JPH0116345B2 - - 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 compresses refrigerant by driving the oscillating scroll.

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.

However, although JP-A No. 53-35840 shows a vertical scroll compressor,
As mentioned above, the focus has been on the compression chamber sealing means and the thrust bearing of the oscillating scroll, and specific proposals have been made to reduce damage to the radial bearing caused by twisting that acts on the part that receives the oscillating scroll shaft. It hasn't been talked about. Additionally, U.S. Patent No.
In the specification of 3874827, an oscillating scroll and a crankshaft are arranged above a fixed scroll, an on-crankshaft balancer 79 is formed of the same material, and the oscillating scroll shaft is fitted into a hole in the lower end surface of the crankshaft. However, similar to the above-mentioned Japanese Patent Application Laid-Open No. 53-35840, there are no specific proposals for reducing damage to the radial bearing caused by strain acting on the part that receives the oscillating scroll shaft. It hasn't been done. Also, if the device described in this U.S. patent were to be turned upside down and the oscillating scroll and crankshaft were placed below the fixed scroll,
Since the balancer 79 is located above the crankshaft bearing 80 and the oscillating scroll shaft 72, the oscillating scroll shaft 70 becomes longer in the axial direction. Since it is provided in the lower half of the bearing 70, when the oscillating scroll oscillates, the gas load force acts as a force to tilt the crankshaft, and this force to tilt the crankshaft is applied to the bearing 72. This acts as a large twisting force and damages the bearing 72. Note that the above phenomenon that acts to tilt the crankshaft occurs in the case of a structure in which the oscillating scroll and the crankshaft are coupled together to drive the oscillating scroll.
The inventors have confirmed through actual measurements that this problem is likely to occur even if the oscillating scroll is supported by a thrust bearing. 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. bearing 80 immediately in the radial direction.
Since the bearing 80 cannot receive the large moment caused by the oscillating motion of the oscillating scroll, the bearing 80
This causes the bearing 80 to be easily worn out. Much less,
In Japanese Patent Application Laid-Open No. 53-35840, the above moment is applied to a radial bearing 13 located considerably below the oscillating scroll shaft.
2, the bearing 13 becomes considerably large.
2 wear and tear is unavoidable.

In view of the above-mentioned conventional situation, the present invention reduces the moment generated on the crankshaft due to the oscillating motion of the oscillating scroll, and reduces damage or wear due to twisting of the bearing part of the oscillating scroll shaft and the bearing part of the crankshaft. Specifically, it is a fixed scroll and an oscillating scroll that each have spiral scroll teeth and are combined with each other so as to form a refrigerant compression chamber between these scroll teeth. A scroll compressor for compressing the refrigerant by driving the oscillating scroll with a crankshaft, the oscillating scroll shaft protruding from a side opposite to the scroll teeth of the oscillating scroll, and a An eccentric hole is provided in the end face on the oscillating scroll side, the oscillating scroll shaft is supported in the eccentric hole via a first bearing metal, and the shaft extends from the axial center of the first bearing metal to both sides in the axial direction. A second bearing metal is provided to surround and support the outer periphery of the end of the crankshaft on the oscillating scroll side over a range, and both of the bearing metals and the end face of the crankshaft on the oscillating scroll side are substantially the same. This is a scroll compressor characterized by being located on a surface.

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 fulcrum 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
Move 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, and in the figure, 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 a communication portion.

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 has a function of supporting the back surface of the oscillating scroll base plate 54.
It 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 is fitted, and is a portion through which the Oldham joint 34 performs linear reciprocating motion. In this embodiment, four suction ports 44 are provided.
It passes 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 whole. . 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 10 μm thicker than the face of the thrust bearing 35 due to the thickness of the rocking scroll base plate 54.
It is sunk by about 50 μm, so that when the fixed scroll 1 is fixed to the end face, the swinging scroll 2 can 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 large diameter 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 is arranged so that its upper end surface is located on the same plane as the bearing metal 37 and the upper end surface of the large diameter shaft portion 66 of the crankshaft 6, as shown in FIG. Also,
This bearing metal 36 may be a normal bearing alloy, or may be a so-called needle roller bearing. The bearing metal 36 has an oil groove 6 for oil supply.
3 is provided, which is usually cut on the anti-load side. The crankshaft large diameter 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 large-diameter crankshaft shaft portion 66 is also provided with an oil groove 62, which constitutes an oil supply path. Furthermore, oil holes 33 are provided at two locations in the figure, connected to the oil grooves 62 and 63, one of which penetrates the central axis of the crankshaft 6 so that oil can be supplied to the shaft fitting portion 68. It's summery. keyway 64
is for fixing the first balance shown in FIG. 2, and the keyway 65 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. 2, and restrains and supports movement of the crankshaft 6 in the radial direction. The stator locking nut screw 69 has
The rotor locking nut 17 shown in FIG. 2 is attached, and the claw portion of the locking washer 16 of the rotor locking nut 17 is inserted 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. Daiichi 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 74 is positioned in the space formed between the bearing support 7 and the motor rotor 9 in order to downsize the entire compressor.
It is installed via the cylindrical portion 72. Also, the part of the balance weight 71 should be
By axially approaching the crankshaft 6 and radially away from the center of the crankshaft 6 as much as possible,
The mass of the balance weight 71 is reduced. If 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 will also be large, so the measures described above should be taken. This prevents the entire compressor 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 motor rotor, and in the figure, 8 is the motor rotor, 11 is the second balance, 74 is the end ring, and 76 is the 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 vibration, and works together with the first balance 10 to reduce 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 connects to the shell 2.
3 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 is to accurately create an air gap formed concentrically between the motor rotor 8 and the motor stator 9.

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. The gas, such as fluorocarbon, flows in through the suction screw hole 28 of the bottom plate 27, passes 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 23, and then reaches the suction port provided in the bearing support 7. 44 (see FIG. 3), and is taken into the compression chamber 4 between the swinging scroll 2 and the fixed scroll 1 via the communication portion 48. This is the outline of the operation,
In the oil supply system, for example, if the discharge chamber 20 has a built-in oil separator (not shown), the oil separated in the discharge chamber 20 is transferred to the oil hole 33 provided in the fixed scroll 1 and the oil provided in the bearing support 7. It reaches the bearing metal 37 through the hole 33. Furthermore, the oil hole 33 and oil grooves 62, 63 shown in FIG.
Through this, each part of the thrust bearing 35, bearing metal 39, and thrust bearing 38 is also supplied with oil. The oil that has passed through the thrust bearing 35 is taken into the compression chamber together with the suctioned gas. The oil that has passed through the thrust receiver 38 and the bearing metal 39 flows 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 suction gas fills the radial and axial gaps between the fixed scroll teeth 49 (see Figure 5) and the oscillating scroll teeth 53 to minimize leakage. It has a suppressing effect. 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, the oil will circulate through the refrigeration cycle and return to the suction screw hole 28 together with the suction gas, if the apparatus is used as a refrigerator, for example. 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 on the motor stator 9 or a temperature rise during abnormal operation, and shuts off, for example, a three-phase AC power supply that is being supplied to the motor stator 9. This is to provide protection.

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 the oil separator shown in the figure by the discharge gas pressure, and the oil flows under pressure in the oil path. By setting the loss 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 slides, and even in this case, the pressure receiving area of the tip surface of the oscillating scroll teeth 53 can be secured sufficiently, so that operation is possible. It is possible. 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 in detail the important features improved with respect to the above-described embodiments, the fixed scrolls 1 and 1 have spiral scroll teeth and are combined with each other so as to form refrigerant compression chambers between these scroll teeth. In a scroll compressor that includes an oscillating scroll 2 and compresses the refrigerant by driving the oscillating scroll 2 with a crankshaft 6, an oscillating scroll shaft 55 is provided on the side opposite to the scroll teeth of the oscillating scroll 2. is provided protrudingly, and an eccentric hole 42 is provided on the end face of the crankshaft 6 on the side of the oscillating scroll 2.
2 supports the oscillating scroll shaft 55 via a first bearing metal 36, and this first bearing metal 3
The oscillating scroll 2 of the crankshaft 6 extends from the axial center of the crankshaft 6 to both sides in the axial direction.
A second bearing metal 37 that surrounds and supports the outer periphery of the side end is provided, and both the bearing metals 36, 37 and the end face of the crankshaft 6 on the side of the oscillating scroll 2 are located on substantially the same plane. An improved scroll compressor is shown. With this configuration, the first and second bearing metals 36 and 37 can be brought as close as possible to the swinging scroll 2, and furthermore,
The point of application of the force that the first bearing metal 36 receives and the second
The point of application of the force received by the bearing metal 37 of the bearing metal 37 can be brought as close as possible to the point of application of the force, and therefore, due to the oscillating movement of the oscillating scroll 2,
The moment in the direction of tilting, that is, the direction of twisting, can be suppressed to a minimum, and both bearing metal 36,
37 can be suppressed, and a highly reliable scroll compressor that can maintain desired characteristics over a long period of time can be realized.

As described above, the present invention includes a fixed scroll and an oscillating scroll that each have spiral scroll teeth and are combined with each other so as to form a refrigerant compression chamber between these scroll teeth. In a scroll compressor that compresses the refrigerant by driving an oscillating scroll, an oscillating scroll shaft is provided protrudingly on a side opposite to the scroll teeth of the oscillating scroll, and an oscillating scroll shaft is provided on an end surface of the crankshaft on the side of the oscillating scroll. An eccentric hole is provided, and the oscillating scroll shaft is supported in the eccentric hole via a first bearing metal. A second bearing metal is provided to surround and support the outer periphery of the end on the oscillating scroll side, and both of the bearing metals and the end face of the crankshaft on the oscillating scroll side are located on substantially the same plane. This is what I did. In a device in which the oscillating scroll shaft of the oscillating scroll is supported in the eccentric hole of the crankshaft, for example, the second bearing metal at the tip of the crankshaft is connected to the first bearing metal of the oscillating scroll shaft. If it is located below the upper end surface, the point of application of the force acting on both bearing metals is shifted, creating a moment on the crankshaft, causing the crankshaft to tilt, causing partial contact with the second bearing metal at the tip of the crankshaft. However, in this invention, since both bearing metals and the end face of the crankshaft on the oscillating scroll side are located on almost the same plane, the effect on both bearing metals is Each point of application of force is as close as possible to the oscillating scroll, and both points of application are hardly displaced in the axial direction, so the above problems are solved and a highly reliable scroll compressor with good bearing performance is obtained. be able to.

[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, 36,
37 is a bearing metal. 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 as to form a refrigerant compression chamber between the scroll teeth, and the oscillating scroll is driven by a crankshaft. In the scroll compressor for compressing the refrigerant, an oscillating scroll shaft is provided protrudingly on the side opposite to the scroll teeth of the oscillating scroll, and the oscillating scroll is provided in an eccentric hole in an end face of the crankshaft on the oscillating scroll side. The shaft is supported via a first bearing metal, and the shaft is supported by surrounding the outer periphery of the end of the crankshaft on the oscillating scroll side over a range extending from the axial center of the first bearing metal to both sides in the axial direction. Scroll compression characterized in that a second bearing metal is provided, and both the bearing metals and the end face of the crankshaft on the oscillating scroll side are located close to the oscillating scroll and on substantially the same plane. Machine.