JPS6343423Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention involves eccentrically engaging the spiral portion of the fixed scroll member and the spiral portion of the movable scroll member, and causing the spiral portion of the movable scroll member to revolve to form a structure between the two spiral portions. The present invention relates to a joint structure for scroll members in a scroll compressor in which compressed fluid is discharged from the center by moving a closed compression chamber toward the center while reducing the volume.

Conventionally, the end faces of the spiral portions of the movable and fixed scroll members were formed flat when the compressor was at room temperature, and the substrates of the scroll members that slidably contacted both end faces were also formed flat, so that no swirl occurred during steady operation. The center of the spiral part, which forms the compression chamber at the end of the compression stroke, has the highest pressure and temperature than the amount of thermal expansion of the spiral part, which forms the compression chamber in the outer part of the spiral part, that is, the compression chamber at the beginning of the compression stroke, where the pressure and temperature are low. The amount of thermal expansion of the spiral portion is larger, and therefore the surface pressure and sliding resistance against the substrate are greater toward the center of the spiral portion, and the center of the spiral portion receives greater gas pressure, resulting in the following: A problem arose.

That is, as shown in FIGS. 11 to 13, for example, at the central end of the end surface 9e of the spiral portion 9c of the movable scroll member 9 (the dotted portion), there is a surface pressure and sliding resistance against the base plate 15a of the fixed scroll. is maximum, and since the central side wall surface of the end surface 9e is steep, stress concentration is likely to occur at the corner R, and the surface that opposes the force F due to sliding resistance at the central end of the end surface 9e is the 16th The virtual cross section n7 shown in the figure by a chain line and the root n6, and the virtual cross section n7
The drag force is transmitted to the root n8 other than the root n6, and as a result, it is received at the root n6 and n8 portions, but the area of these n6 and n8 portions is small, so the stress concentration at the corner R is large and the spiral Part 9
There was a problem that c was easily damaged from the root.

The present invention has been made to solve the above problem, and its purpose is to lower the center side end surface of the spiral portion of the scroll member than the other end surfaces so that there is a gap between the center side end surface and the substrate. By forming
It is an object of the present invention to provide a joining structure for a scroll member in a scroll compressor, which can prevent breakage of a spiral portion, prevent seizure, and reduce frictional power.

Below, an example embodying the present invention is shown in Figs.
To explain FIG. 6, the center housing 1
A front housing 2 is fixed to the left end of the center housing 1 by a plurality of tightening bolts (not shown), and a rear housing 3 is integrally provided to the right end of the center housing 1 .

A cylindrical boss portion 4 is integrally formed in the center of the front housing 2, and a rotating shaft 6 is supported in the center hole 4a by a pair of left and right radial ball bearings 5, and is connected to a drive source at the outer end. Ru. Further, a shaft seal mechanism 7 is interposed between the rotating shaft 6 and the boss portion 4, and a shaft seal mechanism 7 is provided at the upper base end of the boss portion 4 so as to communicate with the upper portion of the seal chamber S that houses the seal mechanism 7. is refrigerant gas introduction hole 4
b is provided.

An eccentric shaft 8 is connected to the inner end of the rotating shaft 6, and a boss integrally formed at the center of the back surface of a circular base plate 9a constituting the movable scroll member 9 is mounted on the eccentric shaft 8. The portion 9b is rotatably supported via a radial needle bearing 10 or a plain bearing. A spiral portion 9c is integrally formed on the front surface of the movable scroll member 9, as shown in FIG.

On the other hand, the outer circumferential edge of a fixing ring 11 that prevents rotation of the movable scroll member 9 is non-rotatably engaged with an annular locking step formed at the joint between the center housing 1 and the front housing 2 by a key 12. ing. A suction chamber A is formed on the front housing 2 side with this fixing ring 11 as a boundary, and an operating chamber B is formed on the center housing 1 side. Refrigerant gas is introduced from an external circuit through the suction port 2a. Further, as shown in FIG. 2, a plurality of suction passages 11a (four in this embodiment, but many small holes may be provided) are provided on the outer side of the fixing ring 11, and the suction passages 11a are actuated from the suction chamber A. Refrigerant gas is introduced into chamber B.

On the back surface of the base plate 9a of the movable scroll member 9, a guide groove 9d for preventing rotation is cut in the vertical direction passing through the center as shown in FIGS. 1 and 2, and on the front surface of the fixed ring 11, as shown in FIG. As shown, guide grooves 11b for preventing rotation are carved in the left-right direction. As shown in FIG. 3, a rotation prevention ring 13 having a rectangular ring shape is engaged with the guide groove 9d so as to be slidable in the vertical direction.
The anti-rotation ring 13 is also engaged with the rotation prevention ring 13 so as to be slidable in the left and right direction, as shown in FIG.

Therefore, when the eccentric shaft 8 is rotated, for example, 90 degrees counterclockwise in FIG. Since the anti-rotation ring 13 is regulated by the guide groove 11b, the anti-rotation ring 13 is moved straight in parallel to the left along the guide groove 11b, and therefore the guide groove 9d of the base plate 9a is also held in the same vertical direction, and the movable scroll member 9
rotation is prevented.

A balance weight 14 is fixed to the inner end of the rotating shaft 6 for smoothing the revolution of the movable scroll member 9.

At the locking step formed by the center housing 1 and the rear housing 3, there is a thick circular base plate 15a constituting the fixed scroll member 15.
The outer periphery of the tube is clamped so that it cannot rotate and cannot move in the radial direction. On the front surface of this board 15a, there is a fourth
As shown in the figure, the spiral portion 15b is integrally fixed to the spiral portion 9c of the movable scroll member so as to be in local contact with the spiral portion 9c at two or more locations at all times.
Further, the substrate 15a is located approximately at the center of the substrate 15a.
a discharge passage 1 capable of discharging compressed refrigerant gas to a discharge chamber D formed by a and a rear housing 3;
5c is provided transparently. This discharge passage 15c is closed within the discharge chamber D by a discharge valve 17 whose position is regulated by a retainer 16. A discharge port 3a is transparently provided at the bottom of the discharge chamber D.

Therefore, when the spiral portion 9c of the movable scroll member 9 revolves clockwise in FIG. 4 while locally contacting the spiral portion 15b of the fixed scroll member 15 by the eccentric shaft 8, both spiral portions 9c,1
The contact part 5b moves toward the center on the inner peripheral surface of the spiral part 15b, so that the closed compression chamber C formed by the two contact parts gradually compresses the taken in refrigerant gas. while moving to the center, and is discharged from the discharge passage 15c to the discharge chamber D, and is discharged from the discharge port 3a.
from there to the external circuit.

Next, the main parts of the present invention will be explained with reference to FIGS. 5 to 9.

As shown in FIGS. 5 to 7, the fixed side substrate 15a of the spiral portion 9c constituting the movable scroll member 9
A slanted chamfer h is formed at the inner end of the end surface 9e (the center side of the spiral portion 9c) that makes sliding contact with the substrate 15a so that the gap G from the substrate 15a increases toward the tip. As shown in FIG. 8, the substrate 1 is also located at the outer end of the end surface 9e of the spiral portion 9c toward the tip.
Slanted chamfered portion to increase gap G from 5a
h′ is formed.

On the other hand, as shown in FIG.
The inner end of the end surface 15d that comes into sliding contact with the discharge passage 15c
Similar to the chamfered portion h described above, a slanted chamfered portion h'' is formed on the end surface 15d so that the gap G with respect to the substrate 9a increases toward the tip. A slanted chamfer h (not shown) is also formed at the outer end, similar to the chamfer h' described above, so that the gap G with respect to the substrate 9a increases toward the tip.

As shown in FIG. 7, it is desirable that the shape length L of the chamfered portion h be approximately 3 to 10 mm, and that the maximum gap G be 20 to 100 .mu.m.

Next, the operation of the scroll compressor constructed as described above will be explained.

Now, in FIG. 1, when the driving force of the engine is transmitted to the rotating shaft 6 through the connection operation of the electromagnetic clutch (not shown) and compression operation is started, the refrigerant gas sent into the suction chamber A is sucked. It is sucked into the working chamber B through the passage 11a. The refrigerant gas sucked into the working chamber B is taken into the compression chamber C in the suction stroke by the revolving action of the movable scroll member 9, and is moved to the discharge passage 15C while being compressed. sent to the outside.

During the orbital movement of the movable scroll member 9,
The end surface 9e of the spiral portion 9c and the fixed side substrate 15a
End face 15d of sliding or stationary spiral portion 15b
This is because even though the scroll members 9 and 15 are designed to have the same dimensions in the drawings, they have tolerances and the height of the spiral portion of either one of the scroll members 9 and 15 is the same. This is because the temperature becomes higher.

By the way, the height of the spiral portion 9c is the height of the spiral portion 15.
Analyzing the effect of force in a state where the end surface 9e of the spiral portion 9c is in sliding contact with the substrate 15a as shown in FIG. The end face 9e where the chamfered portion h ends is subjected to only a bending action, and is subjected to both a bending action due to gas pressure and a bending action due to sliding resistance. As shown in FIG. 6, if the force due to sliding resistance in the small region n of the end face 9e, which has a constant length and has a rectangular shape from the end of the chamfered part h, is F, then the surface facing this force F is There is a root n1 of the same area directly under the small region n, a virtual cross section n2 shown by a chain line on the side of the chamfer h, and a virtual cross section n3 opposite to the virtual cross section n2. Then, the drag force due to both virtual cross sections n2 and n3 is transmitted to the root n4, which has a wide area including the root n1, and as a result, the drag force is applied to a wider area than the conventional root n8 shown in FIG. Damage at the root n4 of the spiral portion 9c can be prevented.

Also, the root n5 of the chamfered portion h is caused by gas pressure and the root n1
Only a portion of the frictional force generated on the surface closer to the outside acts, and even if there is stress concentration at the corner R, it is smaller than before, and damage at the corner R can be prevented. can.

Furthermore, since the chamfered portion h forms a wedge-shaped space between it and the substrate 15a, lubricating oil easily enters the end surface 15e that slides on the substrate 15a, and it is expected that an oil film pressure will be generated. Power can be reduced.

Note that the chamfer h' shown in FIG. 8 also has the same effect as the chamfer h side described above. Further, as shown in FIG. 9, the discharge passage 15c is connected to the spiral portion 15.
If it is provided by wrapping around the root n5 corresponding to the chamfer h'' of b, the strength of the root n5 will be weakened, but this can be sufficiently withstood since the force acting on the chamfer h'' is weak.

It should be noted that the present invention is not limited to the above-mentioned embodiments, but can be modified and embodied as shown below, for example.

That is, in the embodiment described above, in order to make the central end surface of the spiral portion 9c lower than the other end surfaces, the chamfered portion h is
However, instead of this chamfered portion h, a stepped portion i as shown in FIG. 10 may be used. Note that the length L and gap G of this stepped portion i are preferably the same dimensions as those of the chamfered portion h.

As described in detail above, the present invention provides a structure in which the central end surface of at least one of the spiral portions of the movable and fixed scroll members is lower than the other end surface, so that the center side end surface of at least one of the spiral portions of the movable and fixed scroll members is lower than the other end surface. By providing a gap between the spiral portion and the end surface, it is possible to prevent breakage of the spiral portion, prevent seizure, and reduce frictional force.

[Brief explanation of the drawing]

Fig. 1 is a vertical cross-sectional view of the central part of a scroll compressor according to the present invention, Fig. 2 is a cross-sectional view taken along the line X-X of Fig. 1, Fig. 3 is a perspective view of the anti-rotation ring, and Fig. 4 is a cross-sectional view of the scroll compressor according to the present invention. 1 is a cross-sectional view taken along the Y-Y line in Figure 1, Figure 5 is a perspective view of the movable scroll member, Figure 6 is a perspective view showing a chamfered portion formed in the spiral portion, and Figure 7 is a cross-sectional view showing the chamfered portion as well. 8 and 9 are respectively perspective views showing the chamfered portion, and FIG. 10 shows another example of the present invention, in which the central end face of the spiral portion is cut in the longitudinal direction along the spiral portion. FIG. 11 is a perspective view showing a conventional movable scroll member, FIG. 12 is a partially enlarged perspective view of a spiral portion of the conventional movable scroll member, and FIG. 13 is a portion of a conventional spiral portion. It is an enlarged sectional view. Center housing...1, Front housing...2, Rear housing...3, Rotating shaft...6,
Eccentric shaft...7, Movable scroll member...9, Substrate...9a, Spiral portion...9c, End face...9e, Fixed ring...11, Anti-rotation ring...13, Fixed scroll member...15, Substrate...15a, spiral part...15b, end face...15d, chamfered part...
h, h', h'', step part...i, reinforcement part...j.

Claims (1)

[Claims for Utility Model Registration] 1. A rotary shaft is positively rotatably penetratingly supported at approximately the center of the front end surface of the housing, and a movable scroll member is rotatable relative to an eccentric shaft fixed to the inner end of the rotary shaft. A rotation prevention mechanism for the movable scroll member is provided on the inner surface of the housing, and a fixed scroll member is disposed on the rear side of the housing, and the spiral portion of the fixed scroll member is connected to the spiral portion of the movable scroll member. The movable scroll member is overlapped in a state of partial contact at at least two points, and the movable scroll member is caused to revolve on a constant circular trajectory to move the airtight compression chamber formed between both spiral portions toward the center while increasing the volume. causing a unidirectional continuous compression action by causing a reduction in
In a scroll compressor configured to discharge to the outside from a discharge passage provided through a base plate of a fixed scroll member, the central end surface of at least one of the spiral portions of the movable and fixed scroll members is connected to the other end surface. 1. A joining structure for a scroll member in a scroll compressor, characterized in that a gap is provided between a substrate of a mating scroll member and a central end surface, the gap being lower than the end surface. 2. Practical use characterized in that a chamfered portion or a stepped portion is formed on the center side end face of the spiral portion of the movable and fixed scroll members to form a gap between the center side end face and the substrate of the mating scroll member. A joining structure for scroll members in a scroll compressor as claimed in claim 1.