JP2005076545A - Scroll compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a section shape solving a problem wherein rising performance is deteriorated when force in a twisting direction acts on a tip seal and an edge part interferes with a tip seal groove wall surface since a tip seal section surface is U-shaped. <P>SOLUTION: A section of the tip seal 244 has a shape including a chamfered recess part 286 on an anti-seal surface outer side in a section of roughly half winding from a winding completion end 285 of a turning scroll 213 to a winding start side. Since the tip seal stably rises, the highly efficient scroll compressor of high sealing performance can be materialized. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a tip seal of a scroll compressor used for an air conditioner or the like.

  Hereinafter, an oil supply system to the compressor mechanism of a conventional scroll compressor and the function of the tip seal will be described with reference to the drawings.

FIG. 6 is a longitudinal sectional view of a conventional scroll compressor, and FIG. 7 is a partial sectional view of the compression mechanism. The compression mechanism is disposed inside a sealed container 201 having a discharge pressure atmosphere having an oil reservoir 207 for storing lubricating oil at the bottom. The stator 203a of the electric motor that drives this is fixed, the crankshaft 206 that drives the compression mechanism is coupled to the rotor 203b of the electric motor, and the periphery of the compression mechanism of the sealed container 201 is an oil reservoir 207.

  The compression mechanism includes a fixed scroll 210, a turning scroll 213 that meshes with the fixed scroll 210 to form a plurality of compression chambers 214, a rotation restraining component 215 that prevents the turning of the turning scroll 213 and makes only turning, An orbiting drive shaft 222 provided on the opposite side of the orbiting scroll 213, an eccentric bearing 223 provided inside the main shaft 218 of the crankshaft 206 and fitted with the orbiting drive shaft 222, and a main shaft 218 of the crankshaft 206. A bearing part 221 having an axial movement limiting flat surface portion 226 for limiting the axial movement of the orbiting scroll 213 is disposed with a small gap from the main bearing 219 to be supported and the back of the end plate 224 behind the orbiting scroll 213. To do. A sliding partition ring 225 that partitions the gas pressure applied to the end plate back surface 224 into a discharge pressure applied to the central portion and a pressure lower than the discharge pressure applied to the outer periphery of the end plate back surface 224 is disposed on the axial movement limiting flat surface portion 226. . The back pressure chamber 245 formed in the space outside the sliding partition ring 225 is located at the center of the orbiting scroll end plate back surface 224 via the first communication passage 241 having the throttle mechanism 246 provided inside the orbiting scroll end plate 213. It is the structure which communicates with the space 249 where the discharge pressure of a part acts.

  Further, a second communication passage 248 formed in the inside of the orbiting scroll end plate 227 and communicating with the tip seal storage groove 251 is branched from the middle of the first communication passage 241 communicating with the back pressure chamber 245. The throttle mechanism 246 is provided in the downstream first communication passage.

  Further, the crankshaft 206 is also provided with an oil supply passage 243 penetrating the crankshaft 206. An end surface of the oil supply passage 243 on the side opposite to the compression mechanism is an oil reservoir 207 via an oil pump 242, and an end surface on the compression mechanism side is an orbiting scroll end plate. It is configured to communicate with a space 249 in which the discharge pressure at the center of the back surface 224 acts.

  With this configuration, the lubricating oil guided from the oil reservoir 207 to the space 249 in which the discharge pressure at the center of the orbiting scroll end plate back 224 acts by the oil pump 242 or the like is throttled from the first communication passage 241. An appropriate amount is supplied to the outermost compression chamber via the mechanism 246 and is formed in the clearance on the back surface of the chip seal storage groove 251 and the chip seal 244 from the second communication path 248 branched from the first communication path 241. By being sufficiently supplied to the space, the leakage path to the low pressure side formed in the longitudinal direction of the tip seal storage groove 251 is blocked, and the compression chamber is formed by the lubricating oil overflowing from the tip seal storage groove 251. It was the oil supply composition which also supplies to the wall surface.

Further, as shown in FIG. 5, the tip seal 244 is formed with an appropriate length in the longitudinal direction shorter than the tip seal storage groove 251, and a gap 270 is formed at the winding start end to form the tip seal storage groove 251. Since the swivel scroll 213 is swung, the swivel movement of the orbiting scroll 213 causes the discharge pressure to be introduced to the back surface of the tip seal 244 when the winding start end clearance 270 communicates with the discharge hole 260, and is pressed against the bottom surface of the fixed scroll 210. The leakage passage to the lower pressure compression chamber formed outside across the tip seal 244 is blocked.
JP 2000-213477 A

  However, in the above-described conventional configuration, the tip is reduced due to a pressure drop due to passage resistance in the downstream portion (winding end portion or suction side) more than half a turn from the opening end 252 of the discharge hole 260 and the second communication passage 248 on the tip seal storage groove side. Since the ability to float the seal 244 is reduced and the compression chamber 281 on the outer side of the chip seal has a higher pressure (see FIG. 4) than the inner compression chamber 282, the chip seal 244 is placed in the chip seal storage groove. As a result of being twisted and pressed against the inner and outer walls of 251, the end of winding of the tip seal 244 is caught and the floating becomes insufficient, and the tip seal 244 crosses the tip seal 244 and leaks into the compression chamber on the lower pressure side, resulting in reduced performance. Had problems.

  As a measure for improving this, there is a case where the position of the open end 252 of the second communication passage 248 is installed on the winding end side. In this case, the pressure difference between both ends of the second communication passage 248 becomes large. Since the high-pressure and high-temperature lubricating oil excessively leaks into the compression chambers 281 and 282 near the suction chamber via the tip seal storage groove 251, there is a problem that the performance is also deteriorated due to the overheat loss of the suction refrigerant. It was.

  The present invention solves such conventional problems, and an object thereof is to provide higher performance as a compressor.

In order to solve the above problems, the present invention has a chip seal cross-sectional shape in which a chamfered relief portion is provided on the outer side of the anti-seal surface of the chip seal that is installed in an approximately half-winding section from the winding scroll end to the winding start side. To do.

  By making the tip seal cross-sectional shape as described above, it is possible to provide a scroll compressor that improves the floatability of the tip seal and ensures higher performance.

  According to the present invention, the chip seal floatability is deteriorated due to the passage resistance loss due to being away from the discharge hole, and the tip seal is twisted on both side walls of the chip seal storage groove due to the pressure difference of the compression chamber adjacent to the chip seal. Even at the point on the almost half-winding start side from the end of the orbiting scroll that is pressed in a closed state, the tip seal can be easily lifted without being caught by the tip seal storage groove wall surface by the chamfered relief portion of the tip seal. Can do.

  Further, the lubricating oil is guided to a gap formed between the chamfered relief portion of the chip seal and the bottom surface of the chip seal storage groove, and the reaction force when the lubricating oil moves to the end side of the chip seal winding causes the chip The seal is pressed against the side wall surface of the chip seal storage groove and the bottom surface of the fixed scroll, and the sealing performance in the direction across the chip seal is maintained even at the end of the winding. Furthermore, since this action is continuously performed, there is also an effect that a path leaking from the high pressure side to the low pressure side can be blocked along the tip seal housing groove.

  As a result, it is possible to provide a scroll compressor in which the tip seal floats stably and higher performance is ensured.

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

  6 and 7 (FIG. 3), a compression mechanism and a stator 203a of an electric motor that drives the compression mechanism are fixed inside a sealed container 201 having a discharge pressure atmosphere having an oil reservoir 207 that accumulates lubricating oil at the bottom, and the electric motor A crankshaft 206 that drives the compression mechanism is coupled to the rotor 203b, and an oil reservoir 207 is formed around the compression mechanism of the sealed container 201.

  The compression mechanism includes a fixed scroll 210, a turning scroll 213 that meshes with the fixed scroll 210 to form a plurality of compression chambers 214, a rotation restraining component 215 that prevents the turning of the turning scroll 213 and makes only turning, An orbiting drive shaft 222 provided on the opposite side of the orbiting scroll 213, an eccentric bearing 223 provided inside the main shaft 218 of the crankshaft 206 and fitted with the orbiting drive shaft 222, and a main shaft 218 of the crankshaft 206. A bearing part 221 having an axial movement limiting flat surface portion 226 for limiting the axial movement of the orbiting scroll 213 is disposed with a small gap from the main bearing 219 to be supported and the back of the end plate 224 behind the orbiting scroll 213. To do. A sliding partition ring 225 that partitions the gas pressure applied to the end plate back surface 224 into a discharge pressure applied to the central portion and a pressure lower than the discharge pressure applied to the outer periphery of the end plate back surface 224 is disposed on the axial movement limiting flat surface portion 226. . The back pressure chamber 245 formed in the space outside the sliding partition ring 225 has a discharge pressure at the center of the orbiting scroll end plate back surface 224 via the first communication passage 241 provided inside the orbiting scroll end plate 213. It is configured to communicate with the acting space 249.

  Further, the second communication passage 248 formed in the inside of the orbiting scroll end plate 227 and communicating with the tip seal storage groove 251 is branched from the middle of the first communication passage 241 communicating with the back pressure chamber 245.

  Further, the crankshaft 206 is also provided with an oil supply passage 243 penetrating the crankshaft 206. An end surface of the oil supply passage 243 on the side opposite to the compression mechanism is an oil reservoir 207 via an oil pump 242, and an end surface on the compression mechanism side is an orbiting scroll end plate. It is configured to communicate with a space 249 in which the discharge pressure at the center of the back surface 224 acts.

  With this configuration, the lubricating oil guided from the oil reservoir 207 to the space 249 in which the discharge pressure at the center of the orbiting scroll end plate back 224 acts by the oil pump 242 or the like is throttled from the first communication passage 241. An appropriate amount is supplied to the outermost peripheral compression chamber via the mechanism 246 and the like, and is formed in the clearance on the back surface of the chip seal storage groove 251 and the chip seal 244 from the second communication path 248 branched from the first communication path 241. Is sufficiently supplied to the space where the chip seal storage groove 251 is formed, so that the leakage path to the low pressure side formed in the longitudinal direction of the chip seal storage groove 251 is blocked and the compression chamber is formed by the lubricating oil overflowing from the chip seal storage groove 251. The oil supply structure also supplies to the wall surface.

  Further, as shown in FIG. 5, the tip seal 244 is formed to have an appropriate length shorter in the longitudinal direction than the tip seal storage groove 251 and an appropriate amount of clearance 270 is formed at the winding start end. Since the swivel motion of the orbiting scroll 213 causes the winding start end clearance 270 to communicate with the discharge hole 260, the discharge pressure is introduced into the back surface of the chip seal 244 and is pressed against the bottom surface of the fixed scroll 210. The leak passage to the lower pressure compression chamber formed outside across the seal 244 is blocked.

  Further, as shown in FIGS. 1 and 2, the tip seal 244 assembled in the tip seal storage groove 251 has a chamfered portion on the outer side of the anti-seal surface in the approximately half-winding section from the turning scroll winding end 285 to the winding start side. The cross-sectional shape 292 is provided with the escape portion 286.

  By adopting the above-described chip seal cross-sectional shape, the chip seal floating performance is deteriorated due to passage resistance loss caused by being away from the discharge hole 260, and the pressure difference between the compression chambers 281 (282) adjacent to the chip seal 244 is reduced. Chamfered relief of the tip seal 244 also at the point (see FIG. 1) on the almost half winding start side from the turning scroll winding end 285 where the tip seal 244 is pressed in a state of being twisted to both side walls of the tip seal storage groove 251. By the portion 286, the chip seal 244 can be easily lifted without being caught on the wall surface of the chip seal storage groove 251.

  Further, the lubricating oil is guided to a gap formed between the chamfered relief portion 286 of the chip seal 244 and the bottom surface 254 of the chip seal storage groove 251, and the reaction when the lubricating oil moves toward the end of the chip seal winding. The chip seal 244 is pressed against the side wall surface of the chip seal storage groove 251 and the bottom surface 255 of the fixed scroll 210 by the force, and the sealing performance in the cross direction of the chip seal is maintained even at the end of winding. By continuously performing this action, it is possible to simultaneously block a path that leaks from the high pressure side to the low pressure side along the tip seal housing groove 251.

  As a result, it is possible to provide a scroll compressor in which the tip seal floats stably and higher performance is ensured.

  As described above, the scroll compressor according to the present invention can make the tip seal easily float without being caught by the tip seal storage groove wall surface by the chamfered relief portion of the tip seal. However, since the sealing performance in the cross direction of the tip seal is maintained and this action is continuously performed, there is also an effect that the path leaking from the high pressure side to the low pressure side can be cut off at the same time along the tip seal storage groove. Since it becomes possible to provide a highly efficient scroll compressor with high sealing performance, it can be applied to applications such as air conditioners and other refrigeration equipment.

The perspective view which shows the relative position relationship between the tip seal cross-sectional shape of the present invention and the orbiting scroll Enlarged view of the tip seal of the present invention viewed from the orbiting scroll side Enlarged sectional view of the compression mechanism of a conventional scroll compressor The figure explaining the timing when the compression chamber outside the tip seal becomes higher in pressure than the inner compression chamber Partial enlarged sectional view of the winding start portion of the scroll compression mechanism Longitudinal sectional view of a conventional scroll compressor Enlarged longitudinal sectional view of a compression mechanism of a conventional scroll compressor

Explanation of symbols

DESCRIPTION OF SYMBOLS 201 Airtight container 202 Compression mechanism 203a, 203b Electric motor 206 Crankshaft 207 Oil reservoir 210 Fixed scroll 213 Orbiting scroll 214 Compression chamber 215 Rotation restraint component 218 Main shaft 219 Main bearing 221 Bearing component 222 Orbit drive shaft 223 Eccentric bearing 225 Sliding partition ring 241 First communication passage 242 Oil pump 244 Tip seal 245 Back pressure chamber 248 Second communication passage 251 Tip seal storage groove 252 Open end of second communication passage 253 Branch portion of communication passage 254 Tip seal storage groove bottom surface 255 Fixed Scroll bottom surface 260 Discharge hole 270 Tip seal winding start gap 281 Outermost peripheral compression chamber 282 outside the tip seal 282 Outermost peripheral compression chamber 285 inside the tip seal 285 End of orbiting scroll winding 286 Tip seal chamfer 292 Tip Lumpur sectional shape

Claims (1)

There is an oil reservoir for storing lubricating oil at the bottom, an internal motive of a sealed container on which discharge pressure acts, and a compression mechanism driven by this electric motor are arranged, and the compression mechanism is engaged with the fixed scroll and the fixed scroll. A rotating scroll that forms a single compression chamber, a rotation restraining part that prevents the rotating scroll from rotating and only rotates, a crank shaft that drives the rotating scroll to rotate, and a main shaft formed on the crank shaft are supported. An orbiting drive mechanism configured to include a bearing part having a main bearing and engaged with an eccentric drive engaging portion provided on the crankshaft on the back surface of the end plate on the side opposite to the orbiting of the orbiting scroll to rotate the orbiting scroll. A joint portion is provided, and the pressure acting on the back surface of the end plate on the outer side of the turning drive engagement portion acts on the discharge pressure acting on the center portion of the back surface of the end plate and the outer periphery of the back surface of the end plate. A sliding partition ring that divides the pressure into a pressure lower than the discharge pressure is disposed, and high-pressure lubricating oil is supplied from the oil reservoir to the center of the back of the end plate, and the outer side of the center of the back of the end plate and the sliding partition ring The back pressure chamber formed in the space is communicated with a first communication passage formed inside the end plate of the orbiting scroll, and is branched from the middle of the first communication passage, and is connected to a lap tip of the orbiting scroll. The tip seal installed in an approximately half-turn section from the end of the orbiting scroll to the beginning of winding, the second connecting passage communicating with the bottom surface of the tip seal storing groove for storing the provided tip seal A scroll compressor having a tip seal cross-sectional shape in which a chamfered relief portion is provided on the outer side of the anti-seal surface.

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