JPH03202682A - Gas compressor - Google Patents

Abstract

PURPOSE:To downsize an compressor by storing and fixing a compressor mechanism part and a motor in sealed containers respectively, by supporting them with an auxiliary bearing member and the compressor mechanism part, and by fixing the auxiliary bearing member at an end part of a stator made of laminated plates of the motor in the thin state through high density energy welding. CONSTITUTION:A space on the side where a motor 3 is arranged is constituted by an oil separating chamber 128 on the upper side and a motor chamber 6 on the lower side, divided by an upper bearing 126 fixed in the state of a thin bead 7 through high density energy welding, represented by electron beam welding or laser welding, without giving heat distortion to junction members on the upper end surface of a stator 3b of the motor 3 in which laminated thin sheet steels are fixed by rivet. The stator 3b fixed on the upper bearing 126 is shrinkage fixed to a sealed container 1, and a clearance 136 is provided between the outer circumference on the end part of the stator and the sealed container 1 so that shrinkage distortion would not occur at the end part of the stator 3b.

Description

[Detailed Description of the Invention] Industrial Application Field of the Invention 1 Mainly The installation of the bearing that supports the drive shaft across the electric motor of the gas compressor is related to the structure and oil supply to the bearing, but it is different from the conventional one. Technical scroll compressor (Yo) The suction chamber is located on the outer periphery, and the discharge boat is provided at the center of the volute.The compressed fluid is sucked and compressed in a symmetrical volute-shaped compression space with the discharge boat at the center, and the compressed fluid flows in one direction. It is generally known that fluctuations in compression torque are smaller than reciprocating compressors and rotary compressors, and vibration and noise are also extremely low. The general structure of the discharge boat is also well known as shown in FIG. Rolling bearing 106 provided in frame 1060
1 and a sliding bearing 1062
The crank part 1059 at the upper end is a fixed scroll 1o5
an orbiting scroll 105 that meshes with 1 to form a compression chamber;
A bearing coupling mechanism that engages with the sliding bearing 1057 of No. 2 to rotate the orbiting scroll 1° 52 is provided.
A so-called cantilever bearing structure type in which a bearing is placed only on one side of the sealed container 1050.The lubricating oil at the bottom of the sealed container 1050 is transferred to the sliding bearing 1057 at the top. Rolling bearing 1081. Eccentric oil supply hole 106 provided in drive shaft 1058 to sliding bearing 1062
8, 1069 using the centrifugal pump action and differential pressure, as well as rolling bearing 1061 and drive shaft 1058
Drive shaft 1058 within the bearing gap by reducing the gap between the
Reduce the inclination angle of sliding bearings 1057.1082
This structure is devised to improve the durability of the bearing sliding part by reducing uneven contact (Japanese Patent Application Laid-Open No. 115488/1988). However, in the above configuration, during high-speed operation of the compressor, the tip of the drive I 1058 on the motor side may tilt (run out) of the drive shaft 1058 within the bearing clearance, and the drive shaft 10
centrifugal force of the rotor of the electric motor section 1063 attached to the tip of the drive shaft 1058, and electromagnetic force caused by the uneven air gap between the rotor fixed to the drive shaft 1058 and the stator fixed to the sealed container 1050. As a result, rolling bearings 1061. Slide bearing 1
062.1057 causes uneven contact, which significantly reduces bearing durability and impairs the low vibration and low noise characteristics that characterize scroll compressors. -125386, JP-A-62-113881, JP-A-62-1
No. 26282, JP-A-62-126285,
Although there have been proposals to support the drive shaft on both sides of the motor, such as in Japanese Unexamined Patent Publication No. 62-135676, these proposals have the problem of increasing the external size of the compressor and causing misalignment between the two bearings. Problem 1: Excessive human power loss in bearings
In order to avoid excessive manual labor, there were various problems such as vibration and noise caused by increasing the bearing gap.Also, as a means to solve the above problems, the configuration shown in FIG. 17 is also known. A main bearing part 2010 of a rolling bearing is provided in a frame 2008 which has a scroll compressor 2004 in the upper part, an electric motor part 2002 in the lower part, and an oil reservoir 2006 in the bottom part, and is statically connected to the fixed scroll 2014 and the closed container 2001. , electric motor section 2
002 stator 2011 and the cylindrical case 2003 of the sealed container 2001, the rolling bearing (ball bearing... can tolerate some axial inclination) 2035 is installed in the auxiliary bearing part 2030. The water that supports the drive shaft 2009 is a so-called double-end supported rolling bearing configuration, which prevents twisting due to misalignment between the two bearings. Problems to be solved by the present invention with a configuration in which lubricating oil is supplied to the sliding portion of the bearing. There is a problem that the vibration of the piping system connected to the compressor and the noise caused by it increase due to direct propagation, and the difference between the vibration and noise in the cantilever bearing configuration is small and no significant effect is produced. A rolling bearing (ball bearing) 2035 is used as the bearing of the bearing part 2030. Δ Collision caused by the ball jumping phenomenon that occurs when the balls roll on the bearing raceway due to imperfect roundness of the raceway. There is a problem in that noise and vibration propagate to the closed container 2001, impairing the quiet operating characteristics of the scroll compressor. When used with the negative pressure line section and the motor section upside down, there was a problem in which it was difficult to supply oil to the bearing sliding section on the side far from the compression chamber. Publication No. 52-157510, Utility Model No. 5
As described in Publication No. 5-137279, in a horizontal rotary gas compressor in which the drive shaft connected to the electric motor is supported by a bearing placed only on one side of the electric motor section, discharged gas containing lubricating oil is transferred to the drive shaft. There is a known method in which the lubricating oil is separated by the inertial force of the lubricating oil in the discharged gas, and the lubricating oil is separated by the inertial force of the lubricating oil in the discharged gas, and the centrifugal force is used to replenish the bearing near the compression part. A method of supplying oil to the bearing part on the side far from the compression chamber by applying this type of oil supply means when a gas compressor with a bearing configuration supported at both ends as shown in Fig. 17 is installed horizontally, and when the gas compressor is placed upside down. The lubricating oil separated from the discharged gas may pass through the passage or be dispersed, resulting in a low lubricating oil recovery rate, making it impossible to supply sufficient lubricant, and the separated lubricating oil may mix with the discharged gas again. There is a problem that the lubricating oil may leak outside the compressor and cause a shortage of lubricating oil. The end of the discharge pipe leading to the external piping system of the compressor is placed near the center of the end, and the lubricating oil is dispersed around the outer circumference of the motor by centrifugal diffusion of the airflow when the rotor rotates. JP-A-55-1 has a structure that prevents lubricating oil from flowing into the discharge pipe.
9920, and applying this means to a compressor with a bearing structure supported at both ends has the problem that bearing oil supply is difficult and impossible to realize.The present invention ζ has been developed to solve the above problem. The purpose of the bearing installation is to provide a structure that prevents the vibration of the bearing that supports the drive shaft on the side away from the compressor from propagating directly to the closed container, and to achieve quiet operation and miniaturization of the compressor. In addition, according to the present invention, an independent oil supply system is provided that can supply lubricating oil to a bearing part located away from an oil sump without introducing lubricating oil from the oil sump at the bottom of the compressor. Although the present invention is intended to simplify parts, the present invention also provides a method for capturing lubricating oil for supplying lubricating oil to a bearing section located away from an oil sump and preventing the collected lubricating oil from scattering. However, the present invention also has the object of isolating the flow path of the discharged gas from the destination of the lubricating oil supplied to the bearing to prevent the lubricating oil from leaking to the outside of the compressor. Another object of the present invention is to provide a discharge gas passage that prevents the lubricating oil separated from the discharged gas from being mixed into the discharged gas again, and to improve the durability of sliding parts by securing the lubricating oil of the compressor. Invention ζ The lubricating oil separated from the discharged gas is used in the motor (
The purpose is to prevent the diffusion effect caused by the rotation of the rotor of an electric motor and the resulting re-mixing of lubricating oil into the discharged gas, and to prevent an increase in input when the rotor diffuses lubricating oil. The purpose of the invention is to provide an oil supply passage that does not require a large space for storing lubricating oil inside a compressor, thereby reducing the size of the compressor. Although the purpose is to downsize the machine and improve compression efficiency, the present invention ζ forms multiple oil supply paths to increase the amount of oil supplied to the bearing of the compression mechanism, thereby improving the durability of the bearing. The present invention aims at reducing input loss and is a means for solving the problem.In order to solve the above problem (the purpose is a distant relative), the present invention provides the following: A drive shaft is provided on the side of the reaction pressure mechanism of the electric motor. The motor is supported by a sub-bearing member and a compression mechanism part, and the sub-bearing member is fixed in a thin bead shape by high-density energy welding to the end of the stator cut out from the laminated plate of the motor without contacting the sealed container. The present invention also includes a drive shaft supported by a sub-bearing member provided on the side of the reaction pressure mechanism section of the electric motor and a compression mechanism section, and a discharged gas that does not pass through the motor chamber housing the electric motor is transferred between the sub-bearing member and the airtight container. The present invention also includes means for introducing the discharged gas into the oil separation space formed by the end wall and releasing the discharged gas toward an oil receiver provided near the bearing of the auxiliary bearing member and open to the bearing. (1) An oil separation element is arranged between the discharge gas introduction opening into the oil separation space and the oil reservoir of the oil pan. The drive shaft connected to the fixed Lt electric motor is supported by the sub-bearing member provided on the side of the counter-pressure mechanism part of the motor and the compression mechanism part. The discharged gas is introduced into the oil separation chamber formed by the sub-bearing member's bearing, and the discharged gas is discharged toward an oil receiver that is provided near the bearing of the sub-bearing member and opens to the bearing. An oil groove is provided on the outer periphery of the shaft that leads to the oil sump in the oil pan, and the pumping action of the oil groove is used to drain the lubricating oil from the oil sump to the compression mechanism side of the motor room, leading to the outside of the compressor. The discharge side opening may be provided on the side opposite to the compression mechanism part of the motor room. An oil separation chamber is provided that leads to the oil sump at the bottom of the motor room.
The discharge gas that does not pass through the motor room is introduced into the upper part of the oil separation chamber, and the opening of the discharge pipe leading to the outside of the compressor is arranged in the space between the end of the motor rotor and the partition member. It is placed close to the end of the rotor. Also
The present invention stores and fixes a compression mechanism part and an electric motor in a sealed container, and a partition member is disposed between the side of the motor opposite to the compression mechanism part and the end of the sealed container, and the bottom part of the motor room in which the electric motor is housed is provided. An oil separation chamber leading to the oil sump is installed, and the discharge gas that does not pass through the motor room is introduced into the upper part of the oil separation chamber. The opening of the communicating discharge pipe is arranged and the opening is brought close to the end of the rotor, and the drive shaft connected to the electric motor is supported by a sub-bearing member provided on the side of the counter-pressure mechanism of the electric motor and the compression mechanism. The auxiliary bearing member also serves as a partition member. The discharged gas that does not pass through is introduced into the oil separation chamber formed by the sub-bearing member and the end wall of the sealed container, and the discharged gas is discharged toward the oil receiver that communicates with the bearing of the sub-bearing member, thereby removing the lubricating oil in the oil receiver. The drive shaft is provided with an oil passage that leads the oil to the bearing of the auxiliary bearing member and the bearing of the compression mechanism, and the oil is supplied to the bearing of the compression mechanism. The drive shaft, which is housed and fixed inside and connected to the electric motor, is supported by the sub-bearing member provided on the side of the counter-pressure mechanism part of the motor and the compression mechanism part. The discharged gas is introduced into the oil separation chamber formed by the end wall of the sealed container, and the discharged gas is released toward the oil receiver provided near the bearing of the sub-bearing member and open to the bearing.
The lubricating oil in the oil pan is supplied to the bearing of the sub-bearing member that supports the drive shaft and the bearing of the compression mechanism, and the lubricating oil supplied to the bearing of the compression mechanism is injected into the compression chamber. t
, - According to the present invention ζ, a compression mechanism section and an electric motor are housed and fixed in a closed container, and a drive shaft connected to the electric motor is supported by an auxiliary bearing member provided on the side of the counterpressure mechanism section of the electric motor and the compression mechanism section.
The discharged gas that does not pass through the motor chamber that houses the electric motor is introduced into the oil separation chamber formed by the sub-bearing member and the end wall of the sealed container, and the oil that is provided near the bearing of the sub-bearing member and is open to the bearing. The discharged gas is released toward the receiver, and the lubricating oil in the oil receiver is supplied to the bearing of the sub-bearing member that supports the drive shaft and the bearing of the compression mechanism, thereby lubricating the oil sump at the bottom of the motor chamber where the discharge pressure acts. The oil is mixed and supplied to the bearing part of the compression mechanism part, and the effect is as follows. The vibration is attenuated by the thin joints between the laminate and the laminate, and is also attenuated by slight slippage between the laminated plates, so it does not propagate to the sealed container, reducing vibrations on the walls of the sealed container and in the external piping system connected to the sealed container. Mat 2
A welding table that uses high-density energy can weld a small electric motor and a sub-bearing member without causing damage to the stator windings or thermal distortion to the laminated plates. When the discharged gas that does not pass through a chamber and does not separate the lubricating oil changes its flow direction in the oil separation chamber, the lubricating oil in the discharged gas is separated from the discharged gas by its inertial force. The oil film collected directly into the bearing of the secondary bearing member lubricates the sliding surface and alleviates collisions between the drive shaft and the sliding surface, reducing vibration and noise generation. According to the invention, the discharged gas flowing into the oil separation chamber collides with the oil separation element. At that time, the lubricating oil is captured and collected in the oil sump placed below the oil sump. The lubricating oil in the oil sump protects the oil separation element. As a result, scattering due to discharged gas is prevented.Also, according to the present invention ζ
The lubricating oil is separated from the discharge gas that has flowed into the oil separation chamber and is discharged to the outside of the compressor through a discharge side opening provided on the opposite side of the compression mechanism section of the motor chamber. On the other hand, the lubricating oil separated from the discharged gas is collected in the oil reservoir of the oil pan, and then supplied to the bearing of the sub-bearing member by the pumping action of the oil groove on the outer circumference of the shaft portion of the drive shaft. is discharged to the compression mechanism side of the motor room on the opposite side, preventing remixing of the discharged gas and lubricating oil.
In addition, according to the present invention, the lubricating oil separated from the discharge gas in the oil separation space is collected in an oil sump in the motor room, while the discharge pipe from which the lubricant is separated is placed near the end of the rotor of the electric motor. When the discharged gas is about to flow into the discharge pipe, it is centrifugally diffused by the rotor, and the lubricating oil remaining in the discharged gas is separated.The lubricating oil separated in the oil separation chamber, which is about to flow into the discharge pipe, is also centrifugally separated, and the lubricating oil is centrifugally separated from the compressor external piping. The leakage of lubricating oil into the system can also be prevented by the present invention.A sub-bearing member partitions the side of the electric motor leading to the outside of the compressor and an oil separation chamber, and the lubricating oil and discharged gas separated from the discharged gas in the oil separation chamber are separated from each other. This also prevents the lubricating oil from being remixed with the lubricating oil by the rotor of the motor.Also, according to the present invention, the discharged gas that does not pass through the motor chamber and does not separate the lubricating oil is separated from the lubricating oil in the oil separation chamber in its flow direction. When changing the lubricating oil in the discharged gas, the lubricating oil is separated from the discharged gas by its inertia force, and the separated lubricating oil is directly collected in an oil pan installed near the bearing at the front in the direction of movement. The oil film is supplied to the bearings of the auxiliary bearing members supported on both sides and the bearings of the compression mechanism, and the oil film lubricates the sliding surfaces and alleviates collisions between the drive shaft and the sliding surfaces, thereby reducing vibration and noise generation. Also, the present invention (Yo) When the discharged gas that does not pass through the motor room and does not separate the lubricating oil changes its flow direction in the oil separation chamber, the lubricating oil in the discharged gas is separated from the discharged gas by its inertial force, and the separated lubrication After the oil is directly collected in an oil receiver installed near the bearing at the front in the direction of movement, the oil is supplied to the bearing of the auxiliary bearing member that supports the drive shaft on both sides of the motor and the bearing of the compression mechanism, and the oil film It lubricates the sliding surfaces and alleviates collisions between the drive shaft and the sliding surfaces to reduce vibration and noise generation.It also flows into the compression chamber and seals the compression chamber gap with an oil film to prevent compressed gas from leaking and compress it again. A series of oil supply passages are formed which are discharged together with gas into the oil separation chamber. The present invention is carried out by two systems: lubrication from the auxiliary bearing member and lubrication from the oil reservoir of the oil receiver of the sub-bearing member. The scroll refrigerant compressor of the first embodiment will be explained with reference to Figs. An upper high-pressure space housing a main body frame 5 supporting one end of a drive shaft 4 connected to a motor (electric motor) 3 and an upper frame 126 supporting the other end to which a fixed scroll member 15 forming a chamber is fixed with bolts; , lower accumulator chamber 46
The middle partition cover 134 is made of mild steel and has excellent weldability with the airtight container 1, and is provided on its outer peripheral surface. The protruding strip 79a is in contact with the inner wall surface and end surface of the upper sealed case la and the lower sealed case 1b, and the protruded strip 79a, the upper sealed case la, and the lower sealed case lb form a single weld bead 79b. Even though it is hermetically welded by
As shown in FIG. 11, an annular seal ring 135 with a cut made of Teflon is fitted to the outer circumferential groove of the fixed scroll 15, and the seal ring 135 is divided into a side where the motor (electric motor) is arranged and a side where the discharge chamber 2 is disposed. Temperature motor (electric motor)
As shown in Figure 12, the space on the side where 3 is placed is connected to the upper end surface of the stator 3b of the motor 3, which has laminated thin steel plates fixed with rivets, by high-density energy welding, typically by electron beam welding or laser welding. The upper bearing 126 is fixed as a thin bead 137 without causing thermal strain to the member, and the upper bearing 126 is the boundary between the upper oil separation chamber 128 and the lower motor chamber 6. The stator 3b to which the upper bearing 126 is fixed is fixed to the sealed container l by shrink fitting, and there is a gap between the outer periphery of the end and the sealed container l. 136 are provided. The main body frame 5 made of eutectic graphite cast iron to which the fixed scroll 15 is fixed with bolts and its outer periphery are welded and fixed to the closed container 1 at several points, the main part of the drive shaft 4 supported by the upper frame 126 and the main body frame 5. The diameter of the bearing 12 is set to be larger than the sum of the diameter of the crankshaft 14 and twice the eccentricity of the crank, and even if the drive shaft 4 is configured to be able to be pulled out upward, the rotor of the motor 3 An upper balance weight 75 whose outer diameter is set larger than the outer diameter of the rotor 3a and has a disk shape is attached to the upper end of the rotor 3a, and a lower balance weight 76 is attached to the lower end of the rotor 3a, so that the axial movement of the rotor 3a is controlled by the upper frame. 126 and the end of the main body frame 5. The lower surface of the lower balance weight 76 attached to the drive shaft 4 comes into contact with the thrust bearing section 13 provided on the upper end surface of the main body frame 5 and having a plurality of radial shallow grooves 7, thereby connecting the drive shaft 4 and the rotor 3a. I support it. Crankshaft 14 at the lower end eccentric from the main shaft of the drive shaft 4
Even if the fixed scroll 15 is engaged with the orbiting bearing 18b of the orbiting boss 18e provided on the orbiting scroll 18, the fixed scroll 15 is made of high-silicon aluminum whose coefficient of thermal expansion corresponds to an intermediate value between pure aluminum and eutectic graphite cast iron. It is made of alloy and is separated from the spiral fixed scroll wrap 15a and end plate 15b, and is provided with a discharge port 16 that opens at the beginning of the fixed scroll wrap 15a in the center of the end plate 15b. Inhalation chamber 17
is provided. Discharge port 16ζ Discharge chamber 2. A discharge port 16 is connected to the oil separation chamber 128 via a bypass discharge pipe 127 that communicates between the side wall of the closed container 1 and the upper end side wall.
Even if the check valve device 50 is installed so as to cover the Valve body 50b (or valve body 5 having a discontinuous annular hole 50ea)
0e), a valve case 99 having a check valve hole 50a, a central hole 50g, and a plurality of small discharge holes 50h around it, and a valve body 5.
The spring device 50c interposed between the valve case 99 and the spring device 50c contracts when its own temperature exceeds 50°C, but has a shape memory property that expands when its own temperature exceeds 50°C. When the compressor is in operation, the check valve hole 50a contracts to the bottom of the check valve hole 50a in response to the discharge gas pressure, and when the compressor is stopped, the valve body 50 is set to be pressed against the end plate 15b to close the discharge port 16. Fixed scroll wrap 15 as shown in Figures 1 and 13
An orbiting scroll 18 made of an aluminum alloy in which a spiral orbiting scroll wrap 18a that engages with a compression chamber and an orbiting boss portion 18e that engages with a crankshaft 14 of a drive shaft 4 are made upright. & It is arranged surrounded by the fixed scroll 15 and the main body frame 5, and even though the surfaces of the wrap support disk 18c and the orbiting scroll wrap 18a are subjected to hardening treatment such as porous nickel plating, the tip of the orbiting scroll wrap 18a is Even though a spiral tip seal groove is provided and a resin tip seal 98a is installed in the tip seal groove with a slight gap, the orbiting scroll 18 is pressed toward the axial side of the fixed scroll 15. When the flat part of the wrap support disk 18c contacts the tip of the fixed scroll wrap 15a, the tip of the orbiting scroll wrap 18a does not touch the fixed scroll 15 and maintains a very small distance of several microns.
Accumulator chamber 4 leading to the evaporator side of the refrigeration cycle
6 (Y) A U-shaped suction pipe 1 formed of a lower sealed container 1b and a partition lid 134, attached to the partition lid 134, and having an oil suction hole 139 in the middle of the passage.
41 to the suction chamber 17. Suction pipe 141
The Noura suction hole 139 is set so that the refrigerant liquid and lubricating oil stagnant in the low-pressure oil reservoir 46a are sucked up by the negative pressure generated when the refrigerant gas passes through the suction pipe 137. Suction pipe 13 leading to the evaporator side of the refrigeration cycle
81; L Branches and communicates with the suction hole 43 which communicates with the suction chamber 17 and the accumulator chamber 46. A flat plate-shaped thrust bearing 20C whose movement in the rotational direction is restrained by a split bottle-shaped parallel pin 19 fixed to the main body frame 5 and can only move in the axial direction; between the L-wrap support disk 18c and the main body frame 5 The elastic force of the annular seal ring (made of rubber) interposed between the thrust bearing 20 and the main body frame 5 makes it come into contact with the sliding surface of the end plate 15b of the fixed scroll 15 via the spacer 140. The axial dimension of the spacer 140 is set to be approximately 30 microns larger than the height of the lap support disk 18c of the orbiting scroll 18.
As shown in FIGS. 8 and 9, the center of the orbiting bearing 18b and the end surface of the orbiting boss portion 18e of the orbiting scroll 18 on the side of the main body frame 5 are provided to enable the formation of an oil film of lubricating oil in the gap between the planes on both sides of the orbiting scroll 18. A similar annular seal groove 95 is provided, and a partially cut resin annular ring 94 is attached to the annular seal groove 95. (Y) Even if the back pressure chamber 39 of the orbiting scroll 18 formed by the main body frame 5 of the orbiting scroll 181 and the thrust bearing 20 is sealed and the side of the main bearing 12 that supports the drive shaft 4 is sealed, the annular thrust bearing 20 2nd FIA mold for making sintered alloy that can be easily formed into large shapes.As shown in FIG.
Even when the main body frame 5 is installed, a release gap 27 of about 0.05 mm is provided between the main body frame 5 and the thrust bearing 20, and there is a release gap 27 between the inside and outside of the release gap 27. Even if an annular groove 28 is provided for mounting the seal ring 70, the seal ring 70 seals between the release gap 27 and the back pressure chamber 39. Oil filler A38 leading to the discharge chamber oil sump 34
It leads to a. The rotation prevention member (hereinafter referred to as Oldham ring) 24 of the orbiting scroll 18 disposed inside the thrust bearing 20 is made of light alloy or reinforced fiber composite material suitable for sinter molding or injection molding methods, and the inventor The ring thickness of the Oldham ring 24 is such that when the Oldham ring 24 reciprocates, Even if the upper closed container 1 is set so that it slides smoothly between the main body frame 5 and the lap support disk 18c and does not cause a jumping phenomenon.
The rotor 3a passes through the upper frame 126 at the upper end of the rotor 3a.
A discharge pipe 31 extending close to the end of the pipe 31 and a glass terminal 88 for connecting the motor power supply are attached, and in the center thereof, a U-shaped pipe 127a of the discharge bypass pipe 127 is connected to the secondary bearing 8 provided on the upper frame 126. They are provided with opposing openings. Oil pan 1 on the central protrusion of the upper frame 126
Even though the oil separation element 143 is arranged at 4g and the oil sump 144 is provided below it, the upstream end of the U-shaped pipe 127a extends only to the upper end of the upper sealed container 1a. The workability of the welded part 1a3 between the upper cover 1al and the shell 1a2 is improved.The discharge chamber oil sump 34 (
The stator 3b of the motor 3 is connected to the lower outer periphery of the oil separation chamber 128 disposed in the upper part of the motor chamber 6 through a cooling passage 35 provided by cutting out a part of the outer periphery of the stator 3b of the motor 3. A spiral oil groove 41 is provided in the direction in which the lubricating oil separated from the discharged gas in the oil separation chamber 128 is guided to the motor chamber 6 when the drive shaft 4 rotates forward. Even if it is, oil sump 14
4 lubricating oil (axial oil reservoir 11 provided on drive shaft 4)
2a, and communicates with the thrust bearing portion 13 and the main bearing 12 via radial blind holes 113a and 113b. The back pressure chamber 39 of the orbiting scroll 18 is controlled by an annular ring 94 attached to the end of the orbiting boss portion 18e of the orbiting scroll 18. (
(See Figure 8). Oil chamber A7gal& Via a spiral oil groove 41b provided on the outer peripheral surface of the crankshaft 14, an oil chamber B78b provided at the end of the crankshaft 14, and a spiral oil groove 41a provided on the drive shaft 4. It also communicates with the main bearing 12. Although the oil chamber B78b communicates with the back pressure chamber 39 through a thin hole 40 provided in the turning boss portion 18e, there are holes in the sliding shaft portion 4a of the drive shaft 4 and the surface of the crankshaft 14.
The drive shaft 4 rotates in the forward direction.The lubricating oil in the oil chamber A78a is transferred to the oil chamber B78, which is formed by the swing bearing 18b and the crankshaft 14.
Spiral oil grooves 41a and 41b are provided in the direction in which oil is supplied from the screw pump to the motor 3 side, and the upper ends thereof do not reach the thrust bearing portion 13 (~a second compression chamber that intermittently communicates with the suction chamber 17). 51 and the back pressure chamber 39 (as well as the keyway 71 of the orbiting scroll 18 and the oil groove 91 provided in the thrust bearing 20; the outer peripheral space 37 on the outside of the wrap support disk 18c; The oil damper chamber 145 is provided between the oil filler C38c and the end plate 15b and the valve case 99. Even though the back pressure chamber 39 and the outer circumferential space 37 communicate with each other through the injection passage 74 formed by the small diameter injection hole 52, The oil grooves 91 and the keyway 71, which are provided in two places, are arranged at opposite positions so that the second compression chambers 51a and 51b (see FIG. 13) communicate only with the suction chamber 17. In addition, the downstream side of the oil groove 91 provided in the thrust bearing 20 is intermittently opened and closed by the lap support disk 18c. The shape of the oil separation chamber 128, the shape of the oil receiver 142, the arrangement position, the oil separation element 143, the compressor operating speed, etc. Depending on the conditions (it becomes possible to secure sufficient lubricating oil), the axial oil filler 112a may be further extended to open the oil chamber A78a (also, the discharge chamber oil sump 34 may be abolished and the discharge chamber oil The refrigerant gas discharged from the motor chamber 6 may be introduced into the annular groove 28 on the back surface of the thrust bearing 20 while eliminating the oil supply passage from the reservoir 34 to the oil chamber A78a. In the vertical cross-sectional view of the example horizontal scroll refrigerant compressor, the inside of the closed container 201 serves as the high-pressure space side on the left side, which accommodates the drive section and the compression mechanism section, and the accumulator chamber 246 on the right side, by means of a partition lid 134a. Although it is partitioned into a low-pressure space leading to the downstream side of the evaporator of the refrigeration cycle, the main body frame 205 to which the fixed scroll 215 is bolted is fixed to the closed container 201 by welding, and the auxiliary frame 126a is attached to a motor (with high-density energy welding).
Even if the stator 3b of the electric motor) 3 is fixed to the airtight container 201 by shrink-fitting, the discharge chamber 202 and the discharge chamber oil reservoir 234 communicate with each other at the top and bottom. Center hole 242aJ, t,
A secondary bearing 208 that supports the small end shaft 204d of the drive shaft 204
smaller than the inner diameter of the oil separation element 243 and the small end shaft 204
Even if the setting is made so that the lubricating oil in the oil reservoir 244 between the main frame 205 and the auxiliary frame 126 does not leak out,
A helical oil groove 241i provided on the small end shaft 204d of the drive shaft 204 supported by a and a vertical groove opened to the oil sump 244 and provided at the shrink-fit joint between the drive shaft 204 and the rotor 3a of the motor 3. One end of the suction pipe 141a attached to the inner partition lid 134a communicates with the suction chamber 17, and the other end opens toward the top of the accumulator chamber 246. In order to prevent the refrigerant flowing in via the suction pipe 138a from directly flowing into the suction pipe 141a, there is a pipe protruding from the partition plate 147 fixed to the partition lid 134a. A baffle 148 is arranged.Other configurations (such as those shown in FIG. 1 are omitted as they are similar to those shown in FIG.
Figure 5 is a vertical sectional view of a horizontal scroll refrigerant compressor according to a third embodiment of the present invention, showing the upper part of the oil separation chamber 128b formed by the auxiliary frame 126b and the end of the closed container 301, and the discharge chamber. An oil pan 342 provided in the central protrusion of the auxiliary frame 126b is connected to the upper part of the oil container 302 (by a discharge bypass pipe 138b extending outside the sealed container 301). Near the top of the oil pan 342 (
Even though the oil separation element 343 is mounted on the end wall of the closed container 301, the other configurations are similar to those shown in FIGS. 1 and 14, so the explanation will be omitted. The operation of the configured scroll refrigerant compressor will be explained. In Figs. 1 to 13,
A drive shaft 4 is rotationally driven by a motor (electric motor) 3.

Then, the orbiting scroll 18 tries to rotate around the main axis of the drive shaft 4 by the crank mechanism of the drive shaft 4. The key part of the orbiting scroll 18 side of the ball dam ring 24 (see FIG. 2) is the key of the orbiting scroll 18. It engages with the groove 71, and the parallel plane parts on both sides engage with the through hole 24b having the parallel plane part 24a of the thrust bearing 20, which is fixed to the main body frame 5 so that only rotational movement is restricted, thereby preventing rotation. The fixed scroll 15 rotates
At the same time, the volume of the compression chamber is changed to perform suction and compression of refrigerant gas.

Then, from the downstream side of the evaporator of the refrigeration cycle connected to the compressor, the suction refrigerant power of a gas-liquid mixture containing lubricating oil branches from the suction pipe 138 and flows into the suction chamber 17 and the accumulator chamber 46. Straight suction pipe 1 through which gas flows into the suction chamber 17 and the accumulation lake chamber 46
Due to the difference in inertia of the suction refrigerant flowing inside the suction chamber 1
The refrigerant gas flows into the accumulator chamber 7 and the unevaporated refrigerant flows into the accumulator chamber 46. Accumulator chamber 46
The liquid refrigerant and lubricating oil that have been separated from the refrigerant gas due to the weight difference between the gas and liquid and the inertial force when changing the direction of inflow are stored at the bottom of the accumulator chamber 46.
The collected suction refrigerant gas is sucked up into the suction hole 43 in an atomized state through the oil suction hole 139 due to the negative and positive generated when it passes through the suction pipe 141, and is mixed into the suction refrigerant gas again.a Gas-liquid separated suction refrigerant Gas ζ friend inhalation chamber 1
7. It is confined in the compression chamber via the first compression chambers 61a, 61b formed between the orbiting scroll 18 and the fixed scroll 15, and is sequentially transferred to the second compression chambers 51a, 51b, and the third compression chambers 60a, 60b. The oil is discharged from the central discharge port 16 through the check valve device 50 into the discharge chamber 2 and expands into the oil separation chamber 128 via the discharge bypass pipe 127. The discharged refrigerant gas that has flowed into the oil separation chamber 128 collides with the oil separation element 143 to separate the lubricating oil, and then flows into the space between the rotor 3a and the upper frame 126 through the outer periphery of the upper frame 126. The lubricating oil is also separated by the centrifugal diffusion effect of the upper balance weight 75 of the rotor 3a, and is discharged from the discharge pipe 31 to the outside of the compressor. Flowing down along the inner space of the wire bundle
The oil is collected in the discharge chamber oil sump 34. The lubricating oil separated in the oil separation chamber 128 is collected in the lower discharge chamber oil sump 34 via the cooling passage 35 on the outer periphery of the stator 3b.The lubricating oil captured in the oil separation element 143 is collected in the lower oil sump After the sliding surface of the secondary bearing 8 is lubricated through the spiral oil groove 41 provided on the small end shaft 4d of the drive shaft 4, the oil is collected in the discharge chamber oil sump 34 at the bottom of the motor chamber 6. The lubricating oil in the oil sump 144 is protected by the spongy fiber structure of the oil separation element 143 and is prevented from being diffused by the discharged refrigerant gas flowing into the oil separation space 128 (1). Axial oil hole 112a and radial oil hole 113a, 1 provided in oil C drive shaft 4
13b to the thrust bearing section 13. The upper sliding surface of the main bearing 12 is lubricated and the bearing gap of the main bearing 12 is sealed with an oil film to prevent refrigerant gas from the motor chamber 6 from entering the main bearing 12. The release gap No. 27 on the back side of the thrust bearing 20, which communicates with the discharge chamber oil sump 34 via the filter 149゜ oil filler A38a, is filled with lubricating oil on which the discharge pressure acts, but its back pressure bias and the elasticity of the seal ring 70 Due to the force, the thrust bearing 20 attaches the spacer 14 to the coupling surface of the end plate 15b of the fixed scroll 15 with the main body frame 5.
0 and thereby the orbiting scroll 1
Although the lap support disk 18c of No. 8 is held between the end plate sliding surface 15b2 and the thrust bearing 20, the lubricating oil in the discharge chamber oil reservoir 34 flows into the back pressure chamber 39 through a path described later, gradually increasing the back pressure chamber pressure. Takatori The back pressure presses the wrap support disk 18c of the orbiting scroll 18 against the end plate sliding surface 15b2 of the fixed scroll 15, and the fixed scroll wrap 15
The tip of a and the lap support disk 18C of the orbiting scroll 18
As a result, the compression chamber is sealed, and the suction refrigerant gas is efficiently compressed, allowing stable operation to continue. During compression, when refrigerant gas leaks into the adjacent low-pressure compression chamber, it flows into the tip seal groove 98, and the back pressure of the gas presses the tip seal 98a against the side surface of the bottom compression chamber of the tip seal groove 98a and the fixed scroll 15. , to seal the compression gap. When the compressor is stopped, the orbiting scroll 18 momentarily moves in reverse rotation due to the reverse flow based on the pressure difference of the refrigerant gas in the compression chamber. The refrigerant gas flows backward from the compression chamber to the suction chamber 17. The orbiting scroll 18 is as shown in Fig. 13.
Although the first compression chambers 61a and 61b are stopped at the turning angle in which they communicate with the suction chamber 17, the refrigerant gas in the compression chambers flows back into the suction chamber 17, causing the discharge port 16
The refrigerant gas pressure in the discharge port 16 and the discharge chamber 2 suddenly decreased.
The valve body 50b is connected to the discharge port 1 due to the refrigerant gas pressure difference between the
6 to prevent continuous backflow of discharged refrigerant gas from the discharge chamber 2 to the compression chamber. The first compression chambers 61a, 61b and the back pressure chamber 39, which communicate intermittently with the suction chamber 17, are the first compression chamber 6.
1a and 61b are in communication with the suction chamber 17 only when they are in communication with the suction chamber 17. At the same time, the thrust bearing 20 and the lap support disk 18c are sealed with a lubricating oil film, so that the compression chamber During compression, refrigerant gas does not flow back into the back pressure chamber 39 during compression. Liquid compression is likely to occur at the beginning of compressor cold startup, and a thrust force acts on the orbiting scroll 18 in the direction opposite to the discharge port 16 due to the compressed refrigerant pressure in the compression chamber. -Thick Back pressure chamber at the beginning of compressor cold startup 39 pressure is low, orbiting scroll 18
The lap support disk 18c separates from the head plate sliding surface 15b2 and retreats to the thrust bearing 20, where it is supported. If a gap is created between the wrap support disk 18c and the tip of the fixed scroll wrap 15a, the pressure in the compression chamber decreases and the pressure in the compression chamber decreases at the initial stage of startup. If the pressure in the compression chamber suddenly rises abnormally due to liquid compression occurring in the compression chamber during continuous operation, the thrust force acting on the orbiting scroll 18 may This becomes larger than the back pressure force acting on the back surface, and even though the orbiting scroll 18 moves in the axial direction and is supported by the thrust bearing 20, the seal of the compression chamber is released in the same manner as described above, and the pressure in the compression chamber decreases. Although the load decreases, the lubricating oil in the discharge chamber oil sump 34 at the initial stage of cold start of the compressor is transferred to the oil chamber A78a via the oil filler A38a by the screw pump action of the spiral oil grooves 41a and 41b provided on the drive shaft 4. A part of the anti-lubricating oil passes through the spiral oil groove 41b and lubricates the sliding surface of the swing bearing 18b.
The pressure is reduced from the oil chamber B78b through the small hole 40. Back pressure chamber 3
The lubricating oil supplied to the main bearing 12 by the helical oil groove 41a lubricates each sliding surface of the thrust bearing part 13, and then is collected again in the discharge chamber oil sump 34. Although the bearing gap is sealed by the oil film of the lubricating oil supplied to the thrust bearing part 13, the pressure in the motor chamber 6 increases as time passes after the compressor starts cold, and the lubricating oil in the discharge chamber oil sump 34 increases. The differential pressure between the oil and the back pressure chamber 39 causes oil to be sucked into the oil chamber A78a and is supplied to the back pressure chamber 39 along with the screw pump action of the spiral oil grooves 41a and 41b.
Even if the pressure of 9 is increased sequentially, in an arrangement in which the center of the compression chamber, the center of the orbiting bearing 18e, and the center of the annular ring 94 all coincide with each other, the annular ring 94 makes an orbiting motion together with the orbiting scroll 18, so that the inertia at that time is Due to the force, it tends to jump out of the annular seal groove 95 provided in the pivot boss portion] 8e. Thereby, the annular ring 94 is pressed against the outer surface of the main body frame 5 and the annular seal groove 95, and
The annular seal groove 95 is formed by the oil scraping action of the annular ring 94.
Lubricating oil is forced between the annular ring 94 and the annular ring 94, and the annular ring 94 is also pressed by the dynamic pressure generated at that time, sealing the space between the oil chamber A78a and the back pressure chamber 39. Further, the annular ring 94 is pressed against the outer surface of the annular seal groove 95 due to the pressure difference between the back pressure chamber 39 and the oil chamber A78a, so that the seal between the rain spaces is more secure. The sliding surface between the annular ring 94 and the main body frame 5 is sealed by the oil film of lubricating oil retained in the oil groove 94a provided on the surface of the ring 94, and the wear and sliding resistance of the sliding surface is reduced. Lubricating oil pressure in oil chamber A78a and back pressure chamber 3
The orbiting scroll 18 is evenly biased with back pressure toward the fixed scroll 15 by the lubricating oil pressure of 9, and the lap support disk 18c and the end plate sliding surface 15b2 slide smoothly and the deformation of the lap support disk 18c is prevented. Even if the axial clearance of the compression chamber is minimized, the lubricating oil that has flowed into the back pressure chamber 39 will intermittently flow into the outer peripheral space 37 via the curved groove 91 provided in the thrust bearing 20, and further flow into the end plate 15b. Oil filler C38c provided in oil damper chamber 145. The pressure is gradually reduced through the small-diameter injection hole 52 and flows into the second compression chambers 51a, 51b. The lubricating oil injected into the compression chamber together with the suction refrigerant gas joins the lubricating oil and seals the small gap between the compression chambers in contact with an oil film to prevent compressed refrigerant gas leakage. While being lubricated, the compressed refrigerant gas passes through the discharge port 16 to the discharge chamber 2.The discharge bypass pipe 12
7. In the oil supply route from the discharge chamber oil 34 to the second compression chambers 51a and 51b via the back pressure chamber 39, the back pressure chamber 39 maintains an appropriate balance between the discharge pressure and the suction pressure. The second compression chamber 51 maintains an intermediate pressure.
The injection holes 52a and 52b openings ζ of a and 51b generate a force t that is instantaneously higher than the pressure in the back pressure chamber 39, which changes in accordance with the pressure in the motor chamber 6. The lap support disk 18c closes the open end of the oil filler 91 of the thrust bearing 20, and the lap support disk I
Since the sliding surface between Bc and the thrust bearing 20 is sealed with an oil film, the refrigerant gas during compression does not flow back into the back pressure chamber 39, and the average pressure in the second compression chambers 51a and 51b is The pressure L1 is lower than the pressure in the back pressure chamber 39. Also, as described above, the orbiting scroll 18 at the initial stage of starting the compressor is separated from the fixed scroll 15 and supported by the thrust bearing 20 which receives the elastic force of the seal ring 70. Lubricating oil supplied to the back pressure chamber 39 under a differential pressure after the compressor has started and stabilized (upper) A biasing force of an intermediate pressure is applied to the orbiting scroll 18 to press the lap support disk 18c against the end plate 15b, and the sliding surface is coated with an oil film. The lubricating oil in the back pressure chamber 39 is present in the gap between the sliding surfaces of the thrust bearing 20 and the lap support disk 18c, and the gap is sealed between the outer peripheral space 37 and the suction chamber 17. In addition, because the compression ratio of the scroll compressor is constant, when the suction refrigerant gas pressure is relatively high and the compression chamber pressure becomes very high, such as immediately after startup during cooling, or abnormal liquid compression occurs. For example, when the orbiting scroll 18 separates from the fixed scroll 15 and is supported by the thrust bearing 20 as described above,
The thrust bearing 20 (Y), which is biased with back pressure, cannot support the abnormally increased compression chamber pressure load and retreats in the direction of decreasing the release gap 27, causing the wrap support disk 18c of the orbiting scroll 18 and the fixed scroll of the fixed scroll 15 to The axial gap between the end of the wrap 15a and the end of the wrap 15a expands. This causes a lot of leakage between the compression chambers, and the pressure in the compression chamber drops suddenly during compression. It instantly returns to its original position and the back pressure chamber 39
The pressure dropped significantly and stable operation resumed. A force t that also expands the axial dimension between the tip of the orbiting scroll wrap 18a and the fixed scroll 15. The tip seal 98a closes the fixed scroll 15 by the gas pressure on its back surface. Since the compressed refrigerant gas is pressed to the side of In the above embodiment, the lubricating oil in the discharge chamber oil sump 34 is introduced into the release gap 27 provided on the back surface of the thrust bearing 20. Introducing the compressed refrigerant during the final compression stroke, or introducing the discharged refrigerant gas from the area where the compression chamber and the discharge boat 16 communicate during the final compression stroke into the release gap 27.
Furthermore, in the above embodiment, the sliding gap between the lap support disk 18c of the orbiting scroll 18 and the thrust bearing 20 is sealed only with an oil film of lubricating oil.
As proposed in Figure 3 and Figure 4 of the specification of No. 159996, the annular ring (82) is wrapped around the support disk 18c.
The sealing performance of the sliding gap between the back pressure chamber 39 and the outer peripheral space 37 can be improved by attaching it to the back side of the As explained above, the unevaporated refrigerant among the refrigerant returned from the evaporator of the refrigeration cycle flows into the accumulator chamber 246 as in the case of the first embodiment, and the refrigerant gas flows into the suction chamber 17.
flows into. The unevaporated refrigerant that has flowed into the accumulator chamber 246 collides with the baffle 148 and is separated into refrigerant gas with low specific gravity and liquid refrigerant and lubricating oil with high specific gravity.
The liquid refrigerant and lubricating oil are collected in the low pressure oil reservoir 46b at the bottom.
The lubricating oil and liquid refrigerant stored in the low-pressure oil reservoir 46b are inhaled together with the suction refrigerant gas in an atomized state through the oil suction hole 139a due to negative pressure generated when the refrigerant gas flows into the suction chamber F from the upper open end of the suction pipe 141a. Even if the refrigerant gas is sucked into chamber 17, the refrigerant gas sucked in from both sides of suction chamber I7 is
The compressor is discharged into the discharge chamber 202 and flows into the motor chamber 206 through an open passage between the inner wall of the closed container 201 and the outer periphery of the main body frame 205, and the discharge bypass pipe 13.
As in the case of the first embodiment, the lubricating oil in the discharged gas captured by the oil separation element 243 is collected in the oil sump 244 and the drive shaft 20
The motor chamber 206 on the side closer to the compression mechanism section through the spiral oil groove 241 and vertical groove 146 provided in the small end shaft 204d of No. 4
The other operations such as lubricating the sliding surface of the auxiliary bearing 208 during the passage are similar to those in the first embodiment and will not be described here. Next, the operation of the third embodiment will be explained with reference to FIG. 15. The discharged refrigerant gas discharged into the discharge chamber 302 (flows into the motor storage space through the passage between the outer periphery of the main body frame 305 and the inner wall of the sealed container 301, and also flows into the oil separation chamber 128b through the discharge bypass pipe 138b). The lubricating oil separated from the discharge gas when changing the flow direction and the lubricating oil separated when colliding with the oil separation element 343 are collected in the oil sump 344 of the oil receiver 342 at the bottom. Since it is the same as in the second embodiment,
Although the explanation is omitted, as described above, according to the above embodiment, the scroll compression mechanism section and the motor (electric motor) 3 are placed in the closed container 1.
A drive shaft 4 is housed and fixed inside the drive shaft and connected to the motor 3.
The upper frame 12 is provided on the side of the counterpressure mechanism of the motor 3.
6 and the main body frame 5 of the scroll compression mechanism section, and the upper frame 126 is attached to the end of the stator 3b which is cut out from the laminated plate of the motor 3 without contacting the inner wall of the closed container 1 by electron beam welding or laser welding. By fixing the bead 137 in a thin bead 137 by high-density energy welding as represented by , local welding noise using high-density energy can cause damage to the windings of the stator 3b and thermal distortion to the laminate. Since there is no stator 3 with a small outer diameter,
b and the upper frame 126 can be welded, making it possible to downsize the motor 3 (1) and downsize the compressor. In addition, the radial vibration of the upper frame 126 caused by supporting the rotational load of the drive shaft 4 can be reduced. , upper frame 12
Attenuation is caused by slight deformation at the thin joint between the outer periphery of motor 6 and stator 3b of motor 3, and further attenuation can be achieved by slight slippage between the laminated plates. In addition to reducing vibration by supporting on both sides, the vibration of the upper frame 126 is not directly propagated to the inner wall of the closed container 1, and the vibration of the wall surface of the closed container 1, the vibration of the external piping system connected to the closed container l, and the accompanying vibrations are prevented. According to the above embodiment, the scroll compression mechanism and the motor 3 are housed and fixed in the airtight container 1, and the drive shaft 4 connected to the motor 3 is connected to the motor 3. Upper frame 126 provided on the side of the counterpressure mechanism section
The upper frame 12 supports the upper frame 12 and the scroll compression mechanism so that the discharged gas does not pass through the motor chamber 6 that houses the motor 3.
The gas is introduced into the oil separation chamber 128 formed by the end wall of the sealed container 1 and the end wall of the closed container 1, and is discharged toward an oil receiver 142 provided near the sub-bearing 8 of the upper frame 1.26 and open to the sub-bearing 8. By releasing oil, the oil separation chamber 128
When changing the flow direction, the lubricating oil contained in the discharged gas is separated from the discharge gas without passing through the motor chamber 6 and the lubricating oil is not separated, using its inertia force, and the lubricating oil is separated from the discharged gas near the auxiliary bearing 8 at the front in the direction of movement. The lubricating oil can be supplied directly to the oil sump 142 provided at the bottom of the compressor, without introducing lubricating oil from the oil sump at the bottom of the compressor. Since an independent oil supply path can be constructed that can supply lubricating oil without requiring a Component parts can be simplified. Also, according to the above example, there is an oil separation chamber! By arranging the oil separation element 143 between the discharge gas introduction opening to 28 and the oil reservoir 144 of the oil receiver 142 provided in the upper frame 126, the oil separation chamber 12
The discharged refrigerant gas that has flowed into the refrigerant gas 8 collides with the oil separation element 143 so that lubricating oil can be deposited and efficiently captured. The captured lubricating oil is dripped into the oil sump 144 at the bottom, and the discharged refrigerant gas is prevented from passing near the oil sump 144 to prevent the collected lubricating oil from scattering, thereby increasing the durability of the sliding parts by securing the lubricating oil. Further, according to the above embodiment, a spiral oil is formed on the outer peripheral surface of the small end shaft 204d of the drive shaft 204 supported by the sub-bearing 208 of the auxiliary frame 126a, and is connected to the oil sump 244 of the oil pan 242. Groove 2
41 is provided, and by utilizing the screw pump action of the spiral oil groove 241, the lubricating oil in the oil reservoir 244 is discharged to the scroll compression mechanism side of the motor chamber 206 through the vertical groove 146 provided in the drive shaft 204, and compression is performed. By providing the opening of the discharge pipe 31 leading to the outside of the machine on the side opposite to the compression mechanism part of the motor chamber 6, the flow path of the discharge gas discharged to the piping system outside the compressor and the lubricating oil discharge destination are isolated. , it is possible to prevent the remixing of the discharged gas and the lubricating oil, secure the lubricating oil inside the compressor, and improve the durability of the sliding parts. A discharge chamber oil sump 34 is located at the bottom of the motor chamber 6, which is housed and fixed in a sealed container l, and in which the upper frame 126 is disposed between the anti-compression mechanism side of the motor 3 and the end of the sealed container l. Oil separation chamber 12 leading to
8 is provided to introduce the discharged gas that does not pass through the motor chamber 6 into the upper part of the oil separation chamber 128, and also to introduce the discharge gas into the upper part of the oil separation chamber 128.
The opening of the discharge pipe 31 leading to the outside of the compressor is arranged in the space between the end of the oil separation chamber 126 and the upper frame 126, and the opening of the discharge pipe 31 is brought close to the end of the rotor 3a.
The lubricating oil separated from the discharge gas at step 8 is collected in the discharge chamber oil sump 34 at the bottom of the motor chamber 6. When the discharge gas is about to flow into the discharge pipe 31, it is centrifugally diffused by the rotor 3a, and the lubricating oil remaining in the discharge gas can be centrifugally separated, and the lubricant separated in the oil separation chamber 128, which is about to flow into the discharge pipe 31, Since the oil can also be centrifugally diffused, the lubricating oil separated from the discharge gas will not be mixed into the discharge gas again, preventing the lubricating oil from flowing into the compressor external piping system, and lubricating the discharge chamber oil sump 34. It is also possible to prevent oil shortage and improve the durability of the sliding parts by supplying sufficient oil to the main bearing 12 and other sliding parts. 4 is supported by an upper frame 126 provided on the side of the reaction pressure mechanism of the motor 3 and the main bearing 12 of the scroll compression mechanism. By also serving as a partition member that partitions the side of the chamber 128, the lubricating oil separated from the discharged gas can be diffused by the rotation of the rotor 3a of the motor 3 and the resulting discharged gas, without the need for special components. To secure lubricating oil by preventing re-mixing into the motor chamber 6 and effectively collecting it in a discharge chamber oil sump 34 at the bottom of the motor chamber 6 via a cooling passage 35 provided on the outer periphery of the stator 3b of the motor 3. In addition, it is possible to prevent an increase in the input when the rotor 3a diffuses the lubricating oil.Also, according to the above embodiment, the upper frame 126 in which the drive shaft 4 is provided on the side of the counterpressure mechanism part of the motor 3 and the The discharged gas that does not pass through the motor chamber 6 that is supported by the scroll compression mechanism and houses the motor 3 is introduced into the oil separation chamber 128 formed by the upper frame 126 and the end wall of the closed container 1.
The discharged gas is released toward the oil pan 142 opened to the bearing 26, and the lubricating oil captured by the oil pan 142 is transferred to the secondary bearing 8 of the upper frame 126 and the main bearing 1 of the scroll compression mechanism section.
2 (the spiral oil groove 41 and the axial sleeve hole 112a)
, radial oil fillers 113a, 113b) are provided on the drive shaft 4 and supplied to the main bearing 12 of the scroll compression mechanism section, thereby forming an oil supply passage that is not related to the discharge chamber oil sump 34 at the bottom of the motor chamber 6. can, its electrification
It is possible to reduce the size of the compressor by saving space in the motor room 6, and there is no need to limit the angle of inclination when installing the compressor, and the compressor can be placed either vertically or horizontally. In addition, according to the above embodiment, the drive shaft 4 is supported by the upper frame 126 provided on the side of the reaction pressure mechanism of the motor 3 and the scroll compression mechanism, and the motor chamber in which the motor 3 is housed. 6 is introduced into the oil separation chamber 128 formed by the upper frame 126 and the end wall of the closed container l, and the discharged gas is released toward the oil receiver 142 that opens to the bearing of the upper frame 126. Oil passages (spiral oil groove 41, axial oil well 112a, radial sleeve holes 113a, 113b) that guide the lubricating oil captured by the oil receiver 142 to the sub bearing 8 of the upper frame 126 and the main bearing 12 of the scroll compression mechanism. ) is supplied to the main bearing 12 of the scroll compression mechanism installed on the drive shaft 4, and also supplied to the oil chamber A78a, and the lubricating oil is injected into the compression chamber, so that the lubricating oil is injected into the bottom of the motor chamber 6. The compressor can be downsized by saving space in the oil sump 34 in the discharge chamber, and durability and high compression efficiency can be ensured by forming an oil film on the sliding parts of the bearings and sealing gaps in the compression chamber with the oil film. Also, according to the above example,
The drive shaft 4 is supported by an upper frame 126 provided on the side of the counterpressure mechanism of the motor 3 and a scroll compression mechanism, and the discharged gas that does not pass through the motor chamber 6 that houses the motor 3 is transferred to the upper frame 126 and the closed container 1. The discharged gas is introduced into the oil separation chamber 128 formed by the end wall and discharged toward the oil receiver 142 that opens to the bearing of the upper frame 126.
Oil passages (spiral oil groove 41, axial oil well 112a, radial sleeve holes 113a, 113b) that guide the lubricating oil captured by the oil receiver 142 to the sub bearing 8 of the upper frame 126 and the main bearing 12 of the scroll compression mechanism. ) is provided in the drive 11i14 to supply lubricating oil to the main bearing 12 of the scroll compression mechanism, and also to supply lubricating oil from the discharge chamber oil sump 34 at the bottom of the motor chamber 6, where the discharge pressure acts, to the main bearing 12 of the compression mechanism. By doing so, it is possible to increase the amount of oil supplied to the main bearing 12. As a result, it becomes possible to supply sufficient oil to the main bearing 12, which supports most of the compressive load. Although it is possible to reduce input loss by reducing the frictional resistance of the moving parts, it should be noted that similar effects and effects are expected for other rotary gas compressors as well. Effects of the Invention As is clear from the above embodiments, the present invention (1) The compression mechanism section and the electric motor are each housed in a sealed container. It is supported by the sub-bearing member and the compression mechanism, and the sub-bearing member is fixed in a thin bead shape by high-density energy welding to the end of the stator made of laminated plates of the motor without contacting the sealed container. The localized welding table using energy does not cause damage to the stator windings or thermal distortion to the laminated plates, making it possible to weld the stator with a small outer diameter and the sub-bearing member, making it possible to weld the motor. small 4V,
The compressor can be downsized, and the radial vibration of the sub-bearing member caused by supporting the rotational load of the drive shaft can be minimized at the thin joint between the outer periphery of the sub-bearing member and the stator of the electric motor. It can be damped by deformation, and it can also be damped by slight slippage between the laminated plates.As a result, in addition to reducing vibration by supporting the drive shaft on both sides of the motor, the vibration of the sub-bearing member can be suppressed in a sealed container. It is possible to achieve quiet operation by preventing vibrations on the wall surface of the sealed container, vibrations in the external piping system connected to the sealed container, and the accompanying noise generation without directly propagating the vibrations to the inner wall of the sealed container. is housed and fixed in a sealed container, and the drive shaft connected to the electric motor is supported by a sub-bearing member and a compression mechanism provided on the side of the reaction pressure mechanism of the electric motor, so that the discharged gas does not go through the electric motor room where the electric motor is housed. By introducing the discharged gas into the oil separation chamber formed by the sub-bearing member and the end wall of the sealed container, and releasing the discharged gas toward the oil receiver provided near the bearing of the sub-bearing member and open to the bearing. When changing the flow direction in the oil separation chamber, the lubricating oil contained in the discharged gas is separated from the discharge gas without passing through the motor chamber and the lubricating oil is not separated, using its inertia force, and the lubricating oil is separated from the bearing in the forward direction in the direction of movement. A nearby oil sump can be used to supply the bearing directly to the collection bearing, thereby allowing the oil supply pump to be placed in the bearing section away from the oil sump, without introducing lubricating oil from the oil sump at the bottom of the compressor. It is possible to construct an independent oil supply path that can supply lubricating oil without the need for lubricating oil, and it is possible to save space in the motor room and motor compartment oil sump, making the compressor more compact and lubricating it. The oil supply components can be simplified.Also, according to the present invention, the compression mechanism section and the electric motor are housed and fixed in a sealed container, and the drive shaft connected to the electric motor is provided on the side of the counterpressure mechanism section of the electric motor. The discharged gas, which is supported by the sub-bearing member and the compression mechanism section and does not pass through the motor chamber housing the electric motor, is introduced into the oil separation chamber formed by the sub-bearing member and the end wall of the sealed container, and the bearing of the sub-bearing member is By discharging the discharged gas toward an oil pan that is provided nearby and opening into the bearing, and by arranging an oil separation element between the discharge gas introduction opening to the oil separation chamber and the oil sump in the oil pan. However, it is possible to make the discharged gas that has flowed into the oil separation chamber collide with the oil separation element, make the lubricating oil adhere to it, and capture it efficiently. This prevents the collected lubricating oil from scattering by preventing it from passing near the oil sump.
Further, according to the present invention ζ, the compression mechanism section and the electric motor are housed and fixed in a closed container, and the drive shaft connected to the electric motor is supported by the compression mechanism section and an auxiliary bearing member provided on the side of the counterpressure mechanism section of the electric motor. The discharged gas that does not go through the housing motor chamber is introduced into the oil separation chamber formed by the sub-bearing member and the end wall of the sealed container, and the oil receiver is provided near the bearing of the sub-bearing member and opens into the bearing. At the same time, an oil groove leading to the oil sump of the oil sump is installed on the outer periphery of the drive shaft supported by the bearing of the sub-bearing member. By discharging lubricating oil to the compression mechanism side of the motor room and providing a discharge side opening leading to the outside of the compressor on the side opposite to the compression mechanism part of the motor room, the amount of discharged gas discharged to the piping system outside the compressor is reduced. By isolating the flow path and the lubricating oil discharge destination, it is possible to prevent remixing of the discharged gas and the lubricating oil, thereby securing the lubricating oil inside the compressor and improving the durability of the sliding parts. The compression mechanism part and the electric motor are housed and fixed in a sealed container, and a partition member is placed between the side of the motor opposite to the compression mechanism part and the end of the sealed container, and the oil sump at the bottom of the motor room where the motor is housed is placed. An oil separation space that communicates with the outside of the compressor is provided, and the discharge gas that does not pass through the motor room is introduced into the upper part of the oil separation room, and an opening of a discharge pipe that leads to the outside of the compressor is provided in the space between the end of the motor rotor and the partition member. place the parts
By placing the opening close to the end of the rotor, the lubricating oil separated from the discharged gas in the oil separation chamber is collected in the oil sump at the bottom of the motor room.
Clothes that are about to flow into the discharge pipe located near the end of the rotor of the motor.The discharge gas is centrifugally diffused by the rotor, and the lubricating oil remaining in the discharge gas can be centrifugally separated and flowed into the discharge pipe. Since the lubricating oil separated in the oil separation chamber can also be centrifugally diffused, the lubricating oil separated from the discharged gas will not be mixed into the discharged gas again, and this will prevent the lubricating oil from leaking into the piping system outside the compressor. This prevents a lack of lubricating oil in the oil sump, and by supplying sufficient oil to the sliding parts of the compression mechanism, it is possible to improve the durability of the sliding parts. In addition, according to the present invention, the compression mechanism section and the electric motor are housed and fixed in a sealed container, and a partition member is disposed between the side of the motor opposite to the compression mechanism section and the end of the sealed container, and the bottom of the motor room houses the electric motor. An oil separation chamber that communicates with the oil sump is installed, and the discharged gas that does not go through the motor room is introduced into the upper part of the oil separation chamber.
The opening of the discharge pipe leading to the outside of the compressor is arranged in the space between the end of the rotor of the electric motor and the partition member, and the opening of the discharge pipe leading to the outside of the compressor is brought close to the end of the rotor. The auxiliary bearing member provided on the side of the counterpressure mechanism part and the compression mechanism part support the lubrication mechanism, and the auxiliary bearing member also serves as a partition member, allowing the lubrication to be separated from the discharged gas without the need for special components. This prevents oil from being diffused by the rotation of the motor rotor and from being remixed into the discharged gas.
The present invention (
Store and secure the compression mechanism and electric motor in a sealed container.
A drive shaft connected to the electric motor is supported by a sub-bearing member provided on the side of the counter-pressure mechanism part of the motor and a compression mechanism part, and the discharged gas that does not go through the motor chamber that houses the electric motor is transferred to the sub-bearing member and the end of the airtight container. Introduced into the oil separation chamber formed by the wall and
The discharge gas is discharged toward an oil receiver that is provided near the bearing of the sub-bearing member and is open to the bearing, and the lubricating oil in the oil receiver is transferred to the bearing of the sub-bearing member that supports the drive shaft and the bearing of the compression mechanism section. By supplying the oil to the motor compartment, it is possible to form an oil supply passage that is unrelated to the oil sump at the bottom of the motor room. There is no need to limit the angle of inclination when installing the compressor, and it is possible to realize a compressor that can be placed either vertically or horizontally. In addition, according to the present invention, the compression mechanism section and the electric motor are housed and fixed in a closed container.The drive shaft connecting the Lt electric motor is supported by the compression mechanism section and an auxiliary bearing member provided on the side of the counterpressure mechanism section of the electric motor, and the electric motor is housed. The discharged gas that does not go through the motor chamber is introduced into the oil separation chamber formed by the sub-bearing member and the end wall of the sealed container, and is directed to the oil receiver provided near the bearing of the sub-bearing member and open to the bearing. At the same time, the lubricating oil in the oil pan is supplied to the bearing of the auxiliary bearing member supporting the drive shaft and the bearing of the compression mechanism, and the lubricating oil supplied to the bearing of the compression mechanism is injected into the compression chamber. This makes it possible to save space in the oil sump at the bottom of the motor room and downsize the compressor.It also forms an oil film on the sliding parts of the bearings and seals the gap in the compression chamber with the oil film, resulting in improved durability and high performance. Compression efficiency can be ensured, and the present invention also provides an auxiliary bearing member in which the compression mechanism and the electric motor are housed and fixed in an airtight container, and the drive shaft connected to the electric motor is provided on the side of the counterpressure mechanism of the electric motor. Introducing the discharged gas that does not go through the motor chamber supported by the compression mechanism part and housing the electric motor into the oil separation chamber formed by the sub-bearing member and the end wall of the sealed container, and provided near the bearing of the sub-bearing member. Further, the discharge gas is released toward the oil receiver opened to the bearing, and the lubricating oil in the oil receiver is supplied to the bearing of the auxiliary bearing member supporting the drive shaft and the bearing of the compression mechanism part, and the electric motor is subjected to the discharge pressure. By supplying the lubricating oil from the oil sump at the bottom of the chamber to the bearing of the compression mechanism, the amount of oil supplied to the bearing of the compression mechanism can be increased, thereby supporting most of the compression load. Enables sufficient oil supply to the bearing part of the compression mechanism, improving the durability of the bearing part.It also reduces input loss by reducing the frictional resistance of the sliding part of the bearing.

[Brief explanation of drawings]

Figure 1 is a vertical cross section of a scroll refrigerant compressor according to the first embodiment of the present invention. Figure 2 is an exploded perspective view of the main components of the compressor. Figure 3 is an inverse view of the main parts of the compressor. Cross-sections of main parts of the check valve device @ Fig. 4 to Fig. 6 are respectively shown in Fig. 7 (a), which is a perspective view of the components of the check valve device in Fig. 3. (b) is the external appearance of the balance weight in the same compressor.
The figure shows a perspective view of the seal parts in the same compressor.
The figure is a perspective view of a sealing part for sealing the space on the motor side and the space on the discharge chamber side in Figure 1 @ Figure 12 shows the cross section of the joint between the stator of the electric motor and the auxiliary bearing member
Figure 3 is a cross section along line A-A in Figure 1 & 1st
Figure 4 shows the vertical cross section of the scroll refrigerant compressor in the second embodiment of the present invention. Figure 15 shows the vertical cross section of the scroll refrigerant compressor in the third embodiment of the present invention.
7 are longitudinal sectional views of different conventional scroll compressors. l...Airtight container 3...Motor (electric motor), 3
a...Rotation-i 3b...Stator, 4...
... Drive hole 5 ... Main frame A 6 ... Motor room (motor room), 8 ... Sub-bearing, -12 ...
Main shaft i 31...Discharge 34...Discharge base oil 1 excluding 35...Cooling path 1m 41...Spiral oil holder 78a...Oil chamber A, 112a... Vertical oil filling 113a, 113b... Radial oil filling, 12
6...Upper frame 126a...To auxiliary frame 128...Oil separation chamber 137...Thin bead dome 1
42... Oil pan 1, 143... Oil separation required 1
44... Oil a146... Vertical 204...
Drive shaft 204d...Small end assembly 206...Motor chamber 208...Sub bearing, 241...Spiral oil depth 24
2... Oil pan 1, 244... Oil 7 glue

Claims (9)

[Claims] (1) A compression mechanism and an electric motor are housed and fixed in a sealed container, and a drive shaft connected to the electric motor is supported by a sub-bearing member provided on the side of the counter-pressure mechanism of the electric motor and the compression mechanism. and a gas compressor in which the auxiliary bearing member is fixed in a thin bead shape by high-density energy welding to an end of a stator made of a laminated plate of the electric motor without contacting the closed container. (2) A compression mechanism and an electric motor are housed and fixed in a sealed container, and a drive shaft connected to the electric motor is supported by a sub-bearing member provided on a side of the counterpressure mechanism of the electric motor and the compression mechanism. , the discharge gas not passing through the motor chamber housing the electric motor is introduced into an oil separation chamber formed by the sub-bearing member and the end wall of the sealed container, and the sub-bearing member is provided near a bearing of the sub-bearing member; A gas compressor comprising means for discharging the discharged gas toward an oil receiver opened in the bearing. (3) The gas compressor according to claim 2, wherein an oil separation element is disposed between the discharge gas introduction opening into the oil separation chamber and the oil sump of the oil pan. (4) An oil groove communicating with the oil sump of the oil pan is provided on the outer periphery of the shaft of the drive shaft supported by the bearing of the sub-bearing member, and the lubricating oil in the oil sump is discharged into the motor room by the pump action of the oil groove. let me,
3. The gas compressor according to claim 2, wherein a discharge side opening communicating with the outside of the compressor is provided on a side of the motor room opposite to the compression mechanism section. (5) A motor room in which the compression mechanism and the electric motor are housed and fixed in a sealed container, and a partition member is disposed between the side of the motor opposite to the compression mechanism and the end of the sealed container to house the electric motor. An oil separation chamber communicating with an oil reservoir at the bottom of the motor chamber is provided, and discharged gas not passing through the motor chamber is introduced into the upper part of the oil separation chamber, and a space between an end of the rotor of the motor and the partition member is provided. A gas compressor, in which an opening of a discharge pipe leading to the outside of the compressor is arranged, and the opening is close to the end of the rotor. (6) A drive shaft connected to an electric motor is supported by a sub-bearing member provided on a side of a counter-pressure mechanism section of the electric motor and the compression mechanism section, and the sub-bearing member also serves as a partition member. gas compressor. (7) The gas compressor according to claim 2, wherein the lubricating oil from the oil receiver is supplied to the bearing of the sub-bearing member supporting the drive shaft and the bearing of the compression mechanism. (8) The gas compressor according to claim 7, wherein the lubricating oil supplied to the bearing of the compression mechanism is injected into the compression chamber. (9) The gas compressor according to claim 8, wherein the lubricating oil in the oil sump at the bottom of the motor chamber where the discharge pressure acts is fed to the bearing part of the compression mechanism part.