the circumference equally has an oil transfer function once per rotation of the crankshaft. Ε _th in the figure means the turning radius. As shown by the solid line in FIG. 27, the amount of oil leaked by this oil pocket type transfer method is not generally determined by the differential pressure (Pd−Pm) between the hydraulic chamber and the back pressure chamber, and the rotational speed of the crankshaft and the small hole 58 The total volume can be determined. That is, the oil leakage amount Qob (cc / min) is approximately determined by the following equation.

Qob = N × 3.14 × d ₁ ² × H × n × η / 4 (2)
Where N: number of revolutions (rpm) n: number of small holes
η: Transfer efficiency (ratio of actual flow rate to theoretical flow rate)
Further, in order to further improve the above-described oil drainage and reduce outflow resistance, an annular recess 63 is provided on the frame end surface 11c outside the annular groove. In FIG. 26, the oil leakage amount is adjusted so that the amount of oil leakage from the sealing means to the back pressure chamber is about r0 = 1.5% by weight with respect to the amount of refrigerant sucked in the compressor. It is an experimental value indicating that the compressor performance has a peak value and the noise level is lowered and has an effect by making it a very small amount. FIG. 13 shows a structure in which a backup spring 34f is added to the back portion of the seal ring 34a in order to ensure the operation of the seal ring 34a. The backup spring may be formed in a ring shape in the form of a corrugated plate made of, for example, a stainless steel strip for springs, having a plate thickness of about 0.2 mm and a free height of the ring of about 1 mm. (The illustration is omitted.) As shown in the equation (2), a constant amount of oil is always ensured regardless of the differential pressure, thus avoiding the oil shortage phenomenon in the sliding part between the back pressure chamber and the Oldham chamber. Is done.

  18 to 25 show an embodiment in which other minute oil leakage means are configured. 18 includes a recess 72 having an opening having a radial width W1 equal to or less than the seal ring width on the tip surface 6n of the swivel boss 6c, and the recess 72 has a long hole shape extending in the circumferential direction. It is an embodiment. The indented portion 72 is within the width (sliding contact width) W2 for sliding contact shown in FIG. 18, and is set at least inside the seal ring width. In the figure, 6s indicates a sliding contact surface. 19 and 20 show the hole shapes of the recessed portions 58 and 72. These are examples of a rectangular cross section and a conical cross section, respectively.

  FIG. 21 includes recesses 74, 75, 76, 77 having openings equal to or larger than the seal ring width on the tip surface of the turning boss, and the center position of the recess is the center of the frame with respect to the turning center Om. This is an embodiment set inside or outside the center diameter (generally D1 dimension) of the annular seal ring 34a fitted in the annular groove 33 on the end face of the part. 22 and 23 are partial cross-sectional views showing the positional relationship between the radial grooves 77 set on the inner side and the seal ring 34a. Thus, by setting the said recessed part to the position eccentric with respect to center diameter D1, D2 of the sliding contact range W2, those recessed parts 74,75,76,77 turn the turning boss part of a turning scroll. With the circular motion, the oil in the hydraulic chamber 41 around the main shaft accumulates in the recess and is intermittently discharged from the state shown in FIG. 22 to the back pressure chamber 36 in the state shown in FIG. 23 across the seal ring 34a. It will be oiled. In this case, the amount of oil increases because of the oil leakage characteristics due to the differential pressure. With this configuration, the hydraulic chamber and the back pressure chamber around the main shaft are intermittently communicated with each other through the recess. Further, as the amount of eccentricity with the circle 79 having the center diameters D1 and D2 increases, the communication period between the two chambers becomes shorter, and as a result, the amount of oil leakage can be adjusted.

  24 and 25 show an embodiment in which dimple-shaped fine holes 82 (82a, 82b) are provided in the tip surface 6n of the orbiting boss portion having the orbiting scroll bearing portion as another oil leakage structure. The maximum diameter of the hole 82 is about 0.2 to 0.5 mm. The dimple-shaped micro holes 82h may be provided on the entire peripheral surface of the tip surface of the turning boss portion, or may be limited to a certain angle range θs as shown in FIG. The diameter d5 of the dimple-shaped micro holes 82 may be scattered with a value of 1 mm or less. The dimple-like micropore structure has an effect of softening deformation of the sliding surface of the resin seal ring and preventing damage such as small scratches, and has an effect of extending the life of the resin seal ring.

  FIG. 28 shows an embodiment in which the present invention is applied to a horizontal scroll compressor 300. The member numbers shown in FIG. 28 that are the same as the member numbers shown in FIGS. 1 to 27 have the same functions as those described above. A sealing member 34 that seals the high-pressure hydraulic chamber 41a and the low-pressure chamber 36c (inlet pressure atmosphere chamber) is formed on the frame base portion 97f of the stationary member facing the end plate rear surface portion 200a of the orbiting scroll 6, and the orbiting scroll. 6 is provided at a position within a distance range of a size before and after the turning radius εth with respect to the radial direction of the position of the seal ring 34a of the seal portion 34, the width L1 of the seal ring 34a of the seal portion 34 Holes 58p and 58r having a hole diameter d1 that is equal to or smaller than that are provided. In FIG. 28, as the orbiting scroll 6 having the hole 58p orbits, the oil in the hydraulic chamber 41 enters and fills the hole 58p, whereas the position opposite to the hole 58p is 180 degrees. The hole 58r located in the hole serves to discharge the oil, and the discharged oil moves to the thrust sliding portion 92 and further to the Oldham sliding portion 38 located on the outer peripheral portion, and is used for lubrication. In addition, 95a is an oil reservoir part of the discharge chamber 1a, and 95b is an oil reservoir part of the electric motor chamber 1b. Both oil reservoirs are connected by an oil passage 96. The hydraulic chamber 41a communicates as an oil supply path (not shown) through the bearing gap between the oil supply hole 95b and the oil supply hole 13 and the bearing portion 32.

  According to the above embodiment, the high-temperature oil leakage action from the side space seen in the conventional machine to the suction chamber 5f can be suppressed to a very small amount, so that the internal heating amount of the suction gas in the suction chamber can be greatly reduced. . For this reason, the overall heat insulation efficiency can be greatly improved by improving the volumetric efficiency and reducing the stirring loss by reducing the internal heating amount of the suction gas. In addition, this effect and action are remarkable in high pressure ratio operation conditions in which the amount of bearing oil increases and the amount of internal heating of the suction gas increases as compared with the conventional machine using the differential pressure oil supply method.

  The embodiment of the present invention described above has the following effects.

  (1) By optimizing the amount of oil flowing from the high pressure hydraulic chamber 41 into the back pressure chamber 36, the amount of oil flowing out of the bearing gap with respect to the conventional machine is greatly increased into the back pressure chamber 36. In order to reduce, the oil accumulation phenomenon of the space 36 is avoided. Since oil is injected into the compression chamber through the pores provided in the end plate of the orbiting scroll, the oil discharge action goes smoothly and the unstable phenomenon that the intermediate pressure of the conventional machine fluctuates is avoided. . In addition, if the amount of oil is small, stirring loss does not occur.

  (2) Since a small amount of the oil is always secured regardless of the differential pressure, the oil shortage phenomenon of the sliding portion between the back pressure chamber and the Oldham chamber is avoided. In other words, the small amount of oil moves from the back pressure chamber to the Oldham chamber 51 and is used for oil lubrication in the Oldham sliding portion, and oil accumulates in the Oldham key groove, and lubrication in the peripheral portion is surely performed. Therefore, the sliding performance at that portion is improved and the sliding loss is reduced.

  (3) In the above cited example, the passage area of the throttle portion needs to be set very small, and the oil leakage amount characteristic has a problem (problem) that causes a large variation in the oil leakage amount. However, in the present invention, since the oil amount is always constant regardless of the differential pressure, the performance variation is small. For this reason, product quality becomes high.

  (4) Along with the effects of the above items, the performance and reliability of the compressor can be greatly improved by improving the sealing performance with oil, and the power consumption of the air conditioner can be greatly reduced throughout the year.

  (5) The noise of the compressor and the amount of oil to the compression chamber can be suppressed, so that the amount of oil can be reduced and the quality and reliability of the compressor can be improved.

Sectional drawing which shows one Embodiment which provided the seal | sticker part in the frame base part of the scroll compressor which concerns on this invention, and installed the hole for oil transfer in the turning scroll end plate back part. Sectional drawing which shows the state which the turning scroll shown in FIG. 1 turned 180 degree | times. Sectional drawing which shows other embodiment which provided the seal | sticker part in the back panel part of the turning scroll of the scroll compressor which concerns on this invention, and installed the hole for oil transfer in the frame base part. Sectional drawing which shows the state which the turning scroll shown in FIG. 3 turned 180 degree | times. The longitudinal cross-sectional view which shows the whole structure of other embodiment of the scroll compressor based on this invention. The fragmentary sectional view of the compressor part of one embodiment which incorporated the seal member in the frame of the scroll compressor concerning the present invention. The fragmentary longitudinal cross-sectional view of the Oldham chamber vicinity of other embodiment of the scroll compressor which concerns on this invention. The top view which shows the turning scroll in other embodiment of the scroll compressor which concerns on this invention. A-Om-A sectional drawing of FIG. The top view of the seal ring in other embodiments of the scroll compressor concerning the present invention. MM sectional drawing of FIG. The perspective view of the butting | matching part of the seal ring shown in FIG. The fragmentary sectional view which shows the positional relationship of the seal ring and small hole in other embodiment of the scroll compressor which concerns on this invention. The figure which shows the state which the turning scroll turned 180 degree | times in other embodiment of the scroll compressor based on this invention. The top view which shows the positional relationship of the seal ring and small hole in other embodiment of the scroll compressor which concerns on this invention. The top view of the flame | frame in other embodiment of the scroll compressor which concerns on this invention. The top view of the Oldham ring in other embodiments of the scroll compressor concerning the present invention. The top view of the turning boss in other embodiments of the scroll compressor concerning the present invention. The figure which shows one example of the cross-sectional shape of the recessed part in other embodiment of the scroll compressor which concerns on this invention. The figure which shows the other example of the cross-sectional shape of the recessed part in other embodiment of the scroll compressor which concerns on this invention. The fragmentary top view of the turning boss in further another embodiment of the scroll compressor concerning the present invention. The fragmentary sectional view showing the positional relationship of the groove | channel provided in the turning boss | hub part of the scroll compressor shown in FIG. 21, and a seal ring. The fragmentary sectional view showing the positional relationship of a groove | channel and a seal ring when a turning scroll turns 180 degrees from the state of FIG. The fragmentary top view of the turning boss in further another embodiment of the scroll compressor concerning the present invention. The fragmentary sectional view of the dent part in FIG. The figure for demonstrating the effect on the efficiency and noise level in this invention. The figure for demonstrating the effect regarding the back pressure chamber oil amount in this invention. The figure which shows embodiment which applied this invention to the horizontal scroll compressor.

Explanation of symbols

2 ... Sealed container 5 ... Fixed scroll 5a, 6a ... Scroll end plate part 6 ... Orbiting scroll 11 ... Frame 14 ... Main shaft (crankshaft)
14a ... Eccentric shaft portion 18 ... Communication passage 34 ... Sealing means 36 ... Back pressure chamber 38 ... Oldham mechanism portion 40 ... Main bearing 41 ... High pressure chamber 51 ... Oldham chamber 58 ... Small hole 72 ... Recessed portion 74, 75, 76, 77 ... Depression part 200 ... Swivel scroll 202 ... Pedestal part 205 ... Hole 215 ... High pressure chamber 216 ... Low pressure chamber 220 ... Seal part 220a ... Seal ring εth ... Swivel radius

Claims (2)

In a scroll compressor provided with a fixed scroll and a turning scroll formed by standing a spiral wrap upright on a disc-shaped end plate, and a stationary frame provided to face the back side of the turning scroll,
By providing a seal part between the rear side of the orbiting scroll and the frame, the orbiting scroll is provided with a high-pressure hydraulic chamber formed inside and a low-pressure chamber formed outside the seal part. A scroll compressor comprising an oil supply passage that communicates the high-pressure hydraulic chamber and the low-pressure chamber intermittently by movement. A scroll compressor according to the present invention includes a fixed scroll and a orbiting scroll formed by erecting a spiral wrap on a disc-shaped end plate, and a stationary frame provided to face the back side of the orbiting scroll. In the scroll compressor
A sealing means provided on a pedestal portion of the frame, which is a stationary member facing the orbiting scroll, and partitioned intermittently by a high-pressure hydraulic chamber and a low-pressure chamber, and the orbiting scroll and the sealing means. A scroll compressor characterized in that a high-pressure hydraulic chamber and an oil supply passage communicating the low-pressure chamber are provided so that oil in the high-pressure hydraulic chamber flows intermittently into the low-pressure chamber.

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