JPH0116346B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a scroll compressor that combines a fixed scroll and an oscillating scroll and drives the oscillating scroll to compress refrigerant.

Scroll compressors have been known for quite some time in the literature, but they have not been realized as a product, and even though they are known in principle, there are various unresolved issues in commercializing them. There are many problems to solve.

Conventional examples that are typical or described in considerable detail include, for example, Japanese Patent Laid-Open No. 53-35840 and US Pat. No. 3,874,827. Japanese Unexamined Patent Publication 1973-
Publication No. 35840 proposes an improved specific structure, particularly regarding a means for completely sealing a compression chamber and a thrust bearing that receives thrust from an oscillating scroll. Also, U.S. Pat. No. 3,874,827 shows an improved scroll compressor that has fewer parts, is more compact, and is less expensive.

In addition, although JP-A-53-35840 discloses a vertical scroll compressor, as mentioned above, the focus is on the compression chamber sealing means and the thrust bearing of the oscillating scroll. Concrete proposals regarding compact construction of the area around the bearing to reduce damage to the radial bearing due to strain acting on the part that receives the oscillating scroll shaft and to simplify the oil supply path to the thrust bearing. It hasn't been talked about. Further, in US Pat. No. 3,874,827, an oscillating scroll and a crankshaft are disposed above a fixed scroll, and the crankshaft and balancer 7 are disposed above the fixed scroll.
9 is made of the same material and the oscillating scroll shaft is fitted into a hole in the lower end surface of the crankshaft, but like the one in the above-mentioned Japanese Patent Application Laid-Open No. 53-35840,
Specific proposals are made regarding configuring the area around the bearing in a compact manner to reduce damage to the radial bearing due to strain acting on the part that receives the oscillating scroll shaft, and to simplify the oil supply path to the thrust bearing. It hasn't been talked about. Furthermore, if the device described in this U.S. patent were to be turned upside down and the oscillating scroll and crankshaft were positioned below the fixed scroll, the balancer 79 would be connected to the bearing 80 of the crankshaft and the oscillating scroll shaft 72. Since it is located higher up, the oscillating scroll shaft 7
0 is longer in the axial direction, and the bearing 72 of the oscillating scroll shaft is provided in the lower half of the oscillating scroll shaft 70, so when the oscillating scroll makes an oscillating motion, the gas load force is applied to the crankshaft. The force that acts as a force to tilt the crankshaft acts as a large twisting force on the bearing 72, damaging the bearing 72. Note that the phenomenon that acts to tilt the crankshaft described above occurs in the case of a structure in which the oscillating scroll and the crankshaft are coupled together to drive the oscillating scroll, even if the oscillating scroll is supported by a thrust bearing. The inventors have confirmed through actual measurements that this is likely to occur. Further, in this U.S. patent, the bearings 72 and 80 are rolling bearings, and the axial centers of both bearings 72 and 80 are shifted in the axial direction, so that the radial load acting on the bearing 72 is transmitted through the crankshaft. Since the bearing 80 cannot directly receive the movement in the radial direction, a large moment due to the swinging motion of the swinging scroll acts on the bearing 80, and the bearing 80 is likely to wear out. Furthermore, in Japanese Patent Application Laid-Open No. 53-35840, the above-mentioned moment becomes considerably large because the radial bearing 132 is provided considerably below the oscillating scroll shaft, and wear and tear on the bearing 132 is unavoidable. Further, in the above-mentioned Japanese Patent Application Laid-open No. 53-35840, the radial bearing 132 that supports the upper end of the crankshaft is positioned considerably below the thrust bearing 14 of the oscillating scroll, and a balancer 125 is installed between both bearings 14 and 132.
In addition, the above U.S. Patent No. 3874827
The device in the specification also has a balancer 79 interposed between the thrust surface 131 for the oscillating scroll and a radial rolling bearing 80 that supports the tip of the crankshaft, and in both cases, the thrust bearing of the oscillating scroll and the crankshaft are connected to each other. No consideration has been given to making the area around the bearings, including the radial bearing at the tip, compact.

In view of the above-mentioned conventional circumstances, the present invention reduces the moment generated on the crankshaft due to the oscillating motion of the oscillating scroll, thereby preventing damage due to twisting of the bearing portion of the oscillating scroll shaft and the bearing portion of the crankshaft. This was done with the aim of suppressing wear and tear, compactly configuring the area around the bearings, including both of the above bearings and the thrust bearing of the oscillating scroll, and simplifying the oil supply route to each bearing. A fixed scroll and an oscillating scroll each having spiral scroll teeth are combined with each other so that the scroll teeth form a refrigerant compression chamber between them, and the oscillating scroll is controlled by a crankshaft. In the scroll compressor that compresses the refrigerant by driving the oscillating scroll, the oscillating scroll is provided with an oscillating scroll shaft that extends on the side opposite to the scroll teeth, and a oscillating scroll shaft that extends on the side opposite to the scroll teeth of the oscillating scroll is provided on the oscillating scroll. An eccentric hole is provided in the end face, the swinging scroll shaft is supported in the eccentric hole, and the range circumferentially surrounds the scroll shaft via the crankshaft and extends from the axial center to both sides of the scroll shaft. A radial bearing is provided which supports the crankshaft from the outside over a range extending from the axial center of the scroll shaft to both sides in the axial direction. A thrust bearing is provided adjacent to the outside to surround the radial bearing and to which the oil supplied to the radial bearing is supplied; This is a scroll compressor in which the above-mentioned thrust bearing and the above-mentioned radial bearing are provided on a common bearing support.

Before entering into the description of this invention, the principle of a scroll compressor will be described.

The basic elements of a scroll compressor are shown in FIG. 1. In FIG. 1, 1 is a fixed scroll;
2 is an oscillating scroll, 3 is a discharge port, 4 is a compression chamber,
O is a fixed point on the fixed scroll, and O' is a fixed point on the oscillating scroll. The fixed scroll 1 and the swinging scroll 2 are composed of spirals having the same shape, and the shape is a combination of involutes, circular arcs, etc., as is conventionally known.

Next, the operation will be explained. In FIG. 1, the fixed scroll 1 is stationary with respect to space, and the oscillating scroll 2 is combined with the fixed scroll 1 as shown in the figure, and performs rotational movement, that is, oscillation, without changing its attitude relative to space. Figure 1
It moves like 0°, 90°, 180°, 270°. As the oscillating scroll 2 swings, the crescent-shaped compression chamber 4 formed between the fixed scroll 1 and the oscillating scroll 2 gradually reduces its volume, and the gas taken into the compression chamber 4 is compressed. and is discharged from the discharge port 3. During this time, the distance from O to O' in Figure 1 is kept constant, and the distance between the spirals is expressed by a and the thickness by t.
OO'=a/2-t. a corresponds to the pitch of the spiral.

The outline of the device known as a scroll compressor is as above.

Next, the construction and operation of a specific embodiment of a scroll compressor, including this invention, will be explained in detail.

Figure 2 shows a specific example of a scroll compressor used in refrigeration or air conditioning, which is configured as a compressor for a gas such as chlorofluorocarbons, and has a so-called semi-closed configuration. This is what we are doing.

In the figure, 1 is a fixed scroll, 2 is an oscillating scroll, 3 is a discharge port, 4 is a compression chamber, 55 is an oscillating scroll shaft, 6 is a crankshaft, 7 is a bearing support,
8 is a motor rotor, 9 is a motor stator, 10 is a first balance, 11 is a second balance, 12 is a key, 13 is a spacer, 14 is a key, 15 is a washer, 16 is a rotation stopper, 17 is a rotor stopper nut, 18 is a stator, 19 is a bolt, 20 is a discharge chamber, 21 is a bolt, 22 is an O-ring,
23 is a shell, 24 is a stator fixing bolt, 25
is a washer, 26 is a support ring, 27 is a bottom plate, 2
8 is a suction screw hole, 29 to 32 are blind screw holes,
33 is an oil hole, 34 is an Oldham joint, 35 is a thrust bearing, 36 is a bearing metal, 37 is a bearing metal,
38 is a thrust bearing, 39 is a bearing metal, 40 is a hermetic terminal, 41 is a hermetic terminal,
42 is a crankshaft eccentric hole.

The above are the main components, and Figure 3 is a cross-sectional view taken along the - line in Figure 2. In the figure, 6 is the crankshaft, 7 is the bearing support, 34 is the Oldham joint, 35 is the thrust bearing, and 36 is the bearing metal. , 37 is a bearing metal, 42 is a crankshaft eccentric hole, 43 is an Oldham guide groove, 44 is an intake port, 45 is an O-ring groove, 4
6 is a through hole for a bolt, and 47 is a female thread.

Furthermore, FIG. 4 is a sectional view taken along the line -2 in FIG. 2, in which 1 is a fixed scroll, 2 is an oscillating scroll, 3 is a discharge port, 4 is a compression chamber, 46 is a through hole for a bolt, 47 is a female thread, 48 is the communication part.

The configuration of each component of the scroll compressor configured as described above will be explained in detail.

FIG. 5 is a perspective view showing a fixed scroll, and in the figure, 1 is a fixed scroll, 3 is a discharge port, 49 is a fixed scroll tooth, 50 is a fixed scroll base plate, 51 is a through hole for a bolt, and 52 is a fixed scroll. This is a counterbore for the scroll stopper bolt. The fixed scroll has a shape in which spiral grooves are provided in a disk having a uniform thickness, and fixed scroll teeth 49 are formed as a result of providing the grooves. The portion where the groove was not cut becomes the fixed scroll base plate 50.

A discharge port 3 is provided in the central portion of the fixed scroll base plate 50, and a thread is cut on the inner surface of the discharge port 3 to enable connection as required. The fixed scroll retaining bolt counterbore 52 is provided to prevent the head of the bolt from sinking into the counterbore when the discharge chamber 20 shown in FIG. 2 is installed.

FIG. 6 is a perspective view showing an oscillating scroll, in which 2 is an oscillating scroll, 53 is an oscillating scroll tooth, 54 is an oscillating scroll base plate, 55 is an oscillating scroll shaft, and 56 is an Oldham pawl. It is.

The oscillating scroll teeth 53 are connected to the oscillating scroll base plate 5.
4, and the Oldham pawl 56 and the swinging scroll shaft 55 are also integrally molded.

FIG. 7 is a perspective view of the swinging scroll seen from the back, and in the figure, 2 is the swinging scroll;
53 is an oscillating scroll tooth, 54 is an oscillating scroll base plate, 55 is an oscillating scroll shaft, 56 is an Oldham pawl, 57 is an oscillating scroll balancer, and 58 is a balancer fixing bolt. Oscillating scroll shaft 5
5 and the center of the swinging scroll base plate 54 are formed to coincide with each other. The Oldham pawl 56 is connected to the Oldham joint 34 shown in FIGS. 2 and 3.
It is a part that is fitted into the oscillating scroll 2 and regulates the positional relationship between the oscillating scroll 2 and the fixed scroll 3, and is a necessary part for realizing the oscillating movement of the oscillating scroll 2. The Oldham pawls 56 are arranged on a straight line passing through the center. Oscillating scroll shaft 55
is fitted into the crankshaft eccentric hole 42 of the crankshaft 6 shown in FIG. This is the part that makes exercise possible. The oscillating scroll balancer 57 is configured such that the center of gravity of the oscillating scroll teeth 53 of the oscillating scroll 2 is aligned with the oscillating scroll base plate 54 and the oscillating scroll shaft 5.
This is provided to correct the static imbalance caused by the center of the scroll shaft 55 not being aligned with the center of the scroll shaft 55. It's summery.

The balancer fixing bolt 58 fixes the swinging scroll balancer to the swinging scroll base plate 54.

FIG. 8 is a perspective view showing the bearing, and in the figure, 7 is a bearing support, 31 is a blind screw hole, 33 is an oil hole, 35 is a thrust bearing, 37 is a bearing metal,
38 is a thrust receiver, 43 is an Oldham guide groove, 4
4 is a suction port, 45 is an O-ring groove, 46 is a through hole for a bolt, and 47 is a female thread.

The bearing metal 37 portion of the bearing support 7 has a second
The crankshaft 6 shown in the figure is fitted, and the stepped portion of the crankshaft 6 comes to rest on the thrust receiver 38. The thrust bearing 35 is provided adjacent to the bearing metal 37 on the outside in the radial direction, has the function of supporting the back surface of the swinging scroll base plate 54, and receives the thrust applied from the swinging scroll 2. The Oldham guide groove 43 is a portion into which the Oldham joint 34 shown in FIG. 2 fits, and is a portion in which the Oldham joint 34 performs linear reciprocating motion.
In this embodiment, four suction ports 44 are provided, and they penetrate through the bearing support 7. The end face of the bearing support 7 is provided with an O-ring groove 45 for sealing, a female thread 47 for fixing the bearing support 7 and the fixed scroll 1, and a through hole for a bolt for fixing the entire bearing support 7. . The oil hole 33 for oil supply and the blind screw hole 31 communicating therewith are used, for example, when measuring oil supply pressure. The end face where the bolt through hole 46 and the female thread 47 are provided and the face of the thrust bearing 35 are such that the face of the thrust bearing 35 is closer to the thickness of the oscillating scroll base plate 54.
If the fixed scroll 1 is fixed to the end face when it has sunk by an amount of about 10 μm to 50 μm,
The swinging scroll 2 is designed to be able to swing. This situation is better understood in FIG.

FIG. 9 is a perspective view showing the Oldham joint,
In the figure, 34 is an Oldham joint, 59 is a bearing fitting pawl, 60 is an oscillating scroll fitting guide groove, 6
1 is a ring.

The Oldham joint 34, as shown in FIG.
This is to maintain the relative positional relationship between the fixed scroll 1 and the swinging scroll 2.
together with the crankshaft 6.

The bearing fitting pawl 59 fits into the Oldham guide groove 43 of the bearing 7, and the bearing fitting pawl 59 fits into the Oldham guide groove 43 of the bearing 7, and the oscillating scroll fitting guide groove 6
0 fits into the Oldham pawl 56 of the swinging scroll 2. The ring 61 is configured so that the bearing fitting pawl 59 and the swinging scroll fitting guide groove 60 are perpendicular to each other with respect to its center.

Due to the rotation of the crankshaft 6, the oscillating scroll 2
When the bearing 7 performs eccentric movement, the bearing fitting pawl 59 of the Oldham joint 34 engages the Oldham guide groove 43 of the bearing 7.
, the entire Oldham joint 34 performs a reciprocating linear motion in the direction of the Oldham guide groove. In this state, the swing scroll 2 fitted into the Oldham joint 34 via the swing scroll fitting guide groove 60 performs a reciprocating linear motion relative to the Oldham joint 34. As a result, the oscillating scroll 2 realizes an eccentric oscillating motion as a combination of two orthogonal reciprocating linear motions. The above is the configuration and operation of the Oldham joint 34.

FIG. 10 is a perspective view showing the crankshaft,
In the figure, 6 is the crankshaft, 33 is the oil hole, 3
6 is the bearing metal, 42 is the crankshaft eccentric hole, 6
2 and 63 are oil grooves, 64 and 65 are key grooves, 66 is a large diameter shaft portion of the crankshaft, and 67 is a rotor mounting portion. The crankshaft 6 is constituted by the large diameter shaft portion 66, and a stepped portion is formed between the crankshaft eccentric shaft portion 66 and the crankshaft small diameter shaft portion 67. 68 is a shaft fitting portion, 69 is a screw for a stator locking nut, and 70 is a groove for a locking washer.

The crankshaft 6 receives the driving force of the electric motor rotor 8 attached to the rotor mounting portion 67 and applies rotational force to the swinging scroll 2 fitted in the crankshaft eccentric hole 42.
A bearing metal 36 is provided in the crankshaft eccentric hole 42 into which the crankshaft 5 fits. The bearing metal 36 may be a normal bearing alloy, or may be a so-called needle roller bearing. The bearing metal 36 is provided with an oil groove 63 for oil supply, and this groove is normally cut on the opposite load side. The crankshaft eccentric shaft portion 66 fits into the bearing metal 37 portion of the bearing support 7 , and the stepped portion of the crankshaft 6 is supported by the thrust bearing 38 of the bearing support 7 . The eccentric shaft portion 66 of the crankshaft is also provided with an oil groove 62, which constitutes an oil supply path. Furthermore, oil grooves 62, 63
In the figure, two oil holes 33 are provided connected to the crankshaft 6, one of which passes through the central axis of the crankshaft 6 to supply oil to the shaft fitting portion 68. The keyway 64 is for fixing the first balance shown in FIG.
5 is a part to which the electric motor rotor 8 is attached. The shaft fitting portion 68 is a portion that fits into the bearing metal 37 of the bottom plate 27 shown in FIG.
radial movement is constrained and supported. The rotor locking nut 17 shown in FIG. 2 is attached to the stator locking nut screw 69, and the locking washer 16 of the rotor locking nut 17 fits into the locking washer groove 70.

FIG. 11 is a perspective view showing the first balance, and in the figure, 10 is the first balance, 17 is a balance weight, 72 is a cylindrical part, 73 is a fixed part,
74 is a keyway.

As can be understood from FIG. 2, the first balance 10, together with the second balance 11, performs balancing against the centrifugal force derived from the eccentric rocking motion of the rocking scroll 2, and balances the entire rotating system. This ensures quiet operation. First balance 10
The key groove 6 of the crankshaft 6 is inserted into the key groove 74 provided in the fixing part 73 by the key 12.
It is fixed at 4. The balance weight 71 is installed via a cylindrical portion 72 so as to be located in a space formed between the bearing support 7 and the electric motor stator 9 in order to downsize the entire compressor. Also,
The balance weight 17 is brought as close as possible to the oscillating scroll 2 in the axial direction, and the crankshaft 6
By radially separating the balance weight 71 from the center of the balance weight 71 as much as possible, the mass of the balance weight 71 is reduced. When the oscillating scroll 2 is made of commonly used cast iron or spheroidal graphite cast iron,
Its mass cannot be ignored, and the mass of the balance weight 71 also increases, so the above measures are taken to prevent the compressor as a whole from becoming too large in the axial direction.

The first balance 71 is installed making good use of the space created between the bearing support 7 and the electric motor stator 9, and contributes to downsizing the entire system.

FIG. 12 is a perspective view showing the electric motor rotor, and in the figure, 8 is the electric motor rotor, 11 is a second balance, 75 is an end ring, and 76 is a keyway. The electric motor rotor 8 is fixed in a keyway 65 of the crankshaft 6 with a key 14 that fits in a keyway 76, and provides rotational force to the crankshaft 6.
An oscillating scroll 2 is attached to one end of the end ring 75.
A second balance 11 is provided which opposes the first balance 10, and together with the first balance 10, reduces the overall vibration.

FIG. 13 is a perspective view of the electric motor rotor 8 of FIG. 12 viewed from the opposite side, and in the figure, 8 is the electric motor rotor, 11 is the second balance, 18 is the stirrer, and 19
is the bolt, 75 is the end ring, 76 is the keyway,
77 is a stator fixing screw hole. The second balance 11 is fixed to the end ring 75 by a bolt 19. Further, the stirrer 18 is provided on the end ring 75 and the second balance 11.
It is fixed in the stator fixing screw hole 77.

The above-mentioned parts are assembled as shown in the assembly diagram of FIG. 14.

In FIG. 14, first, the crankshaft 6 is fitted into the bearing support 7, and then the Oldham joint 34 is inserted into the bearing support 7. The swinging scroll 2 is fitted onto the crankshaft 6 from above the Oldham joint 34, and the fixed scroll 1 is fixed from above to the bearing support 7 with bolts 78. Attach the first balance 10 from the bottom of the crankshaft 6, insert the spacer 13 therein to determine the axial position of the motor rotor 8, and install the washer 1 from the bottom of the motor rotor 8.
5. Insert the locking washer 16 and tighten the rotor locking nut 17 to secure the first balance 10 and spacer 1.
3. Crankshaft 6 with electric motor rotor 18 integrated
Fixed to. As can be seen from FIG. 2, the first balance 10 corresponds to the stepped portion of the crankshaft 6 and serves as a stopper. A second balance 11 and a stirrer 18 are attached to the electric motor rotor 8.

FIG. 15 is an assembly diagram showing the procedure for assembling the entire interior of the compressor assembled in FIG. 14.

The discharge chamber 20 is fixed to the upper surface of the assembled fixed scroll 1 with bolts 79. An O-ring 22 is attached to the discharge chamber 20 for sealing, as shown in FIG. The bolt 79 passes through the fixed scroll 1 and is screwed into a female thread 80 provided on the upper surface of the shell 23 to achieve fixation. The electric motor stator 9 is fixed to the shell 23 by stator fixing bolts 24 shown in FIG. An O-ring 22 is attached to the upper end surface of the shell 23 in an O-ring groove 81 for sealing. Reference numeral 82 shown in FIG. 15 is a coil end of the motor stator 9.
As can be seen from FIG. 2, a spigot is provided on the back side of the bearing 7 and is fitted into the shell 23. This consists of the motor rotor 8 and the motor stator 9.
This is to accurately bring out the air gap formed concentrically between the two.

Hermetically sealed terminal 4 is located on the outer periphery of shell 23.
0 and 41 are welded together. For example, the two-pin hermetically sealed terminal 40 is for the winding protection circuit of the motor stator 9, and the three-pin hermetically sealed terminal 41 supplies three-phase alternating current to the motor stator 9. It serves as an insulator for the shell 23 and as a seal against the outside air.

FIG. 16 is an assembly diagram showing how the bottom plate 27 is finally fixed to the shell 23 after being assembled as described above. It fits into the joint part 68. In order to realize this concentricity, a pilot part 87 is provided. Also, O-ring groove 9 for sealing.
0 is fitted with an O-ring 22. This bottom plate 27 is fixed to the shell 23 by a female thread 85 of a shell flange 84 of the shell 23 and a bolt 89. A suction screw hole 28 is provided in the bottom plate 27.

As described above, the assembly is completed in the state shown in Fig. 2.

The operation of the scroll compressor as a whole shown in FIG. 2 will be briefly explained.

When, for example, three-phase alternating current is supplied to the motor stator 9 through the hermetic terminal 41, the motor rotor 8 generates torque and rotates together with the crankshaft 6. When the crankshaft 6 starts rotating, rotational force is transmitted to the swinging scroll shaft 55 that fits into the crankshaft eccentric hole 42, and the swinging scroll 2 is guided by the Oldham joint 34 attached to the bearing support 7, and the swinging scroll 2 is guided by the Oldham joint 34 attached to the bearing support 7, Achieve rocking motion. Then, a compression action as shown in FIG. 1 is performed, and the compressed gas is discharged from the discharge port 3. Gases such as chlorofluorocarbons are inhaled through the suction screw hole 28 of the bottom plate 27, pass through the air gap between the motor rotor 8 and the motor stator 9, and the gap between the motor stator 9 and the shell, and then enter the suction port 44 provided in the bearing support 7. (see Fig. 3), the compression chamber 4 between the oscillating scroll 2 and the fixed scroll 1 via the communication part 48.
be taken in. This is the outline of the operation. For example, if the oil supply system has an oil separator (not shown) built in the discharge chamber 20, the oil separated in the discharge chamber 20 is separated from the fixed scroll 1.
It reaches the bearing metal 37 through an oil hole 33 provided in the bearing support 7 and an oil hole 33 provided in the bearing support 7. Furthermore, each part of the thrust bearing 35, bearing metal 39, and thrust bearing 38 is also supplied with oil through the oil hole 33 and oil grooves 62, 63 shown in FIG. Thrust bearing 35
The oil that has passed through is taken into the compression chamber together with the inhaled gas. Thrust bearing 38, bearing metal 39
The oil flows out into the shell 23, is atomized by the flow rate of the suction gas and the action of the stirrer 18, and is taken into the compression chamber together with the suction gas. The oil taken into the compression chamber 4 together with the intake gas flows through the fixed scroll teeth 49 (see Figure 5).
The radial and axial gaps between the oscillating scroll teeth 53 and the oscillating scroll teeth 53 are filled to minimize leakage. The oil flowing out from the thrust bearing 35 also lubricates each sliding surface of the Oldham joint 34. The oil that has flowed into the discharge chamber 20 again in this manner is separated by an oil separator (not shown) and is forced into the oil supply line by the pressure of the discharged gas. During this time, if the oil is not separated by the oil separator, it is circulated through the refrigeration cycle and passed through the suction screw hole 2 along with the suction gas when used as a refrigerator.
It will come back to 8. Furthermore, the oil separator need not be provided within the discharge chamber 20, but may be provided as a separate body outside.

The motor protection device connected by the hermetically sealed terminal 40 detects an overload of the motor stator 9 or a temperature rise during abnormal operation, etc.
This protects the motor stator 9 by cutting off, for example, a three-phase AC power supply.

Now, let us explain in more detail the construction and operation of the thrust bearing of the above embodiment.

In FIG. 2, the oil flowing into the contact area P between the rocking scroll 2 and the thrust bearing 35 of the bearing support 7 is pressure-fed from an oil separator (not shown) by the discharge gas pressure, resulting in pressure loss in the oil path. By setting it to an appropriate value by design,
It has a specified pressure. The force obtained by integrating this pressure over the entire thrust bearing 35 opposes the thrust force of the pressure derived by the oscillating scroll 2 in the compression chamber 4 .

If the integrated pressure of the hydraulic pressure is less than or equal to the thrust force, the surfaces R and S where a gap may occur in the axial direction in Fig. 2 are set to the value 10 at the time of design.
It will be operated with a gap of about 50 μm. Further, a similar gap is created between the end face of the fixed scroll 1 and the opposing face Q of the upper end face of the swing scroll base plate 54 of the swing scroll 2.

When operating in this state, axial sealing of the R and S surfaces will be achieved by the oil taken into the compression chamber 4. In this case, the thrust force is received entirely by the thrust bearing 35. According to experiments, a flow rate sufficient for practical use is secured due to the sealing effect of oil. In this state, wear of the thrust bearing 35 due to insufficient lubrication during startup or shutdown poses a problem in maintaining the axial clearance, but this can be solved by selecting the material.

Furthermore, if the design is such that the integrated value of the oil pressure is greater than the thrust force, the swinging scroll 2 will be pushed upward and will slide on the plane R, S, or Q in FIG. .
In the case of sliding on the R surface, the tip surface of the oscillating scroll tooth 53 (see FIG. 6) of the oscillating scroll 2,
The bottom surface of the fixed scroll base plate 50 (see FIG. 5) on the compression chamber side of the fixed scroll 2 will slide, and even in this case, a sufficient pressure-receiving area of the tip surface of the oscillating scroll teeth 53 can be secured. It is possible to drive. Both sliding surfaces are lubricated with oil taken into the compression chamber 4.

In the case of sliding on the S surface, the end surface of the fixed scroll teeth 49 of the fixed scroll 1 and the upper surface of the swinging scroll base plate 54 of the swinging scroll 2 will slide, and as in the case described above, both operation and lubrication will be affected. It is possible.

If the peripheral part of the upper surface of the oscillating scroll base plate 54 of the oscillating scroll 2 is made a little thicker so that it slides on the plane Q in FIG. As a result, instead of the thrust bearing 35, the outer periphery of the end surface of the fixed scroll 1 slides on the periphery of the upper surface of the oscillating scroll base plate 54, and in this case as well, lubrication, operation, and sealing are possible.

When the thrust force is directed upward like this, the section P is operated with the clearance maintained at a certain value.

The thrust bearing 35 designed to satisfy these requirements can be operated even if load fluctuation occurs and the direction of the total thrust force changes.

In this invention, the radial portion T in FIG. 2 has a certain clearance of 10 to 50 μm and is sealed with oil. To summarize and explain the important improvements in the above embodiment, the fixed scrolls each have spiral scroll teeth and are combined with each other so that the scroll teeth form a refrigerant compression chamber 4 between them. 1 and an oscillating scroll 2, the oscillating scroll 2 is driven by a crankshaft 6 to compress the refrigerant. In addition, an eccentric hole 42 is provided in the end face of the crankshaft 6 on the side of the orbiting scroll 2, and the orbiting scroll shaft 55 is provided in the eccentric hole 42.
The scroll shaft 55 is supported in the circumferential direction via the crankshaft 6, and the scroll shaft 55 is supported via the crankshaft 6 over a range extending from the center in the axial direction to both sides in the axial direction. A radial bearing 37 that supports the crankshaft 6 from the outside is provided over a range extending from the axial center of the scroll shaft 55 to both sides in the axial direction. A thrust bearing 35 is provided to surround the radial bearing 37 and to which the oil supplied to the radial bearing 37 is supplied. A scroll compressor is shown in which the thrust bearing 35 and the radial bearing 37 are provided on a common bearing support 7. In other words, since the relative relationship between the oscillating scroll shaft 55, the eccentric hole 42 on the end face of the crankshaft 6, and the radial bearing 37 on the outer periphery of the tip of the crankshaft is configured as described above, the portion supporting the oscillating scroll shaft 55, i.e. Both the point of application of the load force acting on the peripheral wall of the eccentric hole 42 and the point of application of the load force acting on the radial bearing 37 on the outer periphery of the tip end of the crankshaft 6 can be brought as close as possible to the oscillating scroll 2 side. The deviation in the axial direction between the two points of action can be reduced, and this is due to the twisting of the part that supports the oscillating scroll shaft 55 and the part of the radial bearing 37 that supports the outer periphery of the end of the oscillating scroll 2 side of the crankshaft 6. Damage or wear and tear can be suppressed. Also, the relationship between the swinging scroll shaft 55, the eccentric hole 42 on the end face of the crankshaft 6, the radial bearing 37 on the outer periphery of the tip of the crankshaft, the thrust bearing 35 that receives the thrust load of the swinging scroll 2, and the bearing support 7 Since the relationships are configured as described above, that is, the end surfaces of the crankshaft 6, radial bearing 37, and thrust bearing 35 on the side of the oscillating scroll 2 should be brought as close as possible to the surface of the oscillating scroll 2 on the side opposite to the teeth thereof. Since the radial bearing 37 and the thrust bearing 35 are provided on the common bearing support 7, the area around the bearings becomes compact, and the connection from the radial bearing 35 to the thrust bearing 35 is reduced. This simplifies the oil supply route and ensures reliable oil supply.

As described above, the present invention includes a fixed scroll and an oscillating scroll, each having spiral scroll teeth and combined with each other so that the scroll teeth form a refrigerant compression chamber between them,
In a scroll compressor that compresses the refrigerant by driving the oscillating scroll by a crankshaft, the oscillating scroll is provided with a protruding oscillating scroll shaft extending on a side opposite to the scroll teeth; An eccentric hole is provided in the end face of the crankshaft on the side of the oscillating scroll, the oscillating scroll shaft is supported in the eccentric hole, the scroll shaft is circumferentially surrounded via the crankshaft, and the scroll shaft is aligned with its axis. a radial bearing that supports the crankshaft from the outside over a range extending from the axial center of the scroll shaft to both axial directions; A thrust bearing is provided adjacent to the radial outer side of the radial bearing so as to surround the radial bearing, and is supplied with the oil supplied to the radial bearing. The surface of the scroll opposite to the fixed scroll is supported, and the thrust bearing and the radial bearing are provided on a common bearing support, so that the part that supports the oscillating scroll shaft and the oscillation of the crankshaft are prevented. Damage or wear due to twisting of the radial bearing that supports the outer periphery of the end of the scroll is suppressed by suppressing the moment acting on the crankshaft. This has important effects in commercialization, such as making the area around the bearing including the radial bearing more compact, and simplifying the oil supply path from the radial bearing to the thrust bearing.

[Brief explanation of drawings]

Figure 1 is a diagram of the operating principle of a scroll compressor, Figure 2
The figure is a cross-sectional view showing one embodiment of the scroll compressor of the present invention, FIG. 3 is a cross-sectional view taken along the line -- in FIG. 2, FIG. 4 is a cross-sectional view taken along the line - - in FIG. 6 is a perspective view showing the swinging scroll, FIG. 7 is a perspective view showing the swinging scroll, FIG. 8 is a perspective view showing the bearing, and FIG. 9 is a perspective view showing the Oldham joint. Fig. 10 is a perspective view showing the crankshaft, Fig. 11 is a perspective view showing the first balance, Figs. 12 and 13 are perspective views showing the motor rotor, Fig. 14 is an assembled view of the compressor, Fig. 15, 1st
Figure 6 is an assembly diagram of the entire compressor including the shell. In the figure, 1 is a fixed scroll, 2 is an oscillating scroll, 4 is a compression chamber, 6 is a crankshaft, 7 is a bearing support, 35 is a thrust bearing, and 36 and 37 are bearing metals. Note that the same reference numerals in the figures indicate the same or equivalent parts.

Claims (1)

[Claims] 1. A fixed scroll and an oscillating scroll each having spiral scroll teeth and combined with each other so that the scroll teeth form a refrigerant compression chamber between them, and the oscillating scroll is driven by a crankshaft. In the scroll compressor for compressing the refrigerant, the oscillating scroll is provided with an oscillating scroll shaft extending on the side opposite to the scroll teeth, and an oscillating scroll shaft extending on the opposite side from the scroll teeth is provided on the oscillating scroll, and an oscillating scroll shaft is provided on the end face of the crankshaft on the oscillating scroll side. An eccentric hole is provided, the oscillating scroll shaft is supported in the eccentric hole, the scroll shaft is circumferentially surrounded via the crankshaft, and the scroll shaft is extended over a range extending from its axial center to both sides in the axial direction. A radial bearing is provided which supports the crankshaft from the outside over a range extending from the axial center of the scroll shaft to both sides in the axial direction, and from the radial bearing to the outside in the radial direction. A thrust bearing is provided adjacent to the radial bearing and is supplied with the oil supplied to the radial bearing. A scroll compressor, characterized in that the thrust bearing and the radial bearing are provided on a common bearing support.