JP2930046B2 - Scroll compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly, to a scroll compressor used for refrigeration and air conditioning equipment.

[0002]

2. Description of the Related Art For example, a conventional scroll compressor disclosed in Japanese Patent Application Laid-Open No. 63-80088 was constructed as shown in FIG. 17, 1 is a fixed scroll, 2 is a revolving scroll, 3 is a crankshaft, 4 is a drive bush rotatably mounted on a bearing 2a formed on the revolving scroll 2, 5 is an Oldham ring, and 6 is a main frame. , 6a are main bearings formed on the main frame 6, 7 is a motor stator, 8 is a motor rotor, 9 is a sub-frame, 9
a denotes a sub-bearing formed on the sub-frame 9, 10 denotes a closed container, 11 denotes a suction pipe for guiding a refrigerant from the outside, 12 denotes a discharge pipe, and 13 denotes lubricating oil stored at the bottom of the closed container. An eccentric shaft portion 3a is formed at an upper end portion of the crankshaft 3, and the eccentric shaft portion 3a is formed on a lower surface of a base plate of the orbiting scroll 2 with a driving bush 4 interposed therebetween.
a. The crankshaft 3 has an upper main shaft portion 3b supported by a main bearing 6a of a main frame 6, and a lower sub shaft portion 3c supported by a sub bearing 9a of a sub frame 9. Reference numerals 14 and 15 denote upper balance weights and lower balance weights attached to both sides (up and down) of the motor rotor 8.

Next, the operation of the conventional scroll compressor shown in FIG. 17 will be described. The rotational force of the electric motor is transmitted by the crankshaft 3 fixedly fitted to the electric motor rotor 8 and transmitted to the orbiting scroll 2 via the eccentric shaft 3a and the drive bush 4. Orbiting scroll 2
Performs a revolving motion that moves in a circular orbit by an Oldham ring 5 that is a rotation preventing mechanism, and the refrigerant is compressed in accordance with a change in the volume of a compression chamber formed between the scroll and the fixed scroll 1.

[0004] The refrigerant flows into the closed vessel 10 from the external refrigeration cycle through the suction pipe 11, is compressed in the compression chamber, becomes high pressure, and flows out of the discharge pipe 12 to the external refrigeration cycle. By the way, of the refrigerant compression load acting on the orbiting scroll 2, the thrust direction force is supported by the thrust bearing surface 6 b on the upper end surface of the main frame 6, while the radial direction force Fg is changed by the drive bush 4 as shown in FIG. The crankshaft 3 is supported by a main bearing 6 a provided on a lower boss portion of the main frame 6 and a sub-bearing 9 a provided on a sub-frame 9.

[0005] An upper balance weight 14 and a lower balance weight 15 mounted above and below the motor rotor 8 are
Centrifugal force FC1 generated by the revolving motion of the orbiting scroll 2
The centrifugal forces FC2 and FC3 generated by the upper balance weight 14 and the lower balance weight 15 are also supported by the main bearing 6a and the auxiliary bearing 9a. The lubricating oil 13 stored at the bottom of the sealed container 10 is sent to sliding parts such as bearings and compression chambers by centrifugal force accompanying rotation of the crankshaft 3.

[0006]

As described above, in the conventional scroll compressor, the radial force Fg acting on the orbiting scroll during the compression stroke acts on the eccentric shaft portion 3a which is the upper end portion of the crankshaft 3. However, the eccentric shaft portion 3a, which is the point of application, is a protruding end portion of the main frame 6 opposite to the main bearing 6a and the sub-bearing 9a.
As shown in FIG. 9, the crankshaft 3 deforms flexibly. When the crankshaft 3 is bent, the inclination of the eccentric shaft 3a in the bearing 2a of the orbiting scroll 2, the inclination of the main shaft 3b in the main bearing 6a of the main frame 6, or the auxiliary bearing of the sub-frame 9 9a, the inclination of the sub shaft portion 3c occurs,
As a result, the load capacity of each bearing decreases,
There is a problem that image sticking occurs.

In particular, in recent years, in an air conditioner or the like, the operating range of the compressor has been expanded from a low speed to a high speed due to the variable speed operation of the compressor by inverter control. In the high-speed driving range, the orbiting scroll 2 and the upper balance weight 1
4. The centrifugal force FC generated by the lower balance weight 15
1, FC2, and FC3 increase, and the bending deformation of the crankshaft 3 further increases, and the above-mentioned problem occurs more remarkably.

SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned conventional problems, and it is an object of the present invention to provide a bearing in which even if a bending deformation occurs on a crankshaft due to a radial force of a compressive load acting on an orbiting scroll during a compression stroke. It is an object of the present invention to provide a highly reliable scroll compressor by preventing the occurrence of damage such as wear and seizure of a portion.

[0009]

A scroll compressor according to a first aspect of the present invention compresses a fluid, a rotatable crankshaft having an eccentric shaft portion at an end, a fixed scroll, and a fluid. A pivoting scroll cooperating with the stationary scroll for rotating the pivoting scroll with the eccentric shaft to revolve the pivoting scroll.
And a bearing means, said first bearing means, the swivel scroll - a drive bush rotatably fitted in the bearing portion Le, the between the eccentric shaft portion and the driving bush
It has a curved surface portion curved only along the axial direction of the crankshaft and an opposing engagement surface portion formed by a combination of a flat surface portion.

[0010]

[0011]

[0012]

[0013] Scroll compression according to the second invention.
The machine has a rotatable crankshaft with an eccentric shaft at the end,
A fixed scroll and said fixed scroll for compressing the fluid.
A turning scroll cooperating with a roll, and the turning scroll
The orbiting scroll is eccentric in order to revolve
First bearing means rotatably coupled to the shaft,
The first bearing means is provided on a bearing portion of the orbiting scroll.
A drive bush rotatably fitted to the drive bush;
Axis direction of the crankshaft between the shaft and the eccentric shaft portion
Engaging surface part by combination of curved surface part and flat part along
And a curved surface portion of the eccentric shaft portion and the drive bush.
Or the flat portion of the eccentric shaft portion and the drive block.
A high-hardness member is placed between the
You .

The scroll compression according to the third invention.
The machine comprises a closed container, a fixed scroll, and the fixed scroll.
A swirling scroll for compressing the fluid in cooperation with the scroll;
A motor stator fitted and fixed in a closed container;
Main frames fitted and fixed to the closed container on both sides of the machine
And the sub-frame and the turning scroll
And the radius of the bearings of the main frame and the sub-frame
Crank with main shaft and counter shaft supported in two directions
A shaft, and a rotor of the electric motor fitted and fixed to the crankshaft
And a balance weight that rotates integrally with the crankshaft.
Transports the lubricating oil disposed at the lower end of the crankshaft.
Refueling pump and an upper end of the crankshaft
The eccentric shaft and the revolving scroll are revolved.
In order to rotate the turning scroll on the eccentric shaft,
Coupling first bearing means, said first bearing means
Are formed on a part of the outer peripheral surface of the eccentric shaft portion.
Curved surface along the axial direction of the link shaft, and the turning scroll
The bearing is rotatably fitted to the bearing portion of the
A position corresponding to the curved surface of the eccentric shaft,
And a drive bush having a flat part
There is .

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION

Embodiment 1 FIG. Hereinafter, embodiments of the scroll compressor according to the present invention shown in the drawings will be described in more detail. FIG. 1 shows a scroll compressor 20 according to a first embodiment of the present invention. In FIG. 1 showing the scroll compressor 20 of the present embodiment, the same or corresponding parts as those of the conventional scroll compressor shown in FIG. 17 are denoted by the same reference numerals, and the description thereof will be omitted.

The scroll compressor 20 according to the present embodiment
A crankshaft 21 to which the rotor 8 of the electric motor is fixed by shrink-fit at a substantially axially intermediate portion is included. This crankshaft 2
Reference numeral 1 denotes an eccentric shaft portion 22 which is fitted into a bearing portion 2a of the orbiting scroll 2 and directly imparts a turning force to the orbiting scroll 2, and is integrally formed at an upper end portion. A main shaft portion 23 supported by the main bearing portion 6a and a sub shaft portion 24 supported by the sub bearing portion 9a of the sub frame 9 are formed at a lower end portion. A bearing device for supporting the eccentric shaft portion 22, the main shaft portion 23, and the sub shaft portion 24 formed on the crankshaft 21, that is, a bearing structure will be sequentially described.

FIGS. 2 and 3 are sectional views schematically showing a bearing structure of an eccentric shaft portion 22 formed at an upper end portion of a crankshaft 21 in a scroll compressor 20 according to the present embodiment. As is apparent from FIG. 2, the eccentric shaft portion 22 has an outer shape based on a circle whose center point O2 is a position shifted by a predetermined distance from the center O1 of the crankshaft 21, and has two center points O1. When a line connecting O2 and Y2 is represented by YY and a line perpendicular thereto is represented by XX, a flat surface portion 22a is formed at a position on the peripheral surface of the eccentric shaft portion 22 in a direction along the YY line. Also, the flat surface portion 22 in the eccentric shaft portion 22
A curved surface portion 22b is formed on the peripheral surface on the side opposite to “a” so as to protrude outward along the axial direction.

On the other hand, the drive bush 25 fitted to the eccentric shaft portion 22 and rotatably mounted on the bearing portion 2a of the orbiting scroll 2 has an eccentric shaft portion on the inner peripheral surface of the hole into which the eccentric shaft portion 22 fits. 22, flat surface portions 25a, 2 formed at positions corresponding to the flat surface portion 22a and the curved surface portion 22b, respectively.
5b. When the orbiting scroll 2 is orbited through the drive bush 25 by the eccentric shaft portion 22 having such a configuration, the curved surface portion 22b corresponds to the drive bush 25 even when the eccentric shaft portion 22 is inclined as shown in FIG. Since the rotation and the movement freely contact the flat surface portion 25b in the axial direction, the drive bush 25 does not tilt together with the inclination of the eccentric shaft portion 22 in the bearing portion 2a of the orbiting scroll 2, The eccentric shaft portion 22 performs the bearing function by rotating while being parallel to the bearing. Therefore, there is no occurrence of one-sided contact or the like in the bearing portion 2a of the orbiting scroll 2, so that a decrease in bearing performance is prevented, and wear and seizure can be prevented. 1, 3, and 4, the vertex of the curved surface portion 22 b is located at an axial position substantially at the center of the bearing portion 2 a of the orbiting scroll 2.

FIG. 5 is a perspective view showing another embodiment of the eccentric shaft formed at the upper end of the crankshaft 21. FIG. The eccentric shaft portion 26 is basically based on a circle having a center point O2 at a position shifted by a predetermined distance from the center O1 of the crankshaft 21 similarly to the eccentric shaft portion 22 shown in FIG. An eccentric pin portion 21a having an outer shape and having a flat surface portion 26a formed on a peripheral surface at a position along a line connecting the two center points O1 and O2 is provided. In the eccentric pin portion 21a, a notch 26 having a U-shape as viewed from above is formed on a peripheral surface opposite to the flat surface portion 26a.
b is formed.

As shown in FIG. 5, a separate joining member 27 having a curved surface 27a at the front and a flat surface 27b at the back is inserted into the notch 26b from above as shown in FIG. The joining member 27 has a shape obtained by cutting off a part of the peripheral surface of the cylindrical body along the longitudinal direction, and the joining member 27 has a notched portion 26b of the eccentric shaft portion 26 and a curved surface 27a having an eccentric shaft portion. 26 is mounted so as to be outwardly convex along the axial direction. Thus, the configuration is substantially the same as the eccentric shaft portion 22 shown in FIG. The drive bush to be fitted to the eccentric shaft portion 26 may be the same as that shown in FIG.

FIG. 6 shows another example of a drive bush attached to an eccentric shaft formed at the upper end of the crankshaft 21. The drive bush 28 includes a hole 28a that basically fits into a base circle of the eccentric shaft portion like the drive bush 25 shown in FIG. 2, and the hole 28a is orthogonal to one radial center line. One of the inner peripheral surfaces is provided with a flat surface portion 28b, and the other is provided with a notch portion 28c. The notch portion 28c has a curved surface portion 27a which is exactly the same as the separate bonding member 27 shown in FIG. It is inserted so that it becomes.

When such a drive bush 28 is used, the eccentric shaft portion to which the drive bush 28 is fitted is different from that shown in FIG. 2, and the outer peripheral surface opposite to the one flat surface portion 22a is not a curved surface. And the same flat surface portion is used. It can be understood from this that in the relationship between the eccentric shaft portion and the drive bush, each peripheral surface (the outer periphery of the eccentric shaft portion) at a position along a line connecting the center point O1 of the crankshaft and the center point O2 of the eccentric shaft portion. Of the two sets of opposing engagement surfaces formed on the surface and the inner peripheral surface of the drive bush, both sets of opposing engagement surfaces are flat surfaces (for example, the flat surfaces 2 as shown in FIG. 2).
2a, 25a), but it is sufficient that one of the other set of the opposing engaging surfaces is the curved surface described above and the other is a flat surface.

As shown in FIGS. 5 and 6, when a separate joining member 27 is prepared and mounted on an eccentric shaft portion or a cutout formed in a drive bush, an eccentric shaft portion of a crankshaft is formed. The difficulty of directly and accurately machining a curved surface portion curved in a direction along the axis on the outer peripheral surface and the difficulty similarly occurring on the inner peripheral surface of the fitting hole of the drive bush are eliminated, and the workability and the machining accuracy can be improved. Not only that, but also the processing cost can be reduced. In a set of opposed engagement surfaces between the eccentric shaft portion and the drive bush, the concept of a curved surface portion provided on one of them is, for example, formed perpendicular to the axial direction as shown in FIG. And those formed by fitting a cylindrical roller 30 into the groove 29.

In the case of the example shown in FIG. 7, the cylindrical roller 30 enables the use of general-purpose parts, and the workability can be remarkably improved, so that the work cost can be reduced. Also, as shown in FIG. 8, one set of opposed engagement surface portions includes one curved surface portion (for example, curved surface portion 22b in the case of the eccentric shaft portion 22) and the other flat surface portion (for example, the flat surface portion 25b in the case of the drive bush 25). If a high-hardness member 31 such as hardened steel is disposed between them, sufficient hardness can be ensured for both contact portions, and at this time, the drive bush is formed of a relatively low-hardness material such as a sintered material. Therefore, there is an advantage that the reliability can be secured while reducing the processing cost.

FIG. 9 shows a bearing structure in which the main shaft portion 23 of the crankshaft 21 is supported by the main bearing portion 6a of the main frame 6 of the scroll compressor 20. The main shaft portion 23 is provided with a bar-shaped portion 32 formed in a barrel shape whose central portion is convex over the entire circumference. A cylindrical bush 33 is fitted on the outer periphery of the belt-shaped portion 32 at a maximum protruding portion at a central portion thereof with a small gap, and the cylindrical bush 33 is provided on a seating surface 21 a formed at a lower portion of the main shaft portion of the crankshaft 21. Seated. 1 and FIG. 9, the belt-like portion 32 formed in a barrel shape in which the central portion, which is the vertex of the curved surface portion, is convex over the entire circumference is located substantially at the axial position at the center of the main bearing portion 6a.

The cylindrical bush 33 is rotatably fitted in the main bearing 6a of the main frame 6,
1 and rotates together. Therefore, a hole is formed along the axial direction on both the lower surface 33a of the cylindrical bush 33 and the seating surface 21a, and the connecting pin 34 is press-fitted into this hole. As a result, the cylindrical bush 33 rotates integrally with the crankshaft 21, but the crankshaft 21
When receiving g, the hole is inclined with respect to the cylindrical bush 33 so that one of the holes into which the connecting pin 34 is press-fitted is a long hole that is long in the radial direction. In the example shown in FIG. 9, the hole formed in the seating surface 21 a is an elongated hole, but the hole formed in the lower surface 33 a of the cylindrical bush 33 may be an elongated hole.

As described above, the cylindrical portion disposed on the main shaft portion 23 of the crankshaft 21 and the main bearing portion 6a of the main frame 6 having the belt-shaped portion 32 formed in a barrel shape whose central portion is convex over the entire circumference. According to the bearing structure including the bush 33, the compressive load Fg and the centrifugal load FC applied to the crankshaft 21 are provided.
The directions of FC1, FC2, and FC3 are almost perpendicular to each other, and the size thereof varies depending on the operating conditions of the compressor. Therefore, the bending direction of the crankshaft 21 also varies. The contact with 33 is the crankshaft 2
1 and can move in accordance with the deflection direction and the magnitude of the deflection, and the cylindrical bush 33 always remains parallel to the main bearing portion 6a of the main frame 6 regardless of the operating conditions of the compressor ( (While maintaining the state where the rotation center axis of the cylindrical bush 33 coincides with the center axis of the main bearing portion 6a)
Rotate.

As a result, it is possible to obtain a highly reliable bearing structure without a decrease in bearing load capacity and without a risk of bearing abrasion and seizure.

When the contact point of the cylindrical bush 33 moves on the curved surface of the belt-shaped portion of the main shaft portion 23 of the crankshaft 21, the seating surface 21a and the lower surface 33a of the cylindrical bush 33 are moved.
The gap can be minimized by selecting the curvature of the curved surface portion of the belt-shaped portion 32, and the oil for lubricating the cylindrical bush 33 flows out of the gap. Can be prevented.

In the above-described bearing structure of the crankshaft main shaft portion 23, the seating surface 21a for the cylindrical bush 33 is formed on the crankshaft 21, but as shown in FIG. Good.
In this case, since the outer diameter of the crankshaft 21 can be made equal to or less than the outer diameter of the main shaft portion over the entire length, the machinability of the crankshaft is improved.

Further, as shown in FIG. 11, the center portion of the main shaft portion 23 of the crankshaft 21 is formed on two surfaces in the reaction force direction of the compression load Fg and the reaction force direction of the centrifugal force loads FC1, FC2, and FC3. Cylindrical bush 3 having convex curved portions 23a and 23b and having flat surfaces 35a and 35b corresponding to the curved portions 23a and 23b with a minute gap around the periphery.
5 is fitted, the cylindrical bush 35 has the compression load Fg of the crankshaft 21 and the centrifugal loads FC1, FC2, and FC3.
Of the main shaft 2 of the crankshaft 21
3 can be moved on the curved surface portions 23a and 23b, and as a result, the main frame 6 can be rotated while being parallel to the main bearing portion 6a, and the same effect as the bearing structure of the above-described example can be obtained. Obtainable. In this example, 2
Since the curved surfaces 23a and 23b also have a circumferential connection function between the crankshaft 21 and the cylindrical bush 35, a connecting pin is not required.

Next, FIG. 12 shows a bearing structure in which the auxiliary bearing portion 9a of the auxiliary frame 9 of the scroll compressor 20 supports the crankshaft 21. This bearing structure is similar to the above-described bearing structure in which the main bearing portion 6a of the main frame 6 supports the main shaft portion 23 of the crankshaft 21. Band 36
And a cylindrical bush 37 fitted around the outer periphery thereof with a small gap. 1 and 12, the barrel-shaped belt-like portion 36 having a convex central portion, which is the vertex of the curved surface portion, is located at an axial position substantially at the center of the sub-bearing portion 9a.

This cylindrical bush 37 is used for the crankshaft 21.
The other end of the connecting pin 38, one end of which is press-fitted and fixed in a hole formed in the radial direction so as to rotate integrally with the shaft, is engaged with an axially long hole 24a formed in the crankshaft 21 to form a circumferential direction. Interconnected. 1 and 12, reference numeral 16 denotes a refueling pump unit, and reference numeral 17 denotes a cover of the refueling pump unit.

According to the bearing structure in which the auxiliary shaft portion 24 of the crankshaft 21 is supported by the auxiliary bearing portion 9a of the auxiliary frame 9, when the crankshaft 21 is bent as shown in FIG. The contact point with the cylindrical bush 37 provided on the outer periphery moves on the surface of the barrel-shaped band-shaped portion formed on the sub shaft portion 24 of the shaft 21 and having a convex central portion,
As a result, the cylindrical bush 37 can rotate in a state parallel to the boss portion of the sub-frame 9, that is, the sub-bearing portion 9 a, and the bearing load capacity does not decrease.
A highly reliable bearing structure without the risk of seizure or the like can be obtained.

The countershaft 24 of the crankshaft 21 described above is used.
In the bearing structure that supports the
In this case, a barrel-shaped band portion 36 having a convex central portion is formed, and a cylindrical bush 37 is fitted on the outer periphery thereof. However, as shown in FIG. May be configured by fitting a cylindrical bush 39 having a barrel-shaped band-shaped portion 39a having a convex shape to the crankshaft 21.

The crankshaft 21 and the cylindrical bush 3
7, a connecting pin 38 press-fitted into a hole of the cylindrical bush 37 is engaged with the elongated hole 24a formed in the crankshaft 21. However, as shown in FIG. An elongated hole may be formed in 39, and a connecting pin 38 press-fitted and fixed to a hole formed in the countershaft portion 24 of the crankshaft 21 may be engaged with the elongated hole.

Further, the countershaft portion 24 of the aforementioned crankshaft 21
In the bearing structure for supporting the auxiliary shaft portion 24 or the cylindrical bush 39, a barrel-shaped belt-shaped portion having a convex central portion is formed on the auxiliary shaft portion 24 or the cylindrical bush 39. The compressive load and centrifugal load acting on the eccentric shaft 22,
The compression load or the centrifugal force load applied to the main shaft portion 23 is smaller than that of the main shaft portion 23. Therefore, as shown in FIG.
May be supported. Such a rolling bearing 40 (FIG. 1)
5 uses a deep groove ball bearing), the scroll compressor has an outer ring rotational load (the load direction is rotating, the inner ring is rotating, and the outer ring is stationary), so there is a clearance between the inner ring 40a and the crankshaft 21. I assume it.

When a load acts on the crankshaft 21 in such a bearing structure that supports the sub shaft portion 24 of the crankshaft 21 with such a rolling bearing 40, the inner race 40a tilts in the load direction as shown in FIG. Attempts to follow the tilt of the shaft 21. The load capacity and reliability of the rolling bearing 40 are not impaired with respect to such inclination of the crankshaft 21, and the bearing load capacity and reliability do not decrease even if the crankshaft 21 is inclined.

In the scroll compressor according to the embodiment of the present invention shown in FIG.
2. A convex structure in which the bearing structure supporting the main shaft portion 23 and the sub shaft portion 24 includes the drive bush 25 or the cylindrical bushes 33 and 37, and the bearing surface of each shaft portion acts as a parallel bearing for each bush. However, if any one of the eccentric shaft portion, the main shaft portion, and the sub shaft portion of the crankshaft 21 is supported by the above-described bearing structure, the shaft load capacity of the shaft portion is reduced. Needless to say, this can be prevented.

[0040]

As described above, according to the first aspect of the present invention,
Scroll compressor is rotatable with an eccentric shaft at the end
A simple crankshaft, fixed scroll and fluid compression
A turning scroll cooperating with the fixed scroll for the
In order to revolve the turning scroll, the turning scroll
A first shaft rotatably connecting the roll to the eccentric shaft;
Receiving means, wherein the first bearing means comprises
Drive bush rotatably fitted to the roll bearing
And the clamp between the drive bush and the eccentric shaft portion.
Curved surface and plane curved only along the axis of the rank axis
And an opposing engagement surface portion in combination with the portion.
The axis of the crankshaft between the drive bush and the eccentric shaft
For combination of curved surface and flat surface only curved along the direction
With the opposing engaging surface portion of the crankshaft
Drive bushing parallel to bearings for surrounding inclines
Condition can be maintained and bearing wear, damage and
A scroll compressor without fear of sticking is obtained.
In the opposing engaging surface portion, the flat surface portion and the crankshaft shaft
By line contact with curved surface part which curved only along the line direction,
When the eccentric shaft and the drive bush rotate integrally,
To prevent wear on the curved surface, and highly reliable one-side prevention
A scroll compressor having means is obtained.

[0041]

The scroll compression according to the second invention.
The machine has a rotatable crankshaft with an eccentric shaft at the end,
A fixed scroll and said fixed scroll for compressing the fluid.
A turning scroll cooperating with a roll, and the turning scroll
The orbiting scroll is eccentric in order to revolve
First bearing means rotatably coupled to the shaft,
The first bearing means is provided on a bearing portion of the orbiting scroll.
A drive bush rotatably fitted to the drive bush;
Axis direction of the crankshaft between the shaft and the eccentric shaft portion
Engaging surface part by combination of curved surface part and flat part along
And a curved surface portion of the eccentric shaft portion and the drive bush.
Or the flat portion of the eccentric shaft portion and the drive block.
Since the high-hardness member is disposed between the curved surface and the curved surface , sufficient hardness can be ensured at the contact portion with the curved surface, so that the driving bush or the eccentric shaft portion is engaged with the curved surface. The side having the portion can be formed of a material having a relatively low hardness, and the workability can be improved. Further, in the case where the curved surface portion is formed on the eccentric shaft portion, the drive bush can be formed of a sintered material having low hardness, and there is an advantage that the reliability can be secured while reducing the processing cost.

The scroll compression according to the third invention.
The machine includes a closed container, a fixed scroll, a swivel scroll for compressing a fluid in cooperation with the fixed scroll, a stator of a motor fitted and fixed to the closed container, and the motor. On both sides of the main frame and the sub-frame, which are fitted and fixed in the closed container, and a turning force is applied to the turning scroll, and the bearing portions of the main frame and the sub-frame are provided. A crankshaft having a main shaft portion and a countershaft portion supported in a radial direction, a rotor of an electric motor fitted and fixed to the crankshaft, a balance weight rotating integrally with the crankshaft, and a lower end of the crankshaft; An oil supply pump disposed on the side of the crankshaft for transporting lubricating oil, an eccentric shaft formed at the upper end of the crankshaft, and the eccentric shaft for revolving the orbiting scroll. First bearing rotatably coupled to a shaft A stepped portion, wherein the first bearing means is rotatable on a curved surface portion formed on a part of an outer peripheral surface of the eccentric shaft portion along an axial direction of the crankshaft and a bearing portion of the swivel scroll; And the drive bush having a flat portion at a position corresponding to the curved surface portion of the eccentric shaft portion.
The eccentric shaft is free to rotate and move in the axial direction of the crankshaft with respect to the drive bush via the contact portion between the curved surface of the eccentric shaft and the flat portion of the drive bush. In this case, the drive bush does not tilt with the eccentric shaft part, can maintain the parallel state with the bearing part of the turning scroll, and can ensure ideal fluid lubrication without lowering the bearing load capacity. Further, it is possible to obtain a highly reliable scroll compressor which is free from abrasion, damage, seizure and the like of the bearing due to one side contact.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing a scroll compressor according to an embodiment of the present invention.

FIG. 2 is a top view showing a drive bush fitted to an eccentric shaft portion at an upper end of a crankshaft in the scroll compressor shown in FIG.

3 is a cross-sectional view taken along the line III-III of FIG. 2 in a state where the embodiment of FIG. 2 in which the drive bush is fitted to the eccentric shaft portion is mounted on a bearing portion of the orbiting scroll.

FIG. 4 is a cross-sectional view showing a state in which the crankshaft is tilted in the bearing structure of the eccentric shaft portion of the crankshaft according to the embodiment of the present invention shown in FIG.

FIG. 5 is a perspective view showing another configuration example of the bearing structure of the eccentric shaft portion of the crankshaft.

FIG. 6 is a perspective view showing still another configuration example of a bearing structure of a crankshaft eccentric shaft portion.

FIG. 7 is a cross-sectional view showing still another configuration example in the bearing structure of the crankshaft eccentric shaft portion.

FIG. 8 is a sectional view showing still another bearing structure of a crankshaft eccentric shaft part.

FIG. 9 is a sectional view showing a bearing structure for supporting a main shaft portion of a crankshaft in the scroll compressor according to one embodiment of the present invention.

FIG. 10 is a cross-sectional view showing another configuration example of the bearing structure of the crankshaft main shaft portion.

FIG. 11 is an exploded perspective view showing still another configuration example of the bearing structure of the crankshaft main shaft portion.

FIG. 12 is a cross-sectional view showing a bearing structure for supporting a countershaft portion of a crankshaft in the scroll compressor according to one embodiment of the present invention.

13 is a sectional view schematically showing a state in which the crankshaft is tilted in the bearing structure of the crankshaft countershaft shown in FIG.

FIG. 14 is a cross-sectional view showing another configuration example of the bearing structure of the crankshaft countershaft.

FIG. 15 is a cross-sectional view showing still another configuration example of the bearing structure of the crankshaft countershaft.

16 is a cross-sectional view schematically showing a state in which the crankshaft is tilted in the bearing structure of the crankshaft countershaft shown in FIG.

FIG. 17 is a longitudinal sectional view showing a conventional scroll compressor.

FIG. 18 is an explanatory diagram showing directions of a compression load acting on a crankshaft and a centrifugal force of a balance weight in a scroll compressor.

FIG. 19 is an explanatory diagram schematically showing a state of inclination of a crankshaft in a scroll compressor.

[Explanation of symbols]

1 fixed scroll, 2 orbiting scroll, 2a
Bearing part, 20 scroll compressor, 21 crankshaft, 22 eccentric shaft part, 22a flat part, 22b curved surface part, 25 drive bush, 31 high hardness member.

──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Hiroshi Ogawa 3-181-1, Oka, Shizuoka-shi, Shizuoka Mitsubishi Electric Corporation Shizuoka Works (72) Inventor Norihide Kobayashi 3-181, Oka, Shizuoka-shi, Shizuoka No. Mitsubishi Electric Corporation Shizuoka Works (72) Inventor Yoshinori Shirato 3-18-1 Oka, Shizuoka City, Shizuoka Prefecture Mitsubishi Electric Corporation Shizuoka Works (72) Inventor Takashi Yamamoto 3-18, Oka, Shizuoka City, Shizuoka Prefecture No. 1 Inside Shizuoka Works, Mitsubishi Electric Corporation (72) Inventor Keiki Sakai 3-18-1, Oka, Shizuoka-shi, Shizuoka Prefecture Inside Shizuoka Works, Mitsubishi Electric Corporation (56) References JP-A-60-80088 (JP, A Japanese Utility Model Application Sho 62-143002 (JP, U) Patent 2734408 (JP, B2) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04C 18/02 311

Claims (3)

(57) [Claims] A rotatable crankshaft having an eccentric shaft at an end; a fixed scroll; a swivel scroll cooperating with the fixed scroll to compress a fluid; First bearing means for rotatably connecting the turning scroll to the eccentric shaft for revolving the turning scroll, wherein the first bearing means comprises a bearing for the turning scroll. the Clan a drive bush rotatably fitted, said driving bush between the eccentric shaft portion
A scroll compressor comprising: a facing portion formed by a combination of a curved portion curved only along the axis of a shaft and a flat portion. 2. A rotatable clamp having an eccentric shaft at its end.
Shaft, a stationary scroll , and a swivel cooperating with the stationary scroll to compress the fluid.
A turning scroll and the turning scroll for revolving the turning scroll.
A first shaft rotatably connecting the roll to the eccentric shaft;
Receiving means, wherein the first bearing means is provided on a bearing portion of the orbiting scroll.
A drive bush rotatably fitted, and the clamp between the drive bush and the eccentric shaft portion.
The combination of the curved surface and the flat surface along the axis of the
Has a face engaging surface portion that, the planar portion of the curved portion and the drive bush of the eccentric shaft portion, or
Or the flat part of the eccentric shaft part and the curved part of the drive bush
Characterized by a high hardness member disposed between
-Compressor . 3. A closed container, a fixed scroll, and a swivel scroll for compressing a fluid in cooperation with the fixed scroll.
A roll, a stator of the motor fitted and fixed to the closed container, and a main body fixed to the closed container on both sides of the motor.
A rotational force is applied to the turning frame, the sub-frame and the sub-frame, and the main frame is rotated.
And the main frame supported in the radial direction by the bearings of the sub-frame and
A crankshaft having a shaft portion and a countershaft portion; a rotor of an electric motor fitted and fixed to the crankshaft; a balance weight rotating integrally with the crankshaft; and a lower end side of the crankshaft. Convey lubricating oil
A refueling pump, an eccentric shaft formed at the upper end of the crankshaft , and the revolving scroll for revolving the revolving scroll.
First bearing for rotatably coupling a roll to the eccentric shaft
Means, wherein the first bearing means is provided on a part of the outer peripheral surface of the eccentric shaft part.
The formed curved surface portion along the axial direction of the crankshaft is rotatably fitted to a bearing portion of the turning scroll.
The inner peripheral surface is fitted with the eccentric shaft, and the eccentric shaft is bent.
For example, a drive bush with a flat part at a position corresponding to the surface
And a scroll compressor .