JPS623186A - Scroll compressor - Google Patents

Abstract

PURPOSE:To increase the load capacity of a bearing part by setting a gap between the bearing part at the edge part of a bearing part and a frame in order to increase the load capacity of the bearing part which is generated because of the one-side contact, thus tilting the bearing part together with a crankshaft. CONSTITUTION:The second balance weight 26 is engaged and integrally formed with a crankshaft 10, and a centrifugal force is generated on the second balance weight 26 by revolving the crankshaft 10, and each force applied onto an eccentric shaft 10' and the crankshaft 10 is reduced by the pressure in a compression chamber 3. In this case, together with the crankshaft 10 and the eccentric shaft 10' which are inclined because of the fact that the force is not perfectly offset, a bearing part 9 is inclined by the gap 30 generated between a frame 7, and the load capacity of the bearing part 9 is increased, and the load applied onto the bearing part 9 because of the one-sided contact due to the inclination of the crankshaft is reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a scroll compressor used as a refrigerant compressor for refrigeration and air conditioning, or as a compressor for air or other gases.

Conventional technology Taking a vertical oil-fed scroll compressor for refrigeration and air conditioning as an example,
The basic configuration will be explained with reference to FIGS. 4 and 6.

First, the operating principle of the scroll compressor will be explained with reference to FIGS. 4 and 6. When the orbiting scroll 1 is rotated clockwise between the spiral orbiting scroll 1 and the fixed scroll 2, the wrap 1a of the orbiting scroll 1 and the end plate 1
Of the compression chambers 31L and 3°b formed by the wrap 2a and end plate 2b of the fixed scroll 2, the refrigerant gas sucked from the suction port 4 is hermetically sealed into the compression chamber located on the outermost side. Further, the volume of the compression chambers 32L and 3b gradually decreases as the orbiting scroll 1 rotates, and the pressure of the refrigerant gas is increased and the refrigerant gas is discharged from the central discharge port 5.

Next, we will discuss the basic configuration of a conventional scroll compressor in the fourth section.
This will be explained with reference to FIG. A fixed scroll 2 having a spiral wrap 2a standing upright on an end plate 2b and an orbiting scroll 1 having substantially the same shape as this fixed scroll 2 and consisting of a wrap 1a and an end plate 1b are mutually wrapped 1&, 21L.
A rotation prevention mechanism called an Oldham ring is provided between the frame 7 fastened to the fixed scroll 2 and the orbiting scrolls 1 and 9. A rotor 11aL of an electric motor 11 is connected to a crankshaft 1o that is rotatably supported by a bearing 9 of a frame 7.
The crankshaft 1o is rotationally driven by the stator 11b held in the frame 7 or the closed container 12. The orbiting scroll 1 rotates around the center axis of the bearing section 9 of the seven frames 7 with its end plate 1b sandwiched between the mirror plate section 2C of the fixed scroll 2 and the pedestal 13 of the frame 7.

The crankshaft 10 has an eccentric shaft 10' having an eccentric amount ε, and this eccentric amount ε becomes the turning radius of the orbiting scroll 1.

Further, an orbiting scroll 1 is attached to an eccentric shaft 1 on the crankshaft 1o.
The first balance weight 14 is used to offset the centrifugal force generated by the pressure inside the compression chamber, and the second balance weight is used to reduce the force generated on the crankshaft due to the pressure inside the compression chamber.
A balance weight 26 is engaged and formed integrally.

Next, the operation of the compressor will be explained with reference to FIG. 6 according to the flow of refrigerant gas and lubricating oil.

Low-pressure refrigerant gas is led from the suction pipe 15 to the fixed sp O-
#2 OVAo"'>L51.X, I C1! -/
L-2/'''□1.; reaches the compression chamber 3 formed by the orbiting scroll 1. The refrigerant gas that has entered the compression chamber 3 is gradually compressed by the orbiting movement of the orbiting scroll 1, as described in the operating principle. As it moves to the center of the scroll, the pressure is increased, and the airtight container 12 is discharged from the central discharge port 5.
discharged inside. The discharged high-pressure refrigerant gas enters the closed container 1 through the upper space 16 and the passage 17 in the closed container 12.
It fills the lower space of 2 and is guided to the outside from the discharge pipe 19.

Next, the flow of the lubricating oil 2o will be explained with reference to FIG. The lubricating oil 20 is stored in the lower part of the closed container 12, and the lower end of the crankshaft 10 immersed in the lubricating oil 2o is in an atmosphere of high discharge pressure.

A vertical hole 21 for supplying oil to each bearing portion is formed in the crankshaft 1Q from the lower end to the upper end surface. The orbiting scroll 1 is mounted around the orbiting bearing 22 of the orbiting scroll 1.
In order to maintain the thrust force exerted by the refrigerant gas pressure during compression, a pressure-separated back pressure chamber 23 is provided. The lubricating oil 20' becomes an intermediate pressure atmosphere due to the low pressure gas leaking from the gaps between the end plate 1b of the orbiting scroll 1, the end plate 2C of the fixed scroll 2, and the pedestal 13 of the frame 7. Therefore, the lubricating oil 20 in the high pressure atmosphere accumulated in the lower part of the closed container 12 is transferred to the crankshaft 1 due to the differential pressure.
0 vertical hole 21, and oil is supplied to sliding parts such as bearings. The lubricating oil leaking into the compression chamber 3 is compressed together with the refrigerant gas, moves to the lower part of the closed container 12 through the discharge port 5 and the passage 17, and then rapidly increases the flow velocity and falls to the bottom of the container under its own weight. That is, the lubricating oil 20.20' is used for oil supply, and the lubricating oil 20.
Eccentric shaft 1o', first balance weight 14, second
11, balance weight 26. 7th
The figure is a plan view of Figure 6 viewed from the arrow 1, crankshaft 1.
The centrifugal force F1 generated because the center 3o of the eccentric shaft 10' fitted to the orbiting scroll is eccentric with respect to the rotation center 31 of the balance weight 14 is applied to the rotation center 31 of the balance weight 14. .

The centrifugal force F2 completely cancels it out, but the centrifugal force F4 of the second balance weight 26 reduces the force F3 caused by the pressure generated when the compression chamber moves from the outside to the center while decreasing its volume. However, since the rotation speed changes and it is not completely offset, the crankshaft 10
is tilted, and one piece of contact occurs in the bearing portion 9.

In view of the above-mentioned problems, the present invention provides a scroll compressor that eliminates the problem of uneven support in the bearing section.

Means for Solving the Problems In order to solve the above problems, the present invention provides a gap between the bearing part and the frame at the end of the bearing part in order to increase the load capacity of the bearing part that causes uneven contact. It has been established.

Effect of the Invention With the above-described configuration, when the crankshaft 10 is tilted and a partial contact occurs on the bearing part, the bearing part is tilted together with the crankshaft 10 due to the gap provided between the bearing part and the frame, and the load is reduced. Capacity can be increased.

Example A first embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 is a detailed view of the bearing section, showing a state in which the crankshaft 1Q is tilted. Figure 2 is an overall configuration diagram, and the crankshaft 1o
By holding and integrating the second balance weight 26 and rotating the crankshaft 1o, a centrifugal force is generated in the second balance weight 26, and the pressure inside the compression chamber 3 causes the eccentric shaft 10' and the crankshaft to rotate. Although the force applied to 1o is reduced to a light range, the crankshaft 10 and the eccentric shaft 10' are tilted because they are not completely offset, and the bearing part 9 is tilted by the gap 30 provided between the bearing part 9 and the frame a.
The load capacity of the bearing part 9 is increased, and the load on the bearing part 9 caused by uneven contact due to the inclination of the crankshaft is reduced to a light range.

Next, a second embodiment of the present invention will be explained with reference to FIGS. 3a and 3b. Figure 3 & is the overall configuration diagram, Figure 3 Figure 3 is a detailed view of the entrance of Figure 3 B, 7a is a frame, 7b is an auxiliary frame, and the gap 30 can be changed by replacing the auxiliary frame 7b. , the maximum amount of tilt of the bearing portion 9 when the crankshaft 10 is tilted is changed.

Effects of the Invention As described above, the present invention provides a gap between the bearing part at the end of the bearing part and the frame, so that when the crankshaft is tilted, the bearing part is also tilted, and its load capacity is reduced. can be increased.

[Brief explanation of drawings]

Fig. 1 is a detailed view of the bearing section when the crankshaft is tilted in the first embodiment of the present invention, Fig. 2 is an overall configuration diagram of the scroll compressor in the first embodiment of the present invention, and Fig. 3 a
3 is a detailed view of section A in FIG. 3a, and FIG. 4 is a cross section showing the meshing state of the orbiting scroll and fixed scroll. Figure 6 is a vertical cross-sectional view of a conventional hermetic scroll compressor, Figure 6 is a perspective view of the crankshaft in which the first and second balance weights are engaged and integrated, and Figure 7 is Figure 6. FIG. 1...Orbiting scroll, 2...Fixed scroll, 3...Compression chamber, 10...Crankshaft, 10'...Eccentric shaft , 14.26...
...Balance weight, 7゜enda...Frame, 7b...Auxiliary frame. Name of agent: Patent attorney Toshio Nakao and 1 other person7-
--Fushim needle-Man envy times Suftonoshi 2-1 1 top t... 3-1, pressure control room I 0'--Detection+a@ +4.26--No (Lanthwaite #I 3 Figure 5

Claims (1)

[Claims] a crankshaft; an orbiting scroll eccentrically fixed to the crankshaft and formed by vertically forming a spiral wrap on an end plate;
A fixed scroll having substantially the same shape as the orbiting scroll, and the orbiting scroll and the fixed scroll are engaged with each other with their laps inside, and the orbiting scroll is rotated so that it does not apparently rotate, and the orbiting scroll and the fixed scroll are rotated by the orbiting scroll and the fixed scroll. a compression chamber formed; a first balance weight that offsets the centrifugal force generated because the orbiting scroll is eccentric with respect to the crankshaft; and the orbiting scroll and the crankshaft due to the pressure generated in the compression chamber. a second balance weight that is a balancing component for reducing the force applied to the crankshaft, and a bearing section for supporting the load applied to the crankshaft;
a frame provided on the outer periphery of the bearing portion, and configured to compress the fluid by reducing the volume of the compression chamber while moving the compression chamber from the outside to the center;
A scroll compressor characterized in that a clearance is provided between the bearing portion and the housing.