JPH0450489A - Scroll compressor - Google Patents

Abstract

PURPOSE:To simplify processing by setting the length between a flat surface of a main shaft end part for guiding a slider and a main shaft axis and the length between a flat surface of a shaft bearing engagement hole of the slider to be engaged with the flat surface and a slider axis to be proper, and determining an angle. CONSTITUTION:A length A between a flat surface of a main shaft end part for guiding a slider 16 and a main shaft axis and a length B between a flat surface of a shaft bearing engagement hole 26 of the spider 16 to be engaged with the flat surface and a slider axis are set properly. An angle a formed by the length of this shaft bearing engagement hole 26 and the maximum eccentricity line of a rotary scroll is thus secured at sin<-1> (¦B-A¦/r), where (r) refers to an eccentricity quantity of the slider 16 from the axis of a main shaft 14.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a scroll compressor used in an air conditioner, a refrigerator, etc., and particularly relates to an improvement in a slider mechanism.

[Conventional technology]

FIG. 6 is a vertical cross-sectional view of a conventional scroll compressor that performs radial sealing between a fixed scroll and an oscillating scroll disclosed in, for example, Japanese Patent Application Laid-Open No. 59-120794.
In Figure 7, which is a cross-sectional view showing the main part,
1 is a fixed scroll having a spiral wrap 1a, 2 is an oscillating scroll having a vortex wrap 2a, 3 is a base plate of the oscillating scroll 2, 4 is an oscillating scroll shaft protruding from the center of the back of the base plate 3, 1o is an oscillating scroll having a spiral wrap 1a; A bearing support 11 is fixed to the fixed scroll l with bolts or the like, a ring-shaped Oldham joint 11 is used to prevent the oscillating scroll 2 from rotating and to connect it to the bearing support 10 so that it can swing in the radial direction, and 14 is a bearing. The main shaft 26 supported by the support 10 and driving the oscillating scroll 2 is an elongated bearing fitting hole formed on the upper end surface of the main shaft I4 and located eccentrically from the axis of the main shaft 14. This is a slider disposed within the bearing fitting hole 26 and fitted in a longitudinally slidable but non-rotatable manner.

In the figure, r is the eccentricity of the slider 16 from the axis of the main shaft 14, Fc is the centrifugal force generated during the swinging operation of the swinging scroll 2, Fg is the gas load in a direction almost perpendicular to the centrifugal force, and F
gr is the gas load generated in the opposite direction to the centrifugal force Fc, F
is the resultant force of centrifugal force Fc and gas loads Fg and Fgr, C is the radial gap between fixed scroll 1 and oscillating scroll 2, α
is the angle between the longitudinal direction of the bearing fitting hole 26 and the eccentric direction of the slider 16, and θ is the angle between the resultant force F of the centrifugal force Fc and the gas load Fg and the eccentric direction. Note that the angle α is

θ is positive on the opposite rotation side of the main shaft from the eccentric direction.

Now, as shown in Fig. 7, in the conventional technology, the bearing fitting hole 2
Angle α between the longitudinal direction of the slider 6 and the eccentric direction of the slider 16
In order to determine the sliding direction of the slider 16, the bearing fitting hole 26 is provided so that the longitudinal direction thereof and the eccentric direction form an angle ``with respect to a position separated by an eccentric amount r from the axis of the main shaft 14''. A scroll compressor in which the direction of maximum eccentricity lies at a predetermined angle α has been obtained.

Next, the operation will be explained. When the main shaft 14 rotates, the oscillating scroll 2 performs an oscillating motion about the axis of the main shaft 14 while being guided by the Oldham joint 11 to perform a compression action. The slider 16 slides in the longitudinal direction of the bearing fitting hole 26 due to the component force F' of the resultant force F of the centrifugal force Fc and the gas loads Fg and Fgr, and the oscillating scroll 2 is pressed against the fixed scroll 1 by the contact force F+t at the radius. The compression action is performed by always keeping the directional gap C at zero.

Here, component force F' and contact force Fm are expressed by the following equations.

F' = F cao (-α 10) 1"l-F'/c α ■ α [Problem to be solved by the invention] Since the conventional scroll compressor is configured as described above, the bearing fitting In order to obtain the angle α between the longitudinal direction of the hole 26 and the eccentric direction of the slider 16, the bearing fitting hole 2G is formed at a position r away from the axis of the main shaft 14 and has an angle α with respect to the eccentric direction. It needs to be processed with high precision, the processing method is difficult and special processing tools are required, and it is difficult to accurately inspect the eccentricity r and α, making it unsuitable for mass production. there were.

This invention was made to solve the above-mentioned problems, and it is possible to easily determine the angle α between the longitudinal direction of the bearing fitting hole and the eccentric direction of the slider, and also to The purpose of the present invention is to obtain a scroll compressor with stable accuracy, in which the crankshaft slider device shaft and slider can be machined without the need for extensive machining processes.

[Means for Solving the Problems] A scroll compressor according to the present invention includes a fixed scroll and an oscillating scroll that form a compression chamber by combining both volute wraps, and a side of the oscillating scroll opposite to the volute wrap. an oscillating bearing or oscillating shaft provided at the center of the thrust surface of the oscillating scroll, a frame supporting the thrust surface of the oscillating scroll via the thrust bearing, and a oscillating scroll supported via the main bearing of this frame. A main shaft that transmits driving force, a motor that drives this main shaft, and a swing bearing or swing shaft that is movable in the axial direction, rotatably housed, and slidable in a plane perpendicular to the axis of the main shaft. It is equipped with a slider that engages with the end of the main shaft so that the amount of eccentricity of the center of the oscillating scroll with respect to the center of the fixed scroll can be varied, and furthermore, it is provided with a slider that engages with the end of the main shaft so that the amount of eccentricity of the center of the oscillating scroll is variable with respect to the center of the fixed scroll. In a scroll compressor in which the maximum eccentric direction has a predetermined angle α, the length A between the flat surface of the main shaft end that guides the slider and the main shaft axis
The angle α is characterized by appropriately determining the length B between the flat surface of the bearing fitting hole of the slider that fits into the flat surface and the slider axis.

[For production]

In the scroll compressor of the present invention, whereas in the conventional example the eccentricity r and α were used to determine the above α,
The scroll compressor of this invention only needs to determine the length of A and 82 to determine α, can be machined with high precision without the need for special processing tools, and is relatively easy to perform dimension inspection. In addition to being able to perform highly accurate measurements, α
If α is set to 0, the centrifugal force Fc can be canceled by the component force of the gas load Fg, reducing the contact force F and reducing the compressor input. If α is set to 0, especially in the case of a small scroll compressor, Fc
It is possible to easily and precisely manufacture the angle α in a compact manner so that the slider does not open even in a region where Fc<Fgr is applied at low rotation speeds when a component force of Fg is applied to the slider.

〔Example〕

An embodiment of the present invention will be described below with reference to the drawings. 1st
The figure is a cross-sectional view of a scroll compressor according to the present invention, Figure 2 is a cross-sectional view of the slider mechanism, which is the main part of the invention, in an operating state, and Figures 3 and 4 are cross-sectional views of the main parts of the crankshaft and slider. In the figure, 1 is a fixed scroll having a spiral wrap 1a, 2 is a fixed scroll having a spiral wrap 1a, and 2 is a fixed scroll having a spiral wrap 1a.
This is an oscillating scroll having a spiral wrap 2a that is combined with a compression chamber to form a compression chamber. 3 is the plywood of the swinging scroll 2;
Reference numeral 4a denotes an oscillating scroll bearing protruding from the center of the back surface of this base plate 3, 10 a bearing support fixed to the fixed scroll 1 with bolts, etc., and 11 preventing the oscillating scroll 2 from rotating and allowing it to swing in the radial direction. This is a link-shaped Oldham joint for connecting to the bearing support 10. Reference numeral 14 denotes a main shaft, and a slider mounting shaft 26 having a surface parallel to the heel of the main shaft 14 is provided on the upper end surface of the main shaft.
A is formed on the slider mounting shaft 26a, and the slider 16, which has an elongated inner side, is mounted so as to be slidable in a plane perpendicular to the axis of the main shaft 14 but not rotatable. An oscillating scroll bearing 4a is fitted into the oscillating scroll bearing 4a.

In addition, in FIG. 2, r indicates the slide -1 from the center of the main shaft 14.
6, the eccentricity Fc is the centrifugal force generated during the orbiting operation of the orbiting scroll 2, F is the gas load generated in a direction almost perpendicular to the centrifugal force, Fgr is the gas load generated in the opposite direction to the above Fc, and F is the centrifugal force. The resultant force of force Fc and gas load Fg Fgr,
C is the radial gap between the fixed scroll 1 and the swinging scroll 2,
α is the longitudinal direction of the slider mounting shaft 26a and the slider 1
6 with the eccentric direction, and α is positive on the opposite rotation side of the main shaft 14 from the eccentric direction.

Now, as shown in FIGS. 2, 3, and 4, in this invention, as a method for determining α, the length A between the flat surface of the end of the main shaft 14 that guides the slider 16 and the axis of the main shaft 14 is
And the length B between the flat surface of the slider 16 that fits into the flat surface and the axis of the slider 16 is determined.

Next, the operation will be explained. When the main shaft 14 rotates, the oscillating scroll 2 swings about the axis of the main shaft 14 while being guided by the Oldham joint 11 and performs a compression action. During steady operation, the slider 16 is pushed to a point W where the swinging scroll 2 contacts the fixed scroll l due to the component force in the sliding direction of the resultant force F of the centrifugal force Fc and the gas load Fg and Fgr during the swinging operation of the swinging scroll 2. (that is, the position where the radial clearance C is O).

When α>0, the centrifugal force Fc can be canceled by the component force of the gas load Fg, the contact force F can be reduced, and the input to the compressor can be reduced.

Furthermore, if α<0, the slider 1 will also be in the region where Fg component force is added to Fc and Fc<Fgr at low rotation speeds.
Stable compression can be performed without 6 opening.

According to the present invention, the above-described effects can be easily achieved.

Now, during steady operation of the scroll compressor, the second
As shown in the figure, the axial center of the main shaft 14 and the axial center of the slider 16 are separated by r in the eccentric direction, and the eccentricity r is manufactured with high precision by the swinging scroll 2 and the fixed scroll 1. According to this invention, since A and B are machined with high precision, the length of the slider mounting shaft 26a in the non-longitudinal direction between the axis of the main shaft 14 and the axis of the slider 16 is determined by this, and B, A, and r are Since the accuracy is high, the angle of α can be determined with high accuracy.

In the above embodiment, the main shaft 1 is provided inside the slider 16.
The case of a so-called female-type swinging scroll in which a slider mounting shaft 26a exists at the end of the main shaft 14 has been shown, but as shown in FIG. A similar effect can be obtained even in the case of a so-called male-type oscillating scroll in which there is 16.

[Effects of the Invention] As explained above, according to the present invention, the angle α, which influences the input and reliability of the compressor, is the length A.

Since it is determined by B, the processing method can be simplified,
In addition, it is easy to achieve accuracy, and when performing dimension inspection, measurements can be made with relatively high accuracy without using any special method. Furthermore, since the shape of the slider and the slider mounting shaft of the main shaft can be simplified and lightened easily, an inexpensive and highly accurate scroll compressor can be obtained.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a horizontal scroll compressor according to an embodiment of the present invention, FIGS. 2 to 4 are sectional views of a slider which is the main part of the invention, and FIG. 5 is another embodiment of the slider. 6 is a sectional view of a conventional scroll compressor, and FIG. 7 is an explanatory diagram of the operation of a slider according to a conventional example. 1... Fixed scroll, 1a... Spiral wrap, 2.
...Occillating scroll, 2a...Spiral wrap, 3...
Base plate, 4a... Bearing of swinging scroll, 10... Bearing support, 11... Oldham joint, 14... Main shaft, 1
6...Slider 26...Bearing fitting hole, 26a.
...Slider mounting axis. Note that the same reference numerals in the figures indicate the same or equivalent parts. Agent Masuo Oiwa Figure 1 Figure 2 Figure 3 Two-bearing fitting hole Figure 4 Figure 6 a Figure 5 Figure 7 Year 1998

Claims (1)

[Claims] A fixed scroll and an oscillating scroll that form a compression chamber by combining both spiral wraps, and an oscillating bearing provided at the center of the thrust surface of the oscillating scroll on the opposite side to the spiral wrap. or an oscillating shaft, a frame that supports the thrust surface of the oscillating scroll via a thrust bearing, a main shaft that is supported via a main bearing of this frame and transmits driving force to the oscillating scroll, and a main shaft that drives this main shaft. an oscillating scroll that is movable in the axial direction and rotatably housed in the oscillating bearing or oscillating shaft and is slidable in a plane perpendicular to the axis of the main shaft and that oscillates relative to the center of the fixed scroll; A scroll compressor comprising a slider engaged with an end of a main shaft so that the eccentricity of the center is variable, and further comprising a predetermined angle α between the longitudinal direction of a bearing fitting hole in the slider and the maximum eccentricity direction of an oscillating scroll. , the length A between the flat surface of the spindle end that guides the slider and the spindle axis, and the length B between the flat surface of the bearing fitting hole of the slider that fits into the flat surface and the slider axis, as appropriate. By determining the length, the above angle α can be calculated using the formula,
There are chemical formulas, tables, etc. Scroll compressor characterized by being determined by the relationship ▼.