JPH06105079B2 - Scroll type fluid machine - Google Patents

Description

Description: TECHNICAL FIELD OF THE INVENTION The present invention relates to a first embodiment for controlling a fluid volume in cooperation with each other.
And a scroll type fluid machine in which the second scroll is housed in a closed shell.

[Prior art]

FIG. 1 shows basic components of a scroll compressor. In the figure, (1) is a fixed scroll, (2) is an orbiting scroll, (105) is a discharge port, (P) is a compression chamber, and 0
Is a fixed point on the fixed scroll, and 0'is a fixed point on the orbiting scroll. The fixed scroll (1) and the orbiting scroll (2) are composed of spirals of the same shape, and the shape thereof is a combination of involutes, arcs, etc., as is conventionally known.

Next, the operation will be described. In FIG. 1, the fixed scroll (1) is stationary with respect to the space, and the orbiting scroll (2) is combined with the fixed scroll (1) as shown in the figure so that its posture does not change with respect to the space. In Fig. 1, 0 °, 90 °, 180 °, 2
Exercise like 70 °. As the orbiting scroll (2) swings, the crescent-shaped compression chamber (P) formed between the fixed scroll (1) and the orbiting scroll (2) gradually decreases in volume, and this compression chamber The gas taken into (P) is compressed and discharged from the discharge port (105). During this period, the distances of 0 to 0'in FIG. 1 are kept constant, and the spiral interval is represented by a and the thickness is represented by t. Has become. a corresponds to the pitch of the spiral.

FIG. 2 shows an example of a conventional scroll compressor disclosed in, for example, Japanese Patent Laid-Open No. 55-46081. In the figure,
(1) is a fixed scroll, (2) is an orbiting scroll,
(4) is the main shaft, (6a) is the frame, (9) is the closed container,
(10) is the rotor of the motor, (11) is the stator of the motor,
(100a) is the motor lead wire, (104) is the inlet, (10
5) is a discharge port, (904) is a suction pipe, (905) is a discharge pipe, (9)
07) is a sealed terminal, (909a) is a sump lubricant, (912)
Is the space inside the shell. Further, P is a compression chamber.

This conventional example shows a scroll compressor according to an example of a so-called low-pressure shell type in which a closed type shell is held at a suction side pressure. In this low-pressure shell type, the suction pipe (904) is provided in a shell internal space (912). ) And the discharge pipe (905) is connected to the discharge port (105), the gas sucked from the suction port (104) is compressed by the operating principle described in FIG. ) Is to be discharged from.

In addition, the fixed scroll (1), the orbiting scroll (2),
The frame (6a) is located on the upper side, the rotor (10) of the motor is located on the lower side, and the stator (11) of the motor is located on the lower side. The whole of them is housed in the closed container (9), and the lubricating oil (909a) is stored in the closed container (9a). ) A sealed terminal (907) stored in the lower portion and for supplying electric power to the motor from outside the sealed container (9) is at the bottom of the sealed container (9), and therefore the sealed terminal (907).
And the motor stator (11) from this sealed terminal (907)
The lead wire (100a) connected to is immersed in the lubricating oil (909a), and when used as a refrigerant compressor, when the compressed gas is the refrigerant gas and the lubricating oil is the refrigerating machine oil,
There is a problem that the sealed terminal (907) and the lead wire (100a) are eroded to cause insulation failure.

The present invention has been made in order to solve the above problems, and the terminals and lead wires for motor power feeding are prevented from being immersed in the oil in the oil reservoir in the shell, and It is an object of the present invention to provide a scroll type fluid machine in which insulation failure does not occur and the lead wire is not affected by heat during shell assembly welding.

[Summary of the Invention] A scroll type fluid machine according to the present invention includes a motor housed in a lower part of a hermetic shell, a compression element housed in an upper part of the hermetic shell, and including a fixed scroll, an upper frame, a lower frame, and the like. A scroll-type fluid machine comprising: a terminal provided on an upper portion of the closed shell for supplying power to the motor; and an insulating coating lead wire for electrically connecting the terminal and the motor, wherein the insulating coating lead wire is provided. Is supported and housed in a through-groove in which concave portions formed in the outer peripheral portions of the fixed scroll, the upper frame and the lower frame are vertically overlapped with each other so as to be separated from the hermetic shell. It is a thing.

In the scroll type fluid machine according to the present invention, since the motor power supply terminal and the lead wire are not immersed in the oil in the oil reservoir in the shell, insulation failure does not occur in these terminals and the lead wire, and at the time of shell assembly welding. Lead wire is not affected by heat.

Example of Invention

The configuration of an embodiment of the scroll compressor of the present invention will be described below with reference to FIGS. FIG. 3 is a specific example of the case where the scroll compressor is applied to a hermetically sealed refrigerant compressor.

In the figure, (1) is a fixed scroll, (2) is an orbiting scroll, and (104a) is a peripheral wall portion (104c) of the fixed scroll (1).
The suction port formed in the (105) is a fixed scroll (1)
Is a discharge hole formed in the central portion of the. The fixed scroll (1) is composed of a disk-shaped base plate (101), a spiral side plate (102) integrally formed with the base plate (101), and a peripheral wall portion (104c). Similarly, (2) is also formed of a disc-shaped base plate (201) and a spiral side plate (202) integrally formed, and both scrolls (1) and (2) are engaged with each other to form a base plate (101). A compression chamber (P) surrounded by (201) and the spiral side plates (102) (202) is formed. A plurality of the compression chambers (P) are formed, and the pressure chamber at the central portion, which has the highest pressure, communicates with the discharge hole (105). Grooves (103) and (203) are formed on the end faces of the spiral side plates (102) and (202) along the longitudinal direction of the spiral, and the inner ends of the spiral direction are left. A chip seal (3) is fitted in each of 103 and 203 so as to be movable in the axial direction. Also, (4) is the spindle,
(5) is an eccentric bush which gives a pressing force to the orbiting scroll (2) so that the side plates (102) (202) are always in contact with each other even if the spiral side plates (102) (202) are worn, (6) Is an upper frame whose outer peripheral planar shape is almost the same as that of the fixed scroll (1) and whose maximum outer diameter is the same as that of the fixed scroll (1). (7) is an outer peripheral planar shape which is almost the same as the fixed scroll (1). A lower frame having the same maximum outer diameter as that of the upper frame (6), (8) an Oldham coupling, (601) an annular upper thrust bearing which receives the pressure of the compression chamber (P) and the weight of the orbiting scroll, ( 701) is an annular lower thrust bearing that receives the thrust weight of the main shaft (4) and the rotor (10) of the motor, which will be described later, and the main shaft (4), and (602) the radial load of the main shaft (4). This is done with the upper main bearing received at the upper part. In using the bearing metal. Reference numeral (702) is a lower main bearing that receives the radial load of the main shaft (4) at its intermediate portion, and in this embodiment, a bearing metal is used. At the center of the back surface of the base plate (201) of the orbiting scroll (2), an axis (20) whose axis is perpendicular to the back surface of the base plate (201) and which is parallel to the axis of the main shaft (4).
4) is integrally formed, and an eccentric hole (401) having an axis parallel to the axis (rotation center) of the spindle (4) is formed on the upper end surface of the spindle (4), This eccentric hole (401)
An eccentric bush (5) is rotatably fitted in the. The eccentric bush (5) has an eccentric hole (502) which is eccentric with respect to the outer periphery thereof and has an axis parallel to the axis of the main shaft (4). The eccentric hole (502) has the shaft (204). ) Is rotatably inserted. The main shaft (4) has an upper main bearing (602) fixed by press fitting into a through hole (602a) provided in the upper frame (6), and a bearing mounting round hole (7a) formed on the upper surface of the lower frame (7). ), The lower thrust bearing (701) and the lower frame (7) are fixed by press-fitting to the central through hole (7c) of the cylindrical bearing support portion (7b) integrally extending downward from the central portion. The lower main bearing (702) is pivotally supported, and the upper frame (6) and the lower frame (7) have upper main bearings (602) and lower main bearings due to the brazing fittings (67a) (76a). The (702) s are combined so that they are concentric with each other. Also, the upper main bearing (602) and the upper thrust bearing (601) are concentric, and the upper main bearing (602)
Since the radial bearing surface (602b) and the thrust bearing surface (601a) of the upper thrust bearing (601) are vertical, the main shaft (4) has its axis concentric with the axis of the upper thrust bearing (601). Also, it is maintained perpendicular to the thrust bearing surface (601a). Since the orbiting scroll (2) is supported by the upper thrust bearing (601) on the back surface of the base plate (201), the base plate (201) of the orbiting scroll (2) is attached to the spindle (4). On the contrary, it is maintained in a vertical posture. The upper thrust bearing (601) is crimped to the upper frame (6) by a plurality of rivets (603) so that the upper thrust bearing (601) does not move in any of the vertical direction, the horizontal direction, and the circumferential direction in the drawing. It is firmly fixed.
Note that this fixing may be performed with a plurality of flat head screws or the like instead of the ribet (603). Lower thrust bearing (701)
Is the pin (70) planted in the bottom of the bearing mounting round hole (7a).
3) prevents the main shaft (4) from rotating in the rotating direction. In this embodiment, the bearings of each part are (60
1) (602) (701) (702) are in the form of sliding bearings, and therefore, metal bearings are used for these respective bearings, but lower thrust bearing (701) and lower main bearing (702) Since the bearing load is relatively small compared to other bearings (601) (602), when the lower frame (7) is made of a material having a metal bearing function such as cast iron or aluminum casting, Alternatively, the lower frame (7) itself may directly receive the bearing load without providing the lower bearings (701) (702).

The Oldham's joint (8) is a joint means for preventing the orbiting scroll (2) from rotating and allowing the orbiting scroll (2) to only revolve around the axis of the main shaft (4). It is arranged between the base plate (201) of the orbiting scroll (2) and the upper frame (6).

After the above mechanical components are assembled in the above relative relationship, the upper frame (6), the lower frame (7),
The fixed scroll (1) is a plurality of bolts that penetrate the peripheral wall (104c) and the upper frame (6) of the fixed scroll (1) and have a screw part (106a) at the tip screwed only to the lower frame (7). It is fastened together by (106). For supporting the motor for rotating the main shaft (4), the rotor (10) of the motor is fixed to the main shaft (4) by shrink fitting or the like.
0) and a proper air gear gap are secured and adjusted, the stator (11) of the motor is attached to the lower surface of the lower finger-shaped extension (7d) of the lower frame (7) by a plurality of bolts (704). It is fixed. Further, a concave hole (10b) for accommodating the lower end portion of the tubular bearing support portion (7b) with a small gap is formed in the upper end of the central portion of the core portion (10a) of the rotor (10). In the space (7e) between the finger-shaped extension (7d) and the cylindrical bearing support (7b), the upper end of the stator winding (11a) and the upper end ring (10b) of the rotor are Is housed. Further, since the orbiting scroll (2) is eccentric with respect to the axis of the main shaft (4), it is necessary to balance the rotating system. To balance this, the first balancer (402)
Is integrally formed with the main shaft (4), and the second balancer (403)
Is attached to the lower end ring (10c) of the rotor (10). The first balancer (402) is the spindle (4)
Alternatively, the second balancer (403) may be formed integrally with the lower end ring (10c). An oil cap (12) for supplying oil by a centrifugal pump action is shrink-fitted and press-fitted to the lower end of the main shaft (4). Reference numeral (7h) is a partition wall provided so as to close one of the gas passages (614b) on the outer periphery of the lower frame (7). A mechanical part (13) in which the above mechanical parts are assembled in a relative relationship as described above, that is, a fixed scroll (1), an orbiting scroll (2), an upper frame (6), a lower frame (7), a spindle ( 4), rotor (1
0), the assembly of the stator (11) and the like are fixed in the shell intermediate cylindrical portion (901) at the outer periphery of the lower frame (7) by shrink fitting or spot welding, and the shell upper lid (902) and shell bottom lid (903). ) Is on both end faces of the shell intermediate cylindrical part (901) as shown in the figure.
A shell, that is, a closed container (9) is formed by fitting them so as to cover the outer peripheral portion of (01) and welding and sealing these fitting portions (902a), (903a). When fixing the mechanism portion (13) in the shell intermediate cylindrical portion (901), a step portion (7f) is formed over the entire outer peripheral portion of the lower frame (7) to facilitate axial positioning. In addition, the stepped portion (901a) is formed so as to come into contact with the stepped portion (7f) over the entire circumference of the inner peripheral portion of the shell intermediate cylindrical portion (901). Shell intermediate cylindrical part (901)
The stepped portion (901a) is formed by cutting with a pipe expanding by a press or a lathe. (904) is a closed container (9)
Evaporator (not shown) via external suction pipe (not shown)
A suction pipe for sucking the low-pressure refrigerant inside the closed container (9), and (905) a discharge pipe (not shown) for discharging the high-pressure refrigerant inside the compression chamber (P) at the highest pressure outside the closed container (9). A discharge pipe for discharging to a condenser (not shown) through a pipe, and (906) is a process pipe, which is used for vacuuming the shell, filling oil in the shell, and filling gas in the shell. It is something.
(907) is a sealed terminal, (908) is a terminal box, (909) is a lubricating oil reservoir, (910) is a foaming prevention plate, (911) is four compressor mounting feet, and the shell bottom cover (908) is They are attached to the outer bottom surface at equal intervals in the circumferential direction. Inhalation tube (90
4) is connected to the peripheral wall of the shell intermediate cylindrical portion (901) by welding or the like, and opens to the low pressure space (912) in the closed container (9). The discharge pipe (905) penetrates the central portion of the shell upper lid (902), is hermetically connected to this central portion, and further extends so as to communicate with the discharge hole (105) of the fixed scroll (1). At the joint between the discharge pipe (905) and the fixed scroll (1), a sealing means is provided so that the low pressure space (912) in the closed container (9) does not communicate with the discharge pipe (905) or the discharge hole (105). Is provided with a 0 ring (107). As the sealing means, the discharge pipe (905) may be press-fitted into the communication hole (1a) of the fixed scroll (1) instead of the O-ring. When using the O-ring (107), the discharge pipe (905) is welded to the shell upper cover (902) by the heat generated by welding.
In order to prevent deterioration of the ring (107), while fitting the discharge pipe (905) into the communication hole (1a) while welding the discharge pipe (905) to the shell cover (902) in advance, the shell cover (9
02) is welded by fitting it to the shell intermediate cylindrical portion (901), or the shell upper lid (902) having the discharge pipe holding pipe (913) protruding outside the shell upper lid (902) is attached to the shell intermediate cylindrical portion (901). After welding to the pipe, it is preferable that the discharge pipe (905) is inserted into the communication hole (1a) through the holding pipe (913) and the joint between the holding pipe (913) and the discharge pipe (905) is brazed. . The discharge pipe (905) is press-fitted into the communication hole (1a) without using the O-ring (107), or the discharge pipe (905) is formed of a soft material such as a copper pipe.
After fitting into the discharge pipe (905), a hard pipe is press-fitted into the discharge pipe (905) to expand the discharge pipe (90), and the discharge pipe (90) is inserted into the communication hole (1a).
5) It is not impossible to connect airtightly.

The hermetically sealed terminal (907) is welded to the shell upper lid (902), and the hermetically sealed terminal (907) and the stator winding (11a) of the motor / stator (11) are connected to the low pressure space (912) in the hermetically sealed container (9). ) Is electrically connected by a lead wire (not shown). The low-pressure space (912) in the closed container (9) includes a fixed scroll (1), an upper frame (6) and a lower frame (7).
The assembly of the upper space (912a) and the lower space (912a)
b), and the upper space (912a) and the lower space (912b) are separated from each other by the main shaft (4) on the outer circumferences of the fixed scroll (1), the upper frame (6) and the lower frame (7). The pressure is equalized by a series of notch passages (14) provided in parallel with the axis of the. In addition, the notch passage (1
4) is fixed scroll (1), both frames (6)
A plurality of (7) are provided on each outer periphery at equal intervals in the circumferential direction. Furthermore, the inlet (10) of the fixed scroll (1)
4a) is the fixed scroll (1) and both frames (6)
(7) communicates with the upper space (912a) and the lower space (912b) through a plurality of notch passages (14).
In order to reduce the refrigerant flow resistance in the cutout passage (14) as much as possible, the cutout passages (14) are provided as many as possible, and the fixed scroll (1) and the outer peripheral portions of both frames (6) and (7) are flat. It is preferably shaped like the teeth of a gear.

Next, the configuration of the oil supply path will be described. The lubricating oil sump (909) is located in the lower part of the lower space (912b) in the closed container (9), and the lower end of the main shaft (4) and the oil cap are immersed in the oil (909a) in this lubricating oil sump (909). (12) is immersed.
(910) is a disc-shaped anti-foaming plate that is located above the lubricating oil sump (909) and is fixed to the outer peripheral surface of the shell intermediate cylindrical portion (901) by spot welding or the like on the inner peripheral surface. , The pressure in the low-pressure space (912) suddenly drops when the compressor starts, and the lubricating oil (909a) is generated by the rotation of the main shaft (4).
The well-known forming development that occurs when the toner is agitated is prevented. A hole (910) for the main shaft (4) to penetrate is formed in the center of the foaming prevention plate (910).
a) is provided.

Reference numeral (404) is an oil passage which is formed by penetrating the main shaft (4) along the axial center of the main shaft (4) at a position eccentric to the main shaft (4) so as to penetrate through both upper and lower ends of the main shaft (4), and the lower end of the main shaft (4). Is opened in the oil cap (12) at the lower end surface of the shaft, and the other end is opened at the upper end of the spindle (4) at the bottom of the eccentric hole (401) to connect the eccentric hole (401) and the lubricating oil sump (909). It is in communication. In addition, the oil passage (4
In the middle of 04), to lubricate the sliding surface of the lower main bearing (702), the spindle (4) has a radial oil hole (405) communicating the oil passage (404) with the outside of the spindle (4). Is provided.
Further, in order to reliably supply oil to the sliding surface of the lower main bearing (702), the oil hole (40) should face the oil hole (405).
An oil groove (702a) is provided on the inner peripheral surface of the lower main bearing (702) along the entire circumference at the same height as 5).
Further, from the bottom of the eccentric hole (401) to the lower thrust bearing (70
An oil hole (406) for supplying oil to 1) is formed in parallel with the oil passage (404) at the bottom of the eccentric hole (401) of the main shaft (4). Further, (407) is a gas vent hole which is formed so as to extend from the central portion of the lower surface of the main shaft (4) to the outer peripheral surface. (604)
Is an oil drain hole formed vertically through the upper frame (6), and is an Oldham coupling (8) formed by the upper frame (6) and the base plate (201) of the oil scroll (2). And the balancer chamber (705) for storing the first balancer (402) formed by the upper frame (6) and the lower frame (7) are communicated with each other.

Reference numeral (706) is an oil drain hole, which is formed by the vertical groove (7g) provided on the outer periphery of the lower frame (7) and the inner peripheral surface of the shell intermediate cylindrical portion (901), and which serves as a balancer chamber. (70
The low pressure space (912) in the closed container (9) communicates with 5).

The operation of the scroll compressor configured as described above will be described below. Motor stator (1) through sealed terminal (907)
When electricity is applied to 1), the motor-rotor (10) generates torque and rotates with the main shaft (4). When the main shaft (4) starts to rotate, the main shaft (4) rotates to the shaft (204) of the orbiting scroll (2) through the eccentric bush (5) fitted in the eccentric hole (401) of the main shaft (4). The force is transmitted, and the orbiting scroll (2) is guided by the Oldham coupling (8) to make an orbital motion around the axis of the main shaft (4) without rotating, and as shown in FIG. Various compression actions are performed in the compression chamber (P). At this time, the spiral side plates (102), (2
At the tip end surface of 02), the chip seal (3) is brought into contact with the base plates (101) and (201) respectively, so that the leakage of the compressed refrigerant from the relatively high pressure compression chamber to the low pressure compression chamber is spiral. The side surfaces of the spiral side plates (102) and (202) are prevented from being generated at the tip end surface portions of the side plates (102) and (202), and the centrifugal force generated by the eccentric rotation motion of the orbiting scroll (2), etc. Is used to swing the eccentric bush (5) around the axis (204) of the orbiting scroll (2), and the eccentric amount of the orbiting scroll (2) with respect to the axis of the main shaft (4) is made variable. Thus, the leakage of the compressed refrigerant from the relatively high pressure compression chamber to the relatively low pressure compression chamber is prevented from occurring in the spiral direction between the side surfaces of the spiral side plates (102) and (202). . Next, the flow of the refrigerant gas will be described. The suction refrigerant gas from the evaporator (not shown) flows into the low pressure space (912) in the shell through the suction pipe (904),
The motor / rotor (10), the motor / stator (11), etc. are cooled and the suction port (10) is passed through the cutout passage (14).
4a) is taken in, taken into the compression chamber (P), compressed, and then discharged into the high pressure refrigerant gas through the discharge hole (105) through the discharge pipe (905) to the outside of the closed container (9) and condensed. To a container (not shown).

Next, the oil supply system will be described. The oil in the lubricating oil sump (909) is pumped to the eccentric hole (401) through the oil cap (12) and the oil passage (404) by the centrifugal pump action generated by the rotation of the main shaft (4). , The eccentric bush (5) is refueled. Oil is supplied to the lower main bearing (702) through the oil hole (405) and oil is supplied to the lower thrust bearing (701) through the oil hole (406). Further, the oil that lubricates the eccentric bush (5) through oil grooves, oil holes (not shown) provided in the eccentric bush (5) and the main shaft (4),
The upper main bearing (602) is lubricated and then reaches the upper thrust bearing (601). After lubricating the upper thrust bearing (601), it is discharged into the Oldham chamber (605). Here, the lubricating oil further lubricates the Oldham coupling (8) and then the oil drain hole (60
After passing through 4), the oil is discharged downward through the oil drain port (706), then through the foaming prevention plate (910), and again the lower lubricating oil sump (9
Return to 09). The gas vent hole (407) is provided in order to quickly discharge the gas in the oil cap (12) to the outside so as to accelerate the responsiveness of the pump and increase the pump efficiency.

Furthermore, when the compressor is started, the space inside the closed container (9) (912)
The pressure of the oil decreases and the oil in the lubricating oil sump (909) rapidly forms and mixes with the refrigerant gas, causing a large amount of oil to flow from the suction port (104a) into the compression chamber (P). Since the oil in the lubricating oil sump (909) will be instantly depleted if it is discharged together with the gas as it is, a foaming prevention plate (910) is provided to prevent this depletion. In order to cause this prevention function, the anti-foaming plate (910) is filled with the oil that has lubricated the bearings and the Oldham coupling (8) after being pumped by the oil pump action as described above. Although an oil return passageway (910b) necessary for returning to 909) is secured, the effective area of this oil return passageway (910b) is made small so that a large amount of oil does not pass instantly.

Next, the structure of the fixed scroll (1) will be described in detail with reference to FIG. 4 (a) is a top view, FIG. 4 (b) is a bottom view, and FIG. 4 (c) is a cross-sectional view of the cross-section taken along the line CC of FIG. Fixed scroll (1) in the figure
A spiral groove (108) is formed on the lower surface of the base plate (101) of the base plate, and as a result, the spiral side plate (102) extending vertically below the base plate (101) becomes the base plate (101). It is integrally formed.
Here, the spiral center (O _S ) of the spiral side plate (102) is the base plate (101).
The center of the (O _S) and the match. In addition, the end face of the spiral side plate (102), that is, the orbiting scroll (2) as can be seen from FIG.
The side plate (10) of the spiral side plate (10
A chip seal groove (103) is formed along the spiral shape of 2). The chip seal groove (103) does not extend to the start (center) and end of the spiral. That is, the chip seal groove (103) is the end (103a) before the start and end of the spiral.

On the outer periphery of the base plate (101), a large number of recesses (109) serving as refrigerant gas passages are formed at equal intervals over the entire length in the vertical direction, that is, the axial direction, and one of them (109a) is spiral. The groove (108) communicates with the outermost peripheral end of the groove (108), and the recess (109b) is at a position 180 ° C opposite to the recess (109a).
Also communicates with the groove portion (108) at that position, and these communicating portions serve as two suction ports (104a) (104b). Each of the recesses (109) is formed as deep as possible in the radial direction (d) to the extent that it does not hinder compression, and as a result, is provided along the outer periphery of the spiral groove (108). There is. That is, the outer peripheral surface (108) of the groove (108)
The thicknesses (t) between c) and the radial bottom surface (109c) of the recesses (109) are the same. In addition, the concave portion (109)
Fixed scroll (1) on each of the protrusions (110) between
There is provided a bolt hole (111) through which a bolt (not shown) having a tip screwed into the lower frame (7) is inserted to fix the bolt to the lower frame (7). Furthermore, each convex portion (11
The radial height (d) of 0) is set so that the virtual circle connecting the radial outer surfaces (110a) becomes a perfect circle. Further, on the upper surface of the base plate (101), a large number of radial reinforcing ribs (112) extending radially outward from the outer peripheral surface of the boss portion (101a) around the central discharge hole (105) are arranged at equal intervals. Further provided is a substantially spiral reinforcing rib (113) that continuously connects the radially outer ends of the radial reinforcing ribs (112) along the spiral groove (108) in the circumferential direction. . In other words, the reinforcing ribs (113) are closed in a substantially spiral shape according to the circumferential arrangement of the recesses (109). In addition, the outer peripheral surface of the reinforcing rib (113) and the bottom surface (109c) of each recess (109).
And the distances (l) are the same. By providing the reinforcing ribs (112) and (113) having the above-described structure, the base plate (101) can be made thinner while maintaining strength and rigidity. (114) is a fixed scroll (1)
Are three projections that are checked to fix the fixed scroll (1) when processing the side surface of the spiral side plate (102), that is, the peripheral surface. (112) extend in the extending direction, that is, radially outward, and are arranged at equal intervals in the circumferential direction. (115)
Extends circumferentially on the inner peripheral surface of the discharge hole (105) in order to fit a 0 ring (107) that seals the outer peripheral portion of the discharge pipe (905) and the inner peripheral portion of the discharge hole (105). It is a circular groove provided by.

FIG. 4 (d) shows a state in which the fixed scroll (1) and the orbiting scroll (2) are combined, and as is clear from FIG. 4 (d), two suction ports (104a )(Ten
In 4b), the spiral side plate (102) of the fixed scroll (1) contacts the spiral side plate (202) of the orbiting scroll (2) 2
The two outermost peripheral ends Aa, Ab open toward the outside of the outer peripheral end of the spiral side plate (102). Since the two suction ports (104a) (104b) are open at such positions, the two symmetrical pressure chambers (Pa) (Pb) end closing at the same time, so the compression unbalance during compression Can be eliminated. A
Reference characters a, Ab, A2, and A3 are contact portions of both spiral side plates (102) (202).

Next, the structure of the orbiting scroll (2) will be described in detail with reference to FIG. FIG. 5 (a) is a top view, (b) is a side view, and (c) is a bottom view. In the figure, a spiral groove (201a) is formed on the upper surface of the base plate (201) of the orbiting scroll (2).
Thus, the spiral side plate (202) is integrally formed, and the swing shaft (204) is integrally formed on the lower surface. Here are coincident with the center of the spiral plate (202) (O _Bi) centered (O _Bi) and the pivot shaft of the base plate (201) (204) of the axis (O _Bi). The base plate (201) has a disk shape, and the outer peripheral surface of the outermost peripheral end (205) of the spiral side plate (202) is positioned so as to be substantially in contact with the outer peripheral surface of the base plate (201). Has a fixed diameter. Where spiral side plates (202)
If the center of gravity of is not aligned with the centers of the base plate (201) and the swing shaft (204), static imbalance occurs. Therefore, the center of gravity of the orbiting scroll (2) is made to coincide with the axis O _Bi of the orbiting shaft of the orbiting scroll (2) so that this static imbalance does not occur. A notch (206) is provided in a part of the inner circumference of the spiral side plate (202), and the radial thickness of a part (207) of the outermost peripheral part that does not contribute to the compression of the spiral side plate (202) is made thinner than the radial thickness of the other part. There is. In addition, when it is possible to prevent the static imbalance from occurring only by the notch (206), a part (207) of the spiral side plate (202) does not have to be thinned.

Reference numeral (208) is a guide groove of the Oldham coupling (8).
The guide grooves (208) are provided as a pair at symmetrical positions with respect to the orbiting shaft (204), and the base plate of the orbiting scroll (2) is provided at a site other than the site where the notch (206) is provided. (201) is arranged on the outer peripheral portion of the lower side surface.

Reference numeral (209) is a step portion provided on the outer peripheral portion of the upper surface of the base plate (201), and as shown in FIG.
When processing 2) by milling, the outer periphery of the base plate (201) is pressed in advance by the ring-shaped holding plate (210) and the orbiting scroll (2) is attached to the flat plate-shaped mounting jig (211). It is for mounting and fixing the base plate (20) as compared with other checking means for mounting and fixing the orbiting scroll by pressing and processing the outer peripheral portion in this manner.
The deformation of 1) can be almost eliminated, and the spiral part can be processed with high accuracy. At this time, since it is preferable to uniformly press the base plate (201) over the entire circumference, the notch (206) is divided into a plurality of pieces, and the plurality of notches (206) (206) are projected. The part (212) is left so that it can be held down in this part as well. As shown in FIG. 6, a groove (213) is provided on the peripheral surface of the base plate (201) instead of the step (209), and the groove (213) has a ring shape in FIG. 5 (b). A plurality of holding plates arranged in a ring shape may be inserted like the holding plate (210).

Further, (214) is a hollow portion formed coaxially with the swing shaft (204), and as a result, the swing shaft (204) has a cylindrical shape. By providing the hollow portion (214), the weight of the orbiting scroll (2) is reduced, the weight of the portion that needs to be balanced is reduced, and the centrifugal force is reduced.

(203) is a chip seal groove, and is a spiral side plate (202).
Is formed along the spiral shape of the side plate (202) on the end face of the. As shown in FIG. 5 (a), the end of the groove (203) is located on the inner peripheral side of the spiral side plate (202), which is thinned by cutting the outer peripheral surface of the spiral side plate (202) for balancing. (2
Starting from 15), the terminal end is located at a portion (216) that does not interfere with the discharge hole (105) provided on the fixed scroll (1) side. Chip seal groove (10
3) also the chip seal groove (203) on the orbiting scroll (2) side
And the shape correspond.

FIG. 7 is a perspective view when the spiral chip seal (3) is assembled into the orbiting scroll (2). Reference numeral (301) denotes a plurality of coil-shaped springs for axially urging the chip seal (3). After these springs are inserted into the chip seal groove (203), the chip seal (3) is inserted into the chip seal groove (20).
3) Insert inside. Therefore, the plurality of springs (301) are placed in the chip seal groove (203) and sandwiched between the bottom surface of the chip seal groove (203) and the back surface of the chip seal (3). The fixed scroll (1) has the same structure.

8 (a) is a top view of the upper frame (6), and FIG. 8 (b) is a sectional view of the section taken along line bb of FIG. 8 (a), viewed in the direction of the arrow. In the figure, (600a) is the bottom,
(600b) is a peripheral wall, (600c) is a recess, (602) is an upper main bearing, (606) is an upper thrust bearing (601) shown in FIG.
Is a mounting seat formed on the upper surface of the bottom portion (600a).
(607) Oldham guide groove, (608) Oldham ring sliding surface, (604) oil drain hole, (609) relief groove, (61)
(0) is a riveting hole, (611) is a counterbore, (612) is a fixed scroll fixing surface, (613) is a bolt hole, and (614) is a recess.

A large number of recesses (614) corresponding to the recesses (109) of the outer periphery of the fixed scroll (1) shown in FIG. The drilled bolt hole (613) is also provided corresponding to the bolt hole (111) of the fixed scroll (1).

The structure of the upper frame (6) will be described in detail. A fixed scroll fixing surface (612) is provided on the upper end surface of the peripheral wall portion (600b).
However, the bottom portion (600a) has an upper thrust bearing mounting seat (606) at a position lower than the fixing surface (612), and further between the peripheral wall portion (600b) and the upper thrust bearing mounting seat (606). The Oldham ring sliding surfaces (608) are arranged concentrically at positions lower than the mounting seat (606). The vicinity of the Oldham ring sliding surface (608) becomes an Oldham chamber (605) that houses the Oldham coupling (8).

The upper main bearing (602) is press-fitted into the inner peripheral surface of the mounting seat (606), that is, the through hole (602a). 615), so that the upper main bearing (602) overhangs on the chamfered portion (615) on the upper end side. Here, the end surface of the chamfered portion (615) is the inner peripheral surface (606a) of the mounting seat (606), and (606b) is the outer peripheral surface of the mounting seat (606).

The Oldham guide groove (607) has a pair of symmetrically placed positions across the upper main bearing (602), and the Oldham ring sliding surface (608).
It is provided above, and semicircular relief portions (607a) (607b) are provided at both ends in the radial direction. In particular, the relief portion (607b) is formed by partially engraving the outer peripheral portion of the annular mounting seat (606).

The Oldham guide groove (607) is sandwiched in between, and one end of the Oldham ring sliding surface (608) is opened and the other end is in contact with the outer peripheral surface of the mounting seat (606) on both sides of the balancer chamber (70).
5), four oil drain holes (604) opened,
Further, as clearly shown in FIG. 8 (a), these oil drain holes (604) are provided with a pair of relief grooves (60 having a C-shape when viewed from above).
It communicates with 9). The relief groove (609) is formed on the Oldham ring sliding surface (608) of the upper frame (6).

FIG. 9 shows the structure of the upper thrust bearing (601),
(A) is a top view, (b) is a cross-sectional view of the cross section taken along line bb of (a) in the direction of the arrow, (c) is cc of (a).
It is sectional drawing which expands and shows the cross section in a line.

The upper thrust bearing (601) is a sliding bearing such as an aluminum alloy or lead bronze alloy with a steel backing, and has a donut shape as shown in FIG. ) Sliding surface with the lower surface, that is, the upper surface (601
In a), a plurality of oil grooves (601b) are radially provided from the inner circumference side to the outer circumference side at equal intervals. The cross-sectional shape of the oil groove (601b) is substantially rectangular as shown in FIG. 8 (c), and the corners are chamfered so as to form curved surfaces, and the sag portion (601c) is provided in an R shape to form a sliding surface ( 601a) makes it easy for oil to spread over the entire surface. The pitch of the oil groove (601b) is provided in a range smaller than twice the revolution radius R of the sliding scroll (2). (601d) is the thrust bearing (60
1) Rivet hole for mounting, which intersects with part of the oil groove (601b).

The outer diameter of the thrust bearing (601) is such that the vector of the resultant force is at least from the outer peripheral end of the thrust bearing (601) so that it can receive the overturning moment due to the resultant force of the radial force and the axial force generated in the orbiting scroll (2). It is decided to pass the center side. Where (601e) is the thrust bearing (60
It is the inner peripheral surface of 1), and (601f) is the outer peripheral surface of the thrust bearing (601).

FIG. 10 to FIG. 12 are views for explaining the detailed structure of the Oldham coupling in one embodiment. FIG. 10 (a) is a top view of the Oldham's joint, and FIG. 10 (b) is a sectional view of the section taken along the line bb of FIG. In the figure, (801) is an Oldham ring having a rectangular cross section as clearly shown in FIG. 10 (b), (802) is a pair of rectangular parallelepiped Oldham keys, and (803) is an Oldham ring (801). Are two pairs of relief portions formed in a groove shape on the upper and lower surfaces of the. Upper pair of Oldham key (802) is fixed to the Oldham ring Oldham ring sandwiching the center O _R of the (801) (801) upper relief portion at symmetrical positions on the surface (803) within, The pair of lower Oldham keys (802) is located on the lower surface of the Oldham ring (801) at a position offset by 90 ° in the circumferential direction from the position of the pair of Oldham keys (802) on the upper side. 803)
It is stuck inside. Since each Oldham key (802) and each Oldham ring (801) are made of hardened steel, their sliding surfaces, f _K and f _R, are polished for accuracy. Therefore, the relief part (80
3) is provided on the upper and lower surfaces of the Oldham ring (801) as a joint with the Oldham key (802). Also, each Oldham key (802) is to the Oldham ring (801),
All of them are fixed so that they protrude toward the center O _R side. (802b) is a part of each Oldham key (801) protruding from the Oldham ring (801) by shifting in this way.

Oldham Key (802) and Oldham Ring (801)
Are made separately, and are integrally joined to each other by welding or the like. Figure 11 shows such an Oldham Key (80
In the perspective view of 2), a protrusion (802a) is provided on a portion of the Oldham ring (801) that abuts on the joint surface (801a), and the welding strength is improved when joining by electric resistance welding or the like. It can be held. FIG. 12 is a perspective view showing a state where each Oldham key (802) is attached to the Oldham ring (802). The Oldham key (802) and the Oldham ring (801) individually made as described above are the Oldham ring. Two pairs of upper and lower relief portions (803) of the (801) are provided with protrusions (802) of each pair of Oldham keys (802) from the upper side and the lower side.
They are welded to each other with a) contacted. Two pairs of upper and lower Oldham keys (802) are arranged such that a line connecting the upper Oldham keys (802) and a line connecting the lower Oldham keys (802) are orthogonal to each other.

FIG. 13 is a top view of the upper frame (6) with the thrust bearing (601) and Oldham coupling (8) incorporated, and FIG. 14 is the orbiting joint (8) of the orbiting scroll (2). ) Is a view of the combined state viewed from the lower surface.

In FIG. 13, the flat annular thrust bearing (601) is caulked to the upper surface of the mounting seat (606) of the upper frame (6) by a riveting (603). Here, the inner peripheral surface (601e) of the thrust bearing (601) is attached to the mounting seat (6
Overhang the center O _S side of 06) in the peripheral surface (606a) (60
1g) and the outer peripheral surface (601f) is overhung (601) outside the mounting seat (606) outer peripheral surface (606b) indicated by the dotted line.
h) Yes.

In the Oldham coupling (8), a pair of Oldham keys (802) on the lower side are slidably fitted in the guide grooves (607) having a rectangular cross section on the upper surface of the upper frame (6).
While being guided by the guide groove (607), it reciprocates laterally in the figure. Also, another pair of upper Oldham keys (80) provided on the upper surface of the Oldham ring (801).
2) is swingably fitted in the guide groove (208) of the orbiting scroll (2) shown in FIG. 5 (c). This state is first
Shown in Figure 4. In FIG. 14, the orbiting scroll (2) reciprocates relative to the Oldham coupling (8) in the longitudinal direction while being guided by the Oldham key (802) in its guide groove (208). When the orbiting scroll (2) is driven, the two reciprocating motions are combined, and as a result, the rotation motion is blocked and only the revolution motion is performed.

At this time, it is understood that the range of relative reciprocating motion of the Oldham coupling (8) with respect to the upper frame (6) and the orbiting scroll (2) is the orbital diameter 2R of the orbiting scroll (2).

Therefore, the length L of the linear portion in the longitudinal direction of the guide groove (607) of the upper frame (6) can be L ≧ l + 2R, where l is the length of the Oldham key (802). It is practically difficult to form the guide groove (607) so that the planar shape of the guide groove (607) can be made rectangular by making the corners of (607) right angles. Therefore, as shown in FIG. 13, relief surfaces (607a) (607b) having a semicircular planar shape are provided on the surfaces at both ends in the radial direction. In addition, the groove width of the guide groove (607) and the relief part (607b)
The diameter of the relief part (607a) is the same.
When the Oldham key (802) reciprocates, the Oldham groove (6
It prevents the possibility of biting into 07). In addition, Oldham
The outer diameter D _O (FIG. 10) of the ring (801) is substantially equal to the outer diameter D _S (FIG. 5) of the orbiting scroll. Also, the inner diameter Di (Fig. 10) of the Oldham ring (801) is as shown in Fig. 13, when the Oldham ring (801) is maximally offset to one side, the inner peripheral surface (801c) of the Oldham ring (801c). ) Is close to the outer peripheral surface (601f) of the thrust bearing (601), it is determined to have a slight gap g ₁ (0.5 to 1 mm) between both peripheral surfaces (801c) (601f). At this time, at the position 180 ° opposite to the gap g ₁ , the upper frame (6)
The Oldham chamber (605) peripheral wall surface (605a) is also close to the Oldham ring (801) outer peripheral surface (801b), and a slight gap g ₂ is provided between both peripheral surfaces (605a) (801b). (0.5-1mm), Oldham ring (801) outer diameter D _O
Can be decided. By doing so, the outer diameter of the upper frame (6) can be reduced, and the compressor can be downsized in the radial direction. Further, by providing each of the Oldham keys (802) so as to project inward in the radial direction from the inner peripheral surface (801c) of the Oldham ring (801) in a plan view, by providing the protruding portion (802b), For example, as shown in FIG. 13, it is possible to prevent the terminal corner portion of the Oldham key (802) from interfering with the peripheral wall of the semicircular relief portion (607a) of the guide groove (607) on the outer peripheral side of the Oldham ring (801), and also the Oldham. Ring (801)
On the inner peripheral side, the protruding portion (802b) of the Oldham key (802) overlaps directly under the outer peripheral overhang portion (601h) of the thrust bearing (601), so that the load surface of the Oldham key (802) can be made large. Further, by providing the protruding portion (802b), as shown in FIG. 14, when the Oldham ring (801) is shifted to one side to the maximum extent, the Oldham key (802) and the guide groove (20) of the orbiting scroll (2) are provided.
Since the sliding load surface with 8) can be taken large, the reliability of the sliding surface can be improved.

Next, the lubrication of the thrust bearing (601) will be described. Thirteenth
In the figure, the oil supplied to the oil groove (601b) of the thrust bearing (601) from the radially inner side flows radially outward along each radial oil groove (601b) as indicated by the broken line arrow.
On the other hand, at the time of operation of the orbiting scroll (2), a certain point on the thrust surface of the orbiting scroll (2) crosses one of the orbiting grooves (101b) as shown by arrow a, and the orbiting scroll (2) is moved. Orbit the diameter by 2R, and at some other point, cross the adjacent oil groove (601b) as shown by the arrow B
Orbit for 2R. Here, the pitch in the circumferential direction between the oil grooves (601b) is smaller than the revolution diameter 2R of the orbiting scroll (2), and as a result, the two arrows a and b overlap each other. As can be seen from the above, the thrust bearing sliding surface (60) sandwiched between two adjacent oil grooves (601b)
1a) is always supplied with oil from the oil grooves (601b) on both sides, so good lubrication is maintained. Further, the oil groove (601b) in the thrust bearing (601), the riveting mounting hole (601d), and the portion (601) where the Oldham guide groove (208) of the orbiting scroll (2) and the thrust bearing (601) overlap.
j) (Fig. 14) is where the oil film reaction force does not occur and bearing load capacity is not present. Therefore, as shown in FIG. 14, the ribet mounting hole (601d) and a part of the oil groove (601b) are intersected with each other, and the intersecting part and the guide groove (208) of the orbiting scroll (2) are connected. By overlapping,
It is possible to prevent the load capacity of the thrust bearing (601) from decreasing as much as possible. That is, since the oil groove (601b) is a portion where the oil film reaction force is not originally generated, the oil groove (601b) portion where the oil film reaction force is not generated is a riveting mounting hole (601d) where the oil film reaction force is not generated. (3) and the overlap portion (601j) are concentrated, the decrease in load capacity of the thrust bearing can be suppressed as much as possible.

The oil discharged radially outward from the thrust bearing (601) flows into the Oldham chamber (605) to lubricate the Oldham coupling (8), and then is drilled at the bottom of the Oldham chamber (605).
The oil is discharged into the balancer chamber (705) through the individual oil drain holes (604). Here, from FIG. 13, the oil drain hole (604) and the oil drain hole (604)
The relief groove (609) that communicates with the outer peripheral surface (801) of the Oldham ring (801) regardless of the position of the Oldham ring (801).
It can be seen that it is located closer to the inner side in the radial direction than b). The relief grooves (609) and the oil drain grooves (604) are arranged in this way so that the oil discharged radially outward from the thrust bearing (601) part is the same as the diameter of the Oldham coupling (8). Flowing out to the outside, as shown in FIG.
This is to prevent it from being discharged to the outside of the compressor as it is while flowing into the compression section suction port (104). Of course, the clearances between the upper frame (6), the Oldham coupling (8), and the orbiting scroll (2) are made small so as to minimize the outflow of oil.

That is, FIG. 15 shows the gaps between the above parts, and the base plate (201) of the orbiting scroll (2) and the Oldham ring (80) are shown.
1) gap between the Oldham key (802) and the guide groove (607) of the upper frame (6) and the bottom of the guide groove (607) of the upper frame (6)
08) The gap γ between the bottom and each is very small (about 0.1 mm)
It is set to be.

FIG. 16 shows the structure of the main shaft (4), (a) is a cross-sectional view from the side before mounting the first balancer (402), (b) is an external view thereof, and (c) is the first balancer (402). ) Is an external view seen from the side when the device is attached. Further, FIG. 17 is a top view of the state where the eccentric bush (5) is not inserted, that is, a view seen in the F direction in FIG. 16 (c).

The main shaft (4) is made of, for example, hardened steel, and the first balancer (402) is made of casting, and is firmly attached to the main shaft (4) by press fitting, shrink fitting, or the like.

In the figure, (408) is the upper spindle sliding surface formed on the outer circumference of the maximum diameter portion of the spindle (4), (409) is the lower spindle sliding surface formed on the outer circumference of the intermediate portion of the spindle (4), (410 ) Is a lower thrust shaft sliding surface formed on the lower surface of the maximum diameter portion of the spindle (4), (411) is the first balancer press-fitting portion formed below the maximum diameter portion of the spindle (4), and (412) is The motor / rotor press-fitting part formed in the lower part of the main shaft (4), (413) the oil cap press-fitting part formed in the lowermost end part of the main shaft (4), and (401) the maximum diameter part of the main shaft (4). An eccentric hole formed in the upper end, (404) an oil passage formed in the main shaft (4), (4
05) (406) and (414) are oil holes, (415) is an oil groove whose upper end is open on the upper surface of the spindle (4), (407) is a gas vent hole formed in the spindle (4), and (416) Is the center hole, (417) is the snap ring groove formed on the peripheral wall of the eccentric hole (401), (4)
18) is a pin hole, and (419) is a step portion formed in the first balancer (402) in a boss shape.

The first balancer press-fitting portion (411) is formed with a diameter smaller than the diameter of the upper spindle sliding surface (408), and the stepped portion (411a) having a difference in diameter is used to press-fit the first balancer (402). The axial position of (402) is restricted. Further, the diameter of the lower spindle sliding surface (409) is smaller than the diameter of the first balancer press-fitting portion (411), and the stepped portion having the difference in this diameter, that is, the lower surface of the first balancer press-fitting portion (411), is attached to the lower thrust shaft. Sliding surface (41
0) has been formed. In addition, the motor / rotor press-fitting part (41
The diameter of 2) is made smaller than the diameter of the lower spindle sliding surface (409), and the stepped portion (412a) of this difference in diameter is used to similarly insert the motor rotor (10) (Fig. 3) into the motor rotor. The axial position of is regulated. This can be dealt with by changing the length below the motor / rotor press-fitting part (412) when making the compressor capacity series.

The sliding surfaces (408) (409) (410) and the press-fitting portions (41)
1) (412) and (413) are formed to have the same axial center, and the eccentric hole (401) and the oil passage (404) are located at positions eccentric to this axial center.
Are formed in parallel with the axis.

The eccentric hole (401) is bored at the upper end of the maximum diameter portion of the spindle (4), and the axial depth thereof is the upper spindle sliding surface (408).
It is almost the same as the axial length of. The oil passage (404) has an upper end opening to the bottom surface of the eccentric hole (401) and a lower end opening to the lower end surface of the maximum diameter portion of the main shaft (4), and moreover in the radial direction from the shaft center of the main shaft (4). It extends vertically at a position spaced a predetermined distance outward.

In addition, a center hole (41
6) is formed and is used for rotatably instructing the spindle (4) during machining of the spindle (4), especially during polishing after quenching, so as to improve the working accuracy. The center hole (416) on the side of the smallest diameter portion is concentrically connected to the lower end of the gas vent hole (407).

The oil hole (414) is bored in the main shaft (4) in a radial direction so as to connect the side wall surface of the eccentric hole (401) and the upper main spindle sliding surface (408), and the oil hole (414) is attached to the main shaft sliding surface. The outer end in the radial direction is open to the oil groove (415) formed to extend in the axial direction of the moving surface (408). The oil hole (405) is connected to the oil passage (40
4) to connect the lower spindle sliding surface (409). The oil holes (404) (414) and the oil groove (415) are usually provided on the side opposite to the load direction, which is the resultant force of the centrifugal force and the gas force. An oil groove may be provided on the inner circumferential surface of the bearing in the circumferential direction, and the oil groove may be communicated with the oil holes (405) and (414) to supply oil to the bearing.

The pin hole (418) prevents the eccentric bush (5) fitted in the eccentric hole (401) from excessively rotating to prevent compression failure, which will be described later.
Is inserted in the bottom surface of the eccentric hole (401).

The snap ring groove (417) is a snap ring (421) described later for preventing the eccentric bush (5) from being pushed upward in the axial direction by the oil pressure of oil that has risen from the oil passage (404) due to the centrifugal pump action. (No. 19
(Fig.).

FIG. 18 is a diagram showing in detail the structure of the eccentric bush (5) inserted into the eccentric hole (401) of the main shaft (4), (a) is a top view, (b) is a side sectional view, (c). Is a bottom view.

(501) is the outer peripheral surface of the eccentric bush, and O _Bo is its center. (502) is the inner surface of the eccentric bush, and O _Bi is its center. The center O _Bi is eccentric with respect to the center O _Bo by ε. Further, (503) is concentric with the center O _Bi and is a step portion of an inner groove having a diameter smaller than that of the outer peripheral surface (501) and is provided so as to be connected to the outer peripheral surface (501). (504) is the center O
_The stepped portion is concentric with _Bi and has a diameter larger than that of the inner peripheral surface (502) and is provided so as to be connected to the inner peripheral surface (502).
(505) is a vertically extending oil groove formed so that the lower end is open to the lower end face of the eccentric bush and the upper end is closed so as not to open to the upper end face of the eccentric bush.
Is connected to. (506) is an oil hole for communicating the oil groove (505) with the outer peripheral surface portion (501), and (507) is a notch provided in the outer peripheral surface portion (501), which is the oil hole (506).
The radial outer end of is open to this notch. (50
Reference numeral 8) is a detent hole formed in the lower end surface of the eccentric bush in the thick portion of the eccentric bush. The eccentric bush (5) is made of a bearing material such as aluminum alloy or lead bronze.

FIG. 19 shows such an eccentric bush (5) with a spindle (4).
It is a perspective view for explaining an assembling order when mounting to. In FIG. 19, first, the eccentric hole (401) of the spindle (4)
After fitting a generally cylindrical spring pin (420) with a C-shaped planar shape into the pin hole (418) at the bottom, the spring pin (420) has a detent hole at the bottom of the eccentric bush (5). Insert the eccentric bush (5) into the eccentric hole (401) so that (508) fits. Fit the snap ring (421) into the snap ring groove (417) with the spring pin (420) fitted into the detent hole (508) and the lower end surface of the eccentric bush (5) abutting the bottom surface of the eccentric hole (401). . The snap ring (421) is made of elastic linear material such as thin piano wire.
It is formed into a shape.

FIG. 20 is a view showing a state in which the eccentric bush (5) is incorporated in the main shaft (4). In FIG. 20, O _s is the axial center of the main shaft (4), that is, the rotation center, and the fixed scroll (1 ) Consistent with the center. A straight line connecting the center O _s and the center O _{Bi of the} eccentric bush inner peripheral surface (502) and a straight line connecting the center O _Bi and the eccentric bush outer peripheral surface (501) form a substantially right angle. _So that the center O _Bo is located,
The position of the spring pin (420) has been determined. The diameter of the detent hole (508) is made larger than the diameter of the spring pin (420) so that the eccentric bush (5) can move to some extent in the circumferential direction. Further, the notch (507) is formed so that the oil hole (506) of the eccentric bush (5) and the oil hole (414) of the main shaft (4) are always in communication even when the eccentric bush (5) rotates. A predetermined length is formed in the circumferential direction.

The oscillating shaft (204) of the oscillating scroll (2) is fitted in the eccentric bush (5) so that the outer peripheral surface of the oscillating shaft (204) can slide on the inner peripheral surface (502). The center O _Bi of the inner peripheral surface (502) of the eccentric bush coincides with the swing center, that is, the center of gravity of the swing scroll (2). Accordingly, when the spindle (4) rotates in the direction of arrow W, a centrifugal force is exerted in the direction of arrow G on the straight line connecting the rotation center O _s of the spindle (4) and the center O _{Bi of the} eccentric bush inner surface (502). Occurs, and the eccentric bush (5) produces a moment in the direction of arrow M about the center O _Bo of the outer peripheral surface (501) of the eccentric bush. Therefore, if the fixed scroll (1) and the orbiting scroll (2) have spiral side plates (10
If there is a gap between 2) and (202), these side plates (10
2) The eccentric bush (5) rotates in the direction of arrow M about the center O _Bo of the outer peripheral surface (501) of the eccentric bush so that the orbiting scroll (2) moves until the (202) contacts each other.

The change in the center position will be described with reference to FIG. That is, the eccentric bush (5) rotates in the direction of the arrow M around the center O _Bo of the outer peripheral surface (501) of the eccentric bush, and the center O _Bi of the inner peripheral surface (502) of the eccentric bush is the spiral side plates (102), (). 202)
Move to the point O _Bi ′ where they touch each other. That is, the revolution radius of the orbiting scroll (2) is Change. On the contrary, when the revolution radius is smaller than R due to the working accuracy, the eccentric bush rotates in the direction opposite to the arrow M. This also occurs in the case of liquid backing or foreign matter being caught between both spiral side plates (102) (202).

As described above, the eccentric bush (5) absorbs the variation in the working accuracy, facilitates the assembling, and prevents the compressed refrigerant gas from leaking in the spiral direction between the spiral side plates (102) (202) during compression. As a result, the compression efficiency is improved, and it has the proof strength against liquid backing and the entrapment of foreign matter, which is also useful for improving the reliability.

FIG. 22 is an explanatory view showing a state in which oil supply can be secured even if the eccentric bush (5) rotates, (a) of which is at the maximum right until the detent hole (508) and the pin (420) come into contact with each other. The state that the eccentric bush (5) rotates in the clockwise direction (clockwise in the figure) is shown. Even in this state, the oil hole (41) of the spindle (4)
The position and circumferential length of the notch (507) are set so that 4) and the oil hole (506) of the eccentric bush (5) communicate with each other. (B) shows the state in which the eccentric bush (5) is rotated counterclockwise to the maximum, contrary to the above, and in this case as well, the oil holes (506) (414) are notched (50) so as to communicate with each other.
In 7), its position and circumferential length are set.

FIG. 23 shows an embodiment in which the position of the oil passage (404) is rotated 90 ° to the right with respect to the center O _Bi as compared with the embodiment shown in FIGS. 3 to 22. In this case, When the main shaft (4) rotates about the center O _s in the direction of the solid line arrow, the oil flows out in the direction shown by the broken line arrow, so that the oil groove (5 Since the distance of the oil path to 505) becomes short, the responsiveness of the centrifugal pump by the main shaft (4) itself can be accelerated.

Further, FIG. 23 shows another embodiment for preventing rotation of the eccentric bush (5) and preventing floating.
The eccentric bush (5) and the spindle (4) have a groove (50
9) and (422) are provided, and the stop plate (423) is screwed into the groove (422) of the main shaft (4) with the screw (424).
The small protrusion (423a) on the inner side of 3) controls the rotation amount of the eccentric bush (5) to the pin (420) in the previous embodiment,
It is regulated in the same manner as the anti-rotation hole (508), and also prevents the eccentric bush (5) from rising as in the snap ring groove (417) and the snap ring (421). FIG. 24 is a perspective view for explaining the assembling sequence of the embodiment of FIG. 23. The eccentric bush (401) is inserted into the eccentric hole (401) of the main shaft (4) so that the groove portions (422) (509) are aligned with each other. After inserting 5), the stop plate (423) is fitted into the groove portion (422) so that both side surfaces thereof come into contact with the groove side surfaces, and screwed onto the main shaft (4) with the screw (424).

FIG. 25 is a diagram for explaining the oil supply system passage around the main shaft (4). As a result of centrifugal pump action by the oil cap (12) and the main shaft (4) shown in FIG. 3, the oil passage (40
4) The oil rises inside and the space (42) inside the eccentric hole (401)
Inflow into 5). Here, the oil groove (50) of the eccentric bush (5)
The position of 5) is located further on the outer circumference side from the oil passage (404) located on the outer circumference side from the center of the main shaft (4), so that the oil is subjected to the second centrifugal pump action, and the oil inside the oil groove (505). To rise. The oil in the oil groove (505) is the oil hole (506),
By the action of the third centrifugal pump in (414), the oil groove (4
15) Go up inside. At this time, the oil groove (415) is connected to the main bearing (60
2) It does not flow into the balancer chamber (705) because it does not open at the lower end. In this way, the oil flows into the inner peripheral space (426) of the thrust bearing (601) at the upper end of the main shaft (4), passes through the oil groove (601b) of the thrust bearing (601), and passes through the Oldham chamber (605). Is discharged to. Note that, in FIG. 25, the flow of oil is indicated by a dotted arrow. Lower thrust bearing (70
1) and the lower main bearing (702) to the oil holes (406) (40
5) to refuel.

With such an oil supply system, for example, even if the compressor is operated at a low speed by controlling the rotation speed, the centrifugal pump action by the oil cap (12) is deficient due to the low speed operation. Sufficient negative pressure in the space (426) due to the action of the third-stage centrifugal pump can be supplemented, so that stable oil supply can be continued.

The main shaft (4) may move in the axial direction due to vibrations when the compressor is transported. In this case, the upper end surface (427) of the main shaft (4) may collide with the thrust surface (217) of the orbiting scroll (2) and the thrust surface (217) may be damaged. Therefore, as shown in FIG. 25, rather than the gap length l ₁ between the spindle upper end surface (427) and the orbiting scroll thrust surface (217),
The gap length l ₂ between the upper end surface of the step portion (419) of the first balancer (402) and the lower end surface (616) of the upper frame (6) is configured to be small, and if the main shaft extends axially upward. Even if (4) moves, the upper end surface of the step (419) and the lower end surface (416) of the upper frame first come into contact with each other, and the upper end surface (427) of the main shaft (4).
The thrust surface (217) of the orbiting scroll (2) is prevented from hitting. The gap length l ₃ between the motor rotor (10) and the cylindrical bearing support portion (7b) of the lower frame (7) may be smaller than the gap length l ₁ , but the space (426) Since it is better to discharge the gas collected in the space (426) promptly in order to improve the pump efficiency, it is not possible to take a very large amount, so it is better to regulate it by the above gap length l ₂ .

In addition, the inner peripheral surface (601e) and outer peripheral surface (601f) of the thrust bearing (601) overhang portions (601g) (601h) and the thin stepped portion (503) that is the overhang portion of the eccentric bush (5) are Since the orbiting scroll (2) slightly bends following the sagging or deformation of the orbiting scroll (2) due to the overturning moment of the orbiting scroll (2), the bearing surfaces of the bearings (5) (601) are prevented from hitting the bearing surface.

Further, the overhang portion (615) of the main bearing (4) overhanging from the notch portion (6a) formed by cutting the upper edge portion of the inner circumference of the upper frame (6) has a radial gas load and a first balancer. Since the main shaft (4) flexes slightly following the sag of the main shaft (4) due to the moment due to the centrifugal force of the (402) and the second balancer (403), the one-sided contact phenomenon of the bearing surface of the main bearing (4) is prevented. Further, since the lower end of the lower main bearing (702) projects downward (702a) from the lowermost support end (7b ') of the tubular bearing support portion (7b) of the lower frame (7), the main shaft (4) is When tilted, the protrusion (702a) follows and slightly bends, so that it is possible to prevent the one-sided contact phenomenon of the bearing surface of the bearing (702).

FIG. 26 shows a structure for preventing the capacity of the centrifugal pump from increasing excessively at the time of high-speed rotation due to rotation speed control and the like, and increasing the amount of frying oil more than an appropriate amount. The thrust bearing (601) is located where the position of the oil groove (415) extending in the vertical direction of the main shaft (4) and the position of the radial oil groove (601b) of the thrust bearing (601) coincide in the radial direction.
The amount of oil discharged radially outward from the oil is increased, but at other places, that is, where the oil groove (415) is located between the oil groove (601b) and the oil groove (601b) (dashed line). Shows a configuration in which the amount of discharged oil is narrowed, and as the number of rotations increases, the resistance increases due to the tipper effect, and the amount of discharged oil, that is, the amount of pumped oil is relatively suppressed. In this case, the gap between the inner peripheral surface of the thrust bearing (601) and the outer peripheral surface of the main shaft (4) should be smaller than the circumferential groove width of the oil groove (601b) of the thrust bearing.

Figures (b) and (c) show another embodiment, in which the diameter of the oil groove (415) of the main shaft is made smaller than the diameter of the inner circumference (601e) of the thrust bearing (601) and the outer circumference of the main shaft (4). Thrust bearing (60
A gap (601k) between the lower end surface of 1) and the upper end surface of the spindle (4)
Further, a notch (601 m) that vertically overlaps with the oil groove (415) of the main shaft (4) is provided at the radial inner end of each radial oil groove (601b) of the thrust bearing (601). This structure further improves the tipping effect as compared with the structure shown in FIG. 26 (a). Note that FIG. 26 (b) is a top view, and FIG. 26 (c) is a sectional view of the section taken along the line cc of FIG. 26 as seen in the direction of the arrow.

27 and 28 show another embodiment of the means for supplying oil to the lower main bearing (702), respectively. In the figure, the dashed arrow indicates the flow of oil. FIG. 27 (a) is a vertical sectional side view showing the oil supply passage, and FIG. 27 (b) is a sliding surface (701) of the lower thrust bearing (701).
It is a top view which shows a). The oil that has risen in the oil passage (404) and has flowed into the space (425) is supplied to the lower thrust bearing (701) through the oil hole (406) that penetrates the first balancer. Here, the lower thrust bearing (701) is provided with a plurality of radial oil grooves (701b) that are open on the inner peripheral side but not on the outer peripheral side, as shown in FIG. Has been. Here, (701c) is a pin hole for fixing the lower thrust bearing. An oil hole (406) is arranged at the upper end of the oil groove (701b) so as to cross the oil groove (701b) as the main shaft (4) rotates. As a result, the oil intermittently flowing into the oil shaft (701b) from the oil hole (406) is prevented from flowing into the cylindrical bearing support portion (7b) of the lower frame (7).
It reaches the lower main bearing (702) by gravity while being transmitted between the inner peripheral surface of the main shaft and the outer peripheral surface of the main shaft (4). Here, in order to reliably supply oil, an oil groove (428) is longitudinally provided on the counter-load side of the lower spindle sliding surface (409) of the spindle (4).

In FIG. 28 showing still another embodiment, the oil passage (40
Apart from 4), an oil hole (429) parallel to the oil passage (404) is bored in the main shaft (4), the upper end of which is the bottom of the eccentric hole (401) and the lower end is the lower main bearing. There is an opening on the inner peripheral surface of (702). In this case, the oil that has risen in the oil passageway (464) flows into the space (425), where it partially flows downward again through gravity through the oil hole (429) due to gravity or centrifugal force, and the lower main The bearing (702) will be refueled.

Each of the embodiments shown in FIGS. 27 and 28 is more effective than the one shown in FIG. 3 in that the gas trapped in the space (425) is more effectively supplied to the lower main bearing (702). Since it is discharged from the oil supply passage, it is very effective in terms of pump efficiency and responsiveness.

Next, referring to FIG. 29 and FIG. 30, the oil cap (1
Regarding 2). The oil cap (1
2) is important for supplying oil by a centrifugal pump, but the oil that has entered the oil cap (12) is given a rotational force as the oil cap (12) rotates and a centrifugal force is generated. However, if the temperature of the oil rises and the viscosity decreases, the slip between the oil cap inner surface (12a) and the oil increases and the pump efficiency decreases. In order to prevent the deterioration of the slip, it is preferable to use the means shown in FIGS. 29 and 30, respectively.

Fig. 29 shows the fin (1) on the inner surface (12a) of the oil cap (12).
2b) are provided at equal intervals in the circumferential direction, (a) is a cross-sectional view thereof, and (b) is a cross-sectional view taken along line bb of FIG. In this example, the fin (12
Although a plurality of b) are provided, only one may be provided. Here, the fin (12b) is designed in consideration of its circumferential position so as not to block the oil inlet hole (12c), the gas vent hole (407) and the oil passage (404) of the oil cap (12).

FIG. 30 showing another embodiment is a notch passage (430) extending from the center to the outer peripheral surface of the lower end surface of the main shaft (4).
Is provided, and the oil cap (1
2) is in close contact and covers a part of the lower end opening of the cutout passageway (430), and (a) is a cross-sectional view thereof.
FIG. 30B is a sectional view taken along line bb of FIG. 30A, viewed in the direction of the arrow. Cutout passage (430) in the figure
Is provided so as to connect the center of the main shaft (4), that is, the gas vent hole (407) and the oil passage (404), and this structure prevents slipping more than the oil cap with fins shown in FIG. 29. Has the effect of

FIG. 31 is a diagram showing an example of the wiring structure of a power supply lead wire to the stator winding (11a) of the motor stator (11) and a control lead wire connected to the motor temperature detection thermometer. ) Is a vertical side view, and (b) is a view of a section taken along line bb in (a) in the direction of the arrow.

In FIGS. 31 (a) and 31 (b), one of the recesses (109) of the fixed scroll (1) is a motor stator (1).
1) The lead wire (100a) for feeding the stator winding (11a) and the control lead wire (100b) connected to the motor temperature detection thermometer are covered with a flexible insulating tube (100c). It is used as a passage for the lead wire bundle (100). The lead wire bundle (100) is arranged as shown in FIG. 31 (b), and a small convex portion (110b) extends in the circumferential direction on the convex portion (110) of the fixed scroll (1). A pair is provided so as to face each other, and is used to hold the lead wire bundle (100). Further, the push plate (100d) is used to further secure the holding of the lead wire bundle (100). Furthermore, the planar shapes of the outer peripheral portions of the upper frame (6) and the lower frame (7) are formed in a concavo-convex shape substantially the same as the planar shape of the outer peripheral portion of the fixed scroll (1), one of which is the 31st Shown in the figure (6a) is the upper frame (6)
Concavity formed on the outer periphery of (7g) is the lower frame (7)
Of the recesses formed on the outer periphery of each of the recesses (109) (6
a) (7g) are vertically overlapped with each other to form a series of vertically extending through recessed grooves (100e). Then, the lead wire bundle (100) is vertically passed through the series of recessed grooves (100e), and the pair of small protrusions (110b) of the fixed scroll (1) are used to push the push plate (100d) into the lead wire bundle. It is held by pushing (100). The pressing plate (100d) is formed of a thin plate having elasticity, such as spring steel, and is concave (109) in a curved state against the elastic force as illustrated.
Since they are fitted in (6a) and (7g), the elastic force prevents them from falling out of the series of through grooves (100e).

With such a configuration, the welding part (902
It is possible to prevent insulation failure due to overheating or melting of the coated lead wire in contact with a). Further, (6b) is a small convex portion formed at the tip of the inner wall surface of the concave portion (6a) so as to overlap the small convex portion (110b) of the fixed scroll (1),
Similarly, (7h) is a small convex portion formed at the tip of the inner wall surface of the concave portion (7g) so as to overlap the small convex portion (6b) of the upper frame (6), and (6c) is the upper frame (6). ) Is an air gap formed between the outermost peripheral part and the inner peripheral surface of the shell intermediate cylindrical part (901), and is formed so that heat during welding of the welded part (902a) is not conducted to the upper frame (6). It is a thing. (11
Reference numeral 0c) denotes a space formed between the outermost peripheral portion of the fixed scroll (1), the shell intermediate cylindrical portion (901), and the shell upper lid (902). The heat generated during welding of the welded portion (902a) is fixed scroll. It is formed so as not to conduct to (1). The so-called lead wire portions such as the lead wire bundle (100) and the push plate (100d) are the shell intermediate cylindrical portion (90) of the refrigerant gas suction pipe (904).
The suction pipe (904) is shown by a chain line because it is arranged at a position offset from the opening inward in the circumferential direction. Further, the power supply lead wire (100a) is detachably plugged in to the sealed terminal (907) of FIG. 3, and the control lead wire (100b) is located at a position deviated from the sealed terminal (907) in the circumferential direction. The plug is removably plugged in to another sealed terminal (not shown) provided on the shell upper lid (902).
The push plate (100d) has a flange (100d-1) that comes into contact with the upper surface of the fixed scroll (1) and three through holes (100d-2) that are formed so as to be easily bent. Have

FIG. 32 is a diagram showing another specific example. In FIG. 32, (1) is a fixed scroll, (101) is a fixed scroll (1) base plate, and (102) is a fixed scroll base plate (1).
The spiral side plate formed on 01), (2) is the orbiting scroll, (201) is the base plate of the orbiting scroll (2), and (202) is the orbiting scroll base plate (201). The spiral upper plate (204) is a shaft provided on the base plate (201) of the orbiting scroll on the opposite side of the side plate (202), and between the side plates (102) (202) of both scrolls is a compression chamber ( P) is formed. Further, (Pi) is a suction chamber, and (105) is a discharge hole. Grooves (103) (203) are formed along the spirals at the tips of the spiral side plates (102) (202), and a chip seal (3) is formed inside the grooves (103) (203). Is movably fitted in the axial direction, that is, in the vertical direction. Further, (4) is a spindle, (401) is an eccentric hole provided at one end of the spindle (4) so as to be eccentric with the axis, and (404) is an oil penetrating from the lower end of the spindle (4) to the eccentric hole (401) A hole, (12) is an oil cap integrally formed on the lower end of the spindle (4) or fixed by press fitting, shrink fitting, etc., (407) is a spindle (4)
This is a gas vent hole for the oil cap (12) that connects the lower end to the side surface. An eccentric bush (5) is rotatably fitted in an eccentric hole (401) of the main shaft (4), and an eccentric hole (502) is further provided in the eccentric bush (5). The shaft (204) is slidably supported.
(670) is a frame that directly or indirectly supports the fixed scroll (1), the orbiting scroll (2), the main shaft (4), etc., and (670a) integrally projects downward from the center of the frame (670). The boss part (670b) is the frame (670)
A skirt portion integrally formed in a cylindrical shape downward from the outer peripheral portion of the frame, (607) is an Oldham groove provided in a pair of right and left on the upper surface of the frame (670) according to the diameter method, and (604) is of the frame (670). A plurality of oil return holes that communicate the upper surface and the lower surface and are provided at predetermined intervals in the circumferential direction, and (8) are Oldham couplings that prevent the orbiting scroll (2) from rotating, and are connected to the Oldham ring portion (801). It has a pair of Oldham keys (802) extending in directions orthogonal to each other on the upper surface and the lower surface thereof. Reference numeral (601) is a first thrust bearing fixed to the frame (670) with screws or pins, and slidably supports the base plate (201) of the orbiting scroll (2). Generally, on the sliding surface of the first thrust bearing (601), multiple radial oil grooves (601b) are provided at equal intervals in the circumferential direction in order to promote the supply of lubricating oil. (701) is the frame (670)
A second thrust bearing fixed to the main shaft (4) in the axial direction by a screw or a pin, and a (602) fixed to the frame (670) by press fitting or the like to rotatably support the main shaft (4). One main bearing (702) is a second main bearing fixed to the boss (670a) of the frame (670) by press fitting or the like and also rotatably supporting the main shaft (4). An oil hole (404) for supplying oil to the above-mentioned second thrust bearing (701), first main bearing (602) and second main bearing (702).
Are provided in the spindle (4). (11) is a motor stator, which is fixed to the skirt (670b) of the frame (670) by a method such as bolting, press fitting, or shrink fitting.
Reference numeral (10) is a motor rotor, which is fixed to the main shaft (4) at the same position in the axial direction as the motor stator (11) by a method such as press fitting or shrink fitting. The skirt portion (670b) of the frame (670) is provided with a passage (670c) so that the intake gas can pass through the outer peripheral portion of the motor stator (11) from above to below. At the upper end of the motor rotor (10), the first balancer (4) is installed in the opposite way to the eccentric hole (401) of the main shaft (4).
02) is attached by screws or caulking,
A second balancer (403) is also attached to the lower end in the opposite direction to the first balancer (402) by a method such as screwing or caulking. (9013) is a lower shell that accommodates the above-mentioned components, and a frame (670) is fixed to the lower shell by a method such as press fitting or shrink fitting. (902) is an upper shell, which is fixed to the lower shell (9013) by welding, forms the outer shell of the compressor together with the lower shell (9013), and achieves internal airtightness. (909
a) is the lubricating oil stored at the bottom of the lower shell. (90
4) is a suction pipe that penetrates the side surface of the lower shell (9013) and fits into the hole (670e) of the skirt portion (670b) of the frame (670) to introduce the suction gas into the shell. ). Reference numeral (614) denotes concave portions provided on the outer circumference of the frame (670) at equal intervals in the circumferential direction, and extends in the up-down direction along with the inner circumferential surface of the lower shell (9013), and the suction chamber (Pi) A gas passage (614b) communicating with the pipe (904) is formed. Reference numeral (905) is a discharge pipe for introducing discharge gas from the discharge chamber (105) of the fixed scroll (1) to the outside of the compressor.

FIG. 33 is a partial detailed view of FIG. In FIG. 33,
Reference numeral (208) is an Oldham groove extending in the diameter direction on the back surface of the orbiting scroll base plate (201) and provided in a pair of left and right in the vicinity of the outer peripheral portion, and (601b) is circumferentially equidistant to the first thrust bearing (601). It is a plurality of radial oil grooves provided at intervals. The other reference numerals are the same as those described with reference to FIG. 32 and will not be described.

The operation of the scroll compressor configured as shown in FIGS. 32 and 33 will be described. First, when the motor stator (11) is energized, the motor rotor (10) generates torque and the main shaft (4)
Give a rotational movement to. When the main shaft (4) rotates, the eccentric bush (5) fitted in the eccentric hole (401) at one end also rotates, and swings via the swing scroll shaft (204) fitted in the eccentric bush (5). Try to rotate the scroll (2). However, as shown in FIG. 33, the pair of pawls (802) orthogonal to each other in the Oldham coupling (8) are the Oldham groove (607) of the frame (670) and the Oldham groove (208) of the orbiting scroll (2). The orbiting scroll (2) is slidably fitted to the frame (67).
0) and a predetermined angular posture is always maintained. Therefore, the orbiting scroll (2) makes an orbital motion without rotating with the rotation of the main shaft (4), and performs a compression action according to the principle shown in FIG. It should be noted that the performance of the scroll compressor depends on reliable axial and radial sealing between the compression chambers in the compression process. In this embodiment, as described above, the seal for generating the pressing force in the axial direction is generated by providing the chip seal (3) at the tips of both spirals (1) and (2), and also generating the pressing force in the radial direction. The seal is constructed by providing an eccentric bush (5). Intake gas accompanying the above compression action is absorbed from the intake pipe (904) to the upper part of the motor stator (11),
After cooling the coil end of the stator winding (11a), it passes through the passage (670c), the gas passage (614b), and the suction chamber (Pi).
Is taken into the compression chamber (P), is sequentially compressed, and is discharged from the discharge pipe (905). Next, the lubricating oil path will be described. First, by rotation of the main shaft (4) and the oil pump (12). The lubricating oil in the oil pump (12) produces a centrifugal force, which pushes the oil hole (404) upward. A part of the lubricating oil is supplied to the second main bearing (702) and the second thrust bearing (701) through the oil holes (405) and (406) before reaching the upper end of the main shaft (4). The oil supplied to and discharged from the inner and outer circumferences of the first main bearing (602) and the eccentric bush (5) is supplied to the oil groove (601) of the first thrust bearing (601).
After passing through b), it is discharged outward in the radial direction from the outer peripheral portion of the first thrust bearing (601). The Oldham coupling (8) is configured to form a slight space (S) surrounded by the inner peripheral surface of the ring portion, the upper surface of the frame (670) and the base plate (201) of the orbiting scroll (2). , The oil discharged to the outside in the radial direction of the first thrust bearing (601) and entering the space (S) is not sucked into the suction chamber (Pi) and is returned from the space (S) to the oil return hole (604). Through the motor stator (1
1) It is returned to the upper part and returned to the oil sump (909) through the passage (670c). Also, swing scroll (2)
The orbiting motion of the scroll compressor tries to cause vibration due to unbalanced force, but the first balancer (402) and the second balancer (430) can balance statically and dynamically, Operation can be performed without causing abnormal vibration.

Another embodiment of the present invention will be described below with reference to FIGS. 34 and 35.

In FIG. 34, (6) is the first frame, (67a) is the seal portion provided on the lower surface side of the first frame (6), (60)
Reference numeral 9) is a pair of arcuate grooves provided on the upper surface side of the first frame (6) in an arc shape substantially concentric with the center thereof, (607)
Is also an Oldham groove provided in a pair of left and right extending in the diametrical direction on the upper surface of the first frame (6), and the upper end of the (604) is opened to the arc-shaped groove (609), and the first frame (6) Is an oil return hole penetrating in the axial direction, and a plurality of oil return holes are provided at predetermined intervals in the circumferential direction. Further, (614b) is a gas passage formed in the outer peripheral portion of the first frame (6) by the recesses (600c) extending in the axial direction at predetermined intervals and the inner peripheral surface of the lower shell (9013). It is configured to serve as a passage for inhaled gas during operation. (602) is the first main bearing, which is the above-mentioned Inro (67a)
Is processed concentrically. (7) is the second frame, (7
b) is a boss portion projecting downward from the central portion of the second frame (7) into the concave counterbore (10b) provided in the central portion of the upper surface of the motor rotor (10) described later, and (7b) is the second frame (7). ) A plurality of motor mounting feet protruding downward from the outer peripheral portion in a finger shape, (7g) is an oil return groove provided on the outer peripheral surface of at least one motor mounting foot (7d), and is an upper part of the second frame (7). Communicates with the recess (705). Also, the outer diameter of the second frame (7) was shrunk to the shell (9013),
For fixing by press fitting or the like, a plurality of them are formed to be slightly larger than the outer diameter of the first frame (7), and are arranged on the outer periphery in the same manner as the first frame (6) and are arranged at predetermined intervals extending in the axial direction. The gas passage (614b) is provided. (7h) is a partition wall provided so as to close the upper end of one of these gas passages (614b), and (76a) is a seal portion provided on the upper surface side of the second frame (7). Reference numeral (702) is a second main bearing fixed near the tip of the boss portion (7b) by press fitting or the like, and is processed concentrically with the seal portion (76a). The first frame (6) and the second frame (7) are configured such that the respective cage portions (76a) and (76a) are fitted to each other with almost no clearance, and thus the compressor is assembled. , The concentricity of the first main bearing (602) and the second main bearing (702) is secured, and the main shaft (4) is slidably supported by both bearings (602) (702). Reference numeral (402) is a first balancer protruding from the main shaft (4) so as to be housed in the balancer chamber (705) formed of a recess formed on the upper surface of the second frame (7). In this embodiment, the first balancer (402) is formed integrally with the main shaft (4), but the first balancer (402) formed separately from the main shaft (4) is bolted or shrink-fitted. It may be attached to the main shaft (4) by the method of. Further, (11) is a motor stator, which is fastened and fixed to the lower end of the motor mounting foot (7d) by a bolt (704). Reference numeral (10) denotes a motor rotor, which is fixed to the main shaft (4) by a method such as press fitting or shrink fitting in a state where it is offset from the motor stator (11) by a predetermined amount in the upper direction. In addition, the motor rotor (1
The central part of the upper surface of (0) is the boss part (7b) of the frame (7).
The concave counterbore (10
b) is formed, and a second balancer (403) is further provided at the lower end of the motor rotor (10). (106)
Are bolts for fastening and fixing the fixed scroll (1), the first frame (6) and the second frame (7) together.
(910) is installed on the upper part of the oil storage (909a) and the lower shell (9
[0113] A disk-shaped forming restraint plate whose outer peripheral portion is spot welded to (13) and (910b) are one or a plurality of small holes perforated in the forming restraining plate. Assembly of the main parts of such a scroll compressor will be further described with reference to FIG. FIG. 35 shows the fixed scroll (1), orbiting scroll (2), Oldham coupling (8), first frame (6), second frame (7), main shaft (4), motor stator ( FIG. 11 is an exploded perspective view showing an assembled state of main parts such as 11). In FIG. 35, (111) is a pin hole provided in four pairs on the outer peripheral portion of the fixed scroll (1), and the spiral side plate (102) of the fixed scroll (1) has these paired pin holes (111). It is processed according to the standard. That is, the pair of pin holes (111) centering on the center of the side plate (102) are 180 ° opposite to each other. Also (61
3) is a pin hole provided in four pairs on the outer periphery of the first frame (6), and is drilled at a completely symmetrical position with respect to the center of the first main bearing (602). That is, the pin holes (613) forming each pair with the center of the first main bearing (602) as the center are located at 180 ° opposite positions. In addition, the pin hole (61
The pitch of 3) completely matches the pitch of the pin hole (111) of the fixed scroll. Further, (27) is an assembly pin. The scroll compressor thus constructed is assembled as follows. First, the main shaft (4) is inserted into the second frame (7) from above and then the main shaft (4) is used as a guide, and the inlay portion (67a) of the first frame (6) is moved to the second position.
By fitting the spigot part (76a) of the frame (7), the first frame (6) is set so that the first main bearing (602) and the second main bearing (702) are concentric. The Oldham coupling (8) has its claw (802) attached to the first frame (6).
Of the Oldham groove (607) of the eccentric bush (5) with its shaft (204) attached to the main shaft (4). ), And the Oldham groove (208) is loosely fitted in the claw (802) of the Oldham coupling (8) and mounted on the first thrust bearing (601). Then two pins (27)
Is set so as to pass through the pin hole (111) of the fixed scroll (1) and the pin hole (613) of the first frame (6), so that the fixed scroll (1) is attached to the upper end surface of the first frame (6). The center of the spiral side plate (102) and the center of the first main bearing (602) are aligned with each other.
Thereafter, the fixed scroll (1), the first frame (6) and the second frame (7) are fixed by the bolts (106).
, The fixed scroll (1) forming a compression element, the orbiting scroll (2), the Oldham coupling (8),
The assembly of the first frame (6), the second frame (7), and the spindle (4) is completed. The pin (27) does not have to be used. Then, attach the motor stator (11) to the motor mounting foot (7d) of the second frame (7) with the bolt (20
4) and after mounting the motor rotor (10) on the main shaft (4) by shrink fitting, etc., fix the outer periphery of the second frame (7) to the lower shell (9013) by shrink fitting, etc. Sealing with (902) completes the entire assembly.

As described above, if the frame is divided into the first frame (6) and the second frame (7) and the first balancer (402) integrated with the main shaft (4) is arranged between them, the unbalanced force is generated. Since the first balancer (402) can approach the orbiting scroll (2) that is the source, the first balancer (4)
02) can be miniaturized, and thus the second balancer (403) can also be miniaturized. The second main bearing (7
Below 02), only the second balancer (403) applies a radial force to the main shaft (4), and this force is relatively small. Therefore, the load applied to the second main bearing (702) is also small, and the bearing reliability can be improved. In addition, the boss (7b) of the second frame (7) is connected to the motor rotor (1
By extending into the counter bore (10b) of 0),
The load applied to the above-mentioned second main bearing (702) becomes even smaller. Also, as in the conventional example, the first balancer (402)
When the motor rotor (10) is mounted on the upper end of the motor rotor (10), it is difficult to maintain a large centrifugal force generated in the first balancer (402) due to the strength of the motor rotor (10). Is also resolved.

Next, the lubricating oil path in this embodiment will be described. The oil given the centrifugal force by the oil pump (12) lubricates each bearing through the oil hole (404) in the main shaft (4) and then passes through the oil groove (601b) of the first thrust bearing (601). It is discharged radially outward of the first thrust bearing. The discharged oil drops into the circumferential groove (609) on the first frame (6), then passes through the oil return hole (604) and drops into the upper recess (705) of the second frame (7), After passing through the oil return groove (7g) provided on the outer peripheral side of the motor mounting foot (7b) of the second frame (7), the oil storage (909a) is provided along the outer periphery of the motor stator (11).
It falls on the upper foaming control plate (910). In addition, the position where it falls from the oil return hole (604) is set to the first balancer (4
If it is installed from the outermost circumference to the inner circumference side of 02), the first balancer (40
Centrifugal force is applied to the oil that has dropped due to the rotational movement of 2),
Easier to discharge. The oil that has dropped onto the foaming presser plate (910) passes through the small holes (910b) and is returned to the oil storage (909a). The foaming restraint plate (910) is
It has the effect of preventing oil from being taken away by the foaming when starting with the refrigerant sunk in a).

Next, the gas path inside the compressor will be described. Intake gas is a suction pipe (904) provided around the lower shell (9013).
From the inside to the inside of the compressor, and after colliding with the outer wall of the second frame (7), the partition wall (7h) does not suck the gas upward to the lower side of the second frame (7) and the motor stator (11). ) Is cooled, and then is sucked into the suction chamber (Pi) through the gas passage (614b). The gas sucked into the suction chamber (Pi) is taken into the compression chamber (P), sequentially compressed, and then discharged from the discharge pipe (905). In such a suction gas path, since the suction gas does not directly collide with the coil portion of the motor stator (11), there is no damage to the coil portion due to foreign matters contained in the suction gas, and the second frame (7). Lubrication is easy because the oil in the intake gas can be separated easily because the flow velocity drops sharply in the lower part, the pressure loss of the intake gas is small, and it is difficult for the intake gas to flow near the lower end of the oil return groove (7g). It has the advantage that the oil is less likely to be carried away by the inhaled gas.

Further, in this embodiment, the motor rotor (10) is offset from the motor stator (11) in the upward direction.
As a result, a force acts to return the motor rotor (10) downward. This force acts to prevent the main shaft (4) from moving upward and coming into contact with the base plate (201) of the orbiting scroll (2) due to vibration or external force during operation of the compressor.

Also, as shown in FIG. 36, the Oldham groove (607) of the first frame (6) has a bulge (60) in the lateral direction of the groove at the outer end thereof.
7a) is provided and fitted Oldham coupling (8)
The claw (802) and the groove (607) do not interfere with each other when the claw (802) slides to the outermost part. If the radius of curvature (r) of the inner surface of this bulge (607a) is made equal to 1/2 of the width (W) of the groove (607), the cutter used for processing the groove (607) will remain at the outer end portion by a predetermined amount. It can be easily processed by shifting it to both sides. In this way, bulges (607a) on both sides of the outer edge of the groove (607)
Since it is possible to easily prevent the interference with the claws (802) of the Oldham coupling (8), it is possible to provide an economical frame (6) having a small outer diameter. In addition,
(802 ') shows the position when the claw of the Oldham coupling (8) moves to the innermost position.

Further, as shown in FIGS. 37 (a) and 37 (b), the upper shell (902) is provided with a power supply sealing terminal (907) for supplying power to the motor stator (11) from the outside. The shell (902) is provided with the bulge (902b) in the height direction only at the portion where the power-supplying sealed terminal (907) is provided, so that the shell height is not unnecessarily increased. Furthermore, a three-phase tab (9071A) is provided on the sealed terminal (907) for power supply.
(9071B) and (9071C) are arranged, but it is easy to insert the three lead wires (9072) from the same direction.
71A) (9071B) (9071C) are unified in the same direction. Reference numeral (9073) is a transparent insulating coating which covers the connection portion between each of the tabs and the lead wire (9072) and insulates the connection portion so as not to cause a short circuit between phases. (909) is a control sealed terminal connected to the motor temperature detecting thermometer, and is provided in the bulge (902b) portion similarly to the power feeding sealed terminal (907), and each tab (9091A) (909B). Is also unified in the same direction, so that the two lead wires (9092) can be easily inserted from the same direction.

It should be noted that, as described above, a large number of examples are shown, and a number of improvements are shown in each example. However, various functions can be realized by appropriately combining or substituting the respective improvements of the respective embodiments. The appropriate combination and replacement of these are omitted in order to avoid making the specific illustrations and descriptions redundant, but they are naturally included in the present invention.

〔The invention's effect〕

As described above, according to the present invention, the motor housed in the lower part of the hermetic shell, the compression element housed in the upper part of the hermetic shell, the fixed scroll, the upper frame, the lower frame, etc., and the hermetic shell upper part. Is provided in
In a scroll fluid machine including a terminal for supplying power to the motor, and an insulating coating lead wire that electrically connects the terminal and the motor, the insulating coating lead wire includes the fixed scroll, the upper frame, and Since the recesses formed in the outer peripheral portion of the lower frame are accommodated in the vertically extending through recessed groove so as to be separated from the hermetic shell, the motor power supply terminal and the lead wire are provided. Since it is not immersed in the oil in the oil reservoir inside the shell, insulation failure does not occur at those terminals and lead wires, and the distance from the inner wall of the sealed shell can be reliably secured. Produces an effect that is not affected by.

[Brief description of drawings]

1 (a) to (d) are operation principle diagrams of a scroll compressor, FIG. 2 is a side sectional view of a conventional scroll compressor,
FIG. 3 is a side sectional view of a scroll compressor showing an embodiment of the present invention, FIGS. 4 (a) and 4 (b) are top views and bottom views of a fixed scroll, and FIG. FIG. 4 (a) is a sectional view taken along line cc in FIG. 4 (a), FIG. 4 (d) is also a combined state view of fixed and orbiting scrolls, and FIGS. 5 (a) to 5 (c) are also orbiting scrolls. 6 is a side view of an orbiting scroll showing another embodiment of the present invention, and FIG. 7 is an exploded perspective view of the orbiting scroll showing one embodiment of the present invention. 8A is a top view of the upper frame, FIG. 8B is a cross-sectional view taken along the line bb of FIG. 8A, and FIG. 9A is the upper thrust. A top view of the bearing, FIGS. 9 (b) and (c) are cross-sectional views taken along line bb and cc of FIG. 9 (a), and FIG. 10 (a), respectively. Also a top view of the Oldham coupling,
10 (b) is a sectional view taken along line bb of FIG. 10 (a), FIG. 11 is a perspective view of an Oldham key of the Oldham joint, and FIG. 12 is an exploded perspective view of the Oldham joint. , First
13 is a top view showing the assembled state of the upper frame, upper thrust bearing and Oldham's joint, FIG. 14 is a bottom view showing the assembled state of the orbiting scroll and the Oldham's joint, and FIGS. 15 (a) (b). ) Is an explanatory view of a gap between each member in the assembled state of the orbiting scroll, the Oldham coupling and the upper frame, FIG. 15 (c) is a sectional view taken along the line cc of FIG. 15 (a), 16 Figures (a) and (b)
Is a side sectional view and external view of the spindle, FIG. 16 (c).
Is an external view of a spindle with a balancer attached, and Fig. 17 shows
Similarly, a top view of the spindle showing the eccentric bush not inserted,
18 (a) to 18 (c) are top views of the eccentric bush.
A side sectional view and a bottom view, FIG. 19 is an exploded perspective view of the spindle and the eccentric bush, FIG. 20 is a plan view showing the assembled state of the spindle and the eccentric bush, and FIG. 21 is an explanatory view of the action of the eccentric bush. FIGS. 22 (a) and 22 (b) are sectional views for explaining the operation of the eccentric bush, and FIG. 23 is a top view showing the assembled state of the eccentric bush and the spindle according to another embodiment of the present invention. Fig. 23 is an exploded perspective view of the eccentric bush and the main shaft shown in Fig. 23, Fig. 25 is an enlarged sectional view of the oil supply passage around the main shaft showing one embodiment of the present invention, and Fig. 26 (a) is the same main shaft and upper thrust. FIG. 26 (b) is an enlarged top view showing the relationship of the oil grooves of the bearing, and FIG. 26 (c) is an enlarged top view showing the relationship of the oil grooves of the main shaft and the upper thrust bearing according to another embodiment of the present invention. ) Is a sectional view taken along the line cc of FIG. 26 (b), and FIG. FIG. 27 (a) is a side sectional view of a means for supplying oil to a lower main bearing, FIG. 27 (b) is a top view of a sliding surface of a lower thrust bearing, and FIG. FIG. 29 (a) is a side sectional view of a means for supplying oil to a lower main bearing showing another embodiment, and FIG. 29 (a) is a side sectional view of a centrifugal pump section at the lower end of a main shaft showing one embodiment of the present invention. Is a cross-sectional view taken along line bb in FIG. 29 (a).
FIG. 30 (a) is a side sectional view of a centrifugal pump portion at the lower end of a main shaft according to another embodiment of the present invention, FIG. 30 (b) is a sectional view taken along line bb of FIG. 30 (a), FIG. 31 (a) is an enlarged side sectional view showing a lead wire portion for supplying power to a motor showing an embodiment of the present invention, and FIG. 31 (b) is a b- line in FIG. 31 (a).
Sectional view taken along line b, FIG. 31 (c) is FIG. 31 (a).
FIG. 32 is a perspective view showing the push plate (100d) in FIG.
A side cross-sectional view of the entire scroll compressor which is another embodiment of the present invention, FIG. 33 is an exploded perspective view of the upper part of the scroll compressor, and FIG. 34 is a scroll compression showing another embodiment of the present invention. Fig. 35 is a side sectional view of the entire machine, Fig. 35 is an exploded perspective view of the upper part of the scroll compressor, and Fig. 36 is an enlarged top view showing the relationship between the Oldham key and the guide groove showing one embodiment of the present invention. FIG. (A) is a perspective view of the upper shell portion shown in FIG. 32, and FIG. 37 (b) is an enlarged top view of the same. In the drawings, the same reference numerals indicate the same or corresponding parts. In the figure, (1) is a fixed scroll, (2) is an orbiting scroll, (4) is a spindle, (6) and (7) are upper and lower frames, (9) is a closed container, and (10) and (11) are Motor / rotor and stator, (100) lead wire bundle, (404) oil supply passage, (406) oil hole, (601) (701) upper and lower thrust bearings, (907) sealed terminal, (909) Is an oil sump.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Tsutomu Inaba 6-5-6 Tedai, Wakayama, Wakayama Sanryo Electric Co., Ltd. Wakayama Plant (72) Masahiko Oide, 6 Tedai, Wakayama, Wakayama 5-66 Sanrishi Electric Co., Ltd. Wakayama Works (72) Inventor Tadashi Kimura 6-5-6 Tehira, Wakayama, Wakayama Sanriki Electric Co., Ltd. (72) Norihide Kobayashi Wakayama Wakayama Prefecture 6-5-6, Ichiteira Sanryo Electric Co., Ltd. Wakayama Manufacturing Co., Ltd. (56) Reference JP-A-58-122386 (JP, A) JP-B-58-28433 (JP, B2)

Claims (1)

[Claims] 1. A motor housed in a lower part of a hermetic shell,
A compression element that is housed in the upper portion of the closed shell and includes a fixed scroll, an upper frame, a lower frame, and the like, a terminal that is provided on the upper portion of the closed shell and that supplies power to the motor, and the terminal and the motor are electrically connected. In the scroll-type fluid machine, the insulation-coated lead wire is electrically connected to the fixed scroll, and the recesses formed in the outer peripheral portions of the fixed scroll, the upper frame, and the lower frame are vertically overlapped with each other. A scroll-type fluid machine characterized in that it is supported and housed in a vertically extending through groove so as to be separated from the hermetic shell.