JPH0472484A - scroll compressor - Google Patents

Abstract

PURPOSE:To simplify the control of parts and enlarge the load capacity of an oscillating bearing part in a wide range of operating conditions by forming a slider or the boss part of an oscillating scroll into soft structure for compensating the inclination of a crankpin. CONSTITUTION:A slider 3 is engaged with the crankpin 4a of a main spindle, in such a way as to be slidingly reciprocated in the axial direction. The slider 3 is also engaged rotatably with the oscillating bearing 2c of the boss part 2b of an oscillating scroll 2. In this case, the slider 3 is provided with a soft structure space 3, a circular deep groove, across one face of a slider drive face 3a from the crankpin 4a inserting side. The inclination of the crankpin 4a is thereby absorbed, and the oscillating bearing 2c and the slider peripheral surface 3e can be held in the relatively parallel relation. As a result, there is no need to previously provide the slider drive face 3a or the crankpin drive face 4b with any inclination matching the inclination of the crankpin 4a, and the load capacity of the oscillating bearing part can be enlarged in a wide range of operating conditions.

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a scroll compressor used in refrigeration equipment, air conditioners, etc.

[Conventional technology]

FIG. 6 is a longitudinal cross-sectional view of the main components of a conventional scroll compressor disclosed in, for example, Japanese Patent Application Laid-Open No. 1-159480.

In FIG. 6, 1 is a fixed scroll having plate-shaped spiral teeth 1a, and 2 is an oscillating scroll having plate-shaped spiral teeth 2a. Both plate-shaped spiral teeth 1a and 2a mesh with each other to form a compression chamber. There is. 2b is a boss portion of the swinging scroll 2 provided on the surface opposite to the plate-like spiral teeth 2a, and a swing bearing 2C is formed on the cylindrical inner surface.

3 is a slider inserted into the boss portion 2b, and its inner surface is a slider driving surface 3a, and its outer peripheral surface is a slider outer peripheral surface 3e in contact with the swing bearing 2c.

Reference numeral 4 denotes a first bearing 5a and a second bearing 5a provided on the first frame 5.
The main shaft is radially supported, that is, rotatably supported, by a second bearing 6a provided on the frame 6, and a crank pin 4a is provided at the end on the compression mechanism side, that is, the end on the boss portion 2b side. and its crank pin drive surface 4b
is engaged with the slider driving surface 3a of the slider 3 so as to be able to reciprocate and slide in the linear direction that is the axial direction. In addition, the slider outer peripheral surface 3e of the slider 3 is a swing bearing 2C.
The main shaft 4 is rotatably engaged with the main shaft 4 and functions to transmit the driving force generated by the main shaft 4 to the swinging scroll 2. At the same time, the slider 3 has the function of minimizing the radial leakage gap of the compression chamber by performing minute reciprocating movements in the linear direction along the crankpin driving surface 4b, following the variations in the spiral shape.

Next, in FIG. 7, in (^) and (B), the crank pin drive surface 4b of the crank pin 4a is formed with a slight angle of inclination, and in (C) and (0), the slider 3
The slider driving surface 3a is formed at a slight angle inclination. In addition, (A) and (C) show the cross sections of the slider 3 and the main shaft 4 in the stopped state, and (B) and (D) show the states in which the slider 3 and the main shaft 4 are engaged in the operating state. is shown in cross section.

Next, the operation will be explained.

In FIG. 6, the main shaft 4 is rotationally driven by an electric motor.
The rotational power is transmitted to the swinging scroll 2 via the slider 3, causing the swinging scroll 2 to rotate. Due to this orbiting motion of the oscillating scroll 2, the compression chambers formed between the plate-shaped spiral teeth 1a of the fixed scroll 1 and the plate-shaped spiral teeth 2b of the oscillating scroll 2 are narrowed one after another, and the refrigerant gas is compressed. It is done. Due to this compression operation, the gas load in the radial direction acts on the plate-shaped spiral teeth 2a of the oscillating scroll 2, and the oscillating bearing 2c and the slider outer peripheral surface 3.
e, it acts on the slider 3, and then acts on the crank pin 4a of the main shaft 4 via the slider drive surface 3a and the crank pin drive surface 4b. On the other hand, since the main shaft 4 is supported in the radial direction by the first bearing 5a and the second bearing 6a, it has a cantilevered structure against the radial gas load and is bent.Due to the bending of the main shaft 4, the crank pin 4a It has an inclination angle with respect to the first bearing 5a.

In FIG. 7, in both cases (A) and (B) and cases (C) and (D), the inclination angle of the slider drive surface 3a provided in advance and the inclination angle of the crank pin 4a are are almost the same, and therefore the slider outer circumferential surface 3
e is parallel to the first bearing 5a shown in FIG.

- On the one hand, a swing bearing 2c, a first bearing 5a, and a second bearing 6a formed on the inner surface of the boss portion 2b of the swing scroll 2;
are parallel to each other, so in the swing bearing part,
The shaft, that is, the slider outer circumferential surface 3e, and the bearing, that is, the swing bearing 2c are maintained parallel to each other. If the parallelism between the slider outer circumferential surface 3e and the swing bearing 2C is maintained, the load capacity of the swing bearing can be increased.

[Problems to be Solved by the Invention] Since the conventional scroll compressor is configured as described above, in order to increase the load capacity of the swing bearing part, the slider drive surface 3a or the crankpin drive surface 4 is
In order to provide the angle b in advance with an inclination matching the inclination of the crank pin 4a, the following problem occurred.

(2) It is difficult to process and control the angle of a minute inclination provided on the slider drive surface 3a or the crankpin drive surface 4b.

■ The magnitude of the radial gas load changes depending on the operating conditions, and the deflection angle of the main shaft 4 and the inclination angle of the crank pin 4a also change accordingly.
Alternatively, it becomes difficult to set the angle of the minute inclination provided on the crank pin drive surface 4b.

This invention was made to solve the above problems, and provides a scroll compressor that can simplify the management of parts and increase the load capacity of the swing bearing under a wide range of operating conditions. The purpose is to obtain.

(Means for Solving the Problems) One scroll pressure mm of the present invention includes a slider that is engaged with a crank pin of a main shaft so as to be able to reciprocate in the axial direction, and the slider oscillates in a boss portion of an oscillating scroll. In a scroll press rotatably engaged with a dynamic bearing, the slider or boss part has a flexible structure.

Another scroll compressor of the present invention is a scroll compressor in which a flexible structure space is formed in the vicinity of the maximum oil film pressure generation area in the slider.

[Function] In one scroll compressor of the present invention, the inclination of the crank pin of the main shaft is absorbed by the flexible structure of the slider or the boss part of the swinging scroll, so that the inner surface of the boss part in the swing bearing part The relative parallel relationship between the swing bearing and the outer circumferential surface of the slider as a shaft can be maintained.

In another scroll compressor according to the present invention, the flexible structure space near the maximum oil film pressure generation area of the slider weakens the rigidity in the vicinity of that area, causes elastic deformation, and widens the maximum oil film pressure generation area on the outer peripheral surface of the slider.

〔Example] Embodiments of the present invention will be described below with reference to the drawings.

In FIG. 1, parts that are the same as or equivalent to the conventional ones are designated by the same reference numerals 1 to 6 as in FIG. 6. la~6a, 2b.

2c, 3e, and 4b are attached. The plate-shaped spiral teeth 1a of the fixed scroll 1 and the plate-shaped spiral teeth 2a of the oscillating scroll 2 mesh with each other to form a compression chamber. The oscillating scroll 2 has a boss portion 2b on a surface opposite to the plate-like spiral teeth 2a, and a oscillating bearing 2c is formed on the cylindrical inner surface of the boss portion 2b.

The main shaft 4 is supported in the radial direction by a first bearing 5a provided on the first frame 5 and a second bearing 6a provided on the second frame 6. Further, a crank pin 4a is provided at the end of the main shaft 4 on the compression mechanism side, and a crank pin drive surface 4b of the crank pin 4a is engaged with a slider drive surface 3a of the slider 3 so as to be slidable back and forth in a linear direction. .

The slider 3 is rotatably engaged with the swing bearing 2c, and functions to transmit the driving force generated by the main shaft 4 to the TG scroll 2. At the same time, the slider 3 makes minute reciprocating movements in the linear direction along the crankpin drive surface 4b, thereby following the variations in the spiral shape.
It has the function of minimizing the leakage gap in the radial direction of the compression chamber.

The configuration of the main parts described above is the same as that of the conventional example.

3b is a flexible structure space provided in the slider 3, which will be explained with reference to FIG. 2. In FIG. 2, (A) is a cross-sectional view of the slider 3, and (B) is a vertical cross-sectional view of the slider 3. A flexible structure space 3b, which is a deep groove, is provided in the slider 3. The rigidity of the slider drive surface 3a of the slider 3 is weakened by the flexible structure space 3b, and the slider drive surface 3a of the slider 3 is made to be elastically deformed.

In addition, in Fig. 2, (C) shows a cross section of the slider 3 and the main shaft 4 in a stopped state, and (D) shows a cross section of the slider 3 and the main shaft 4 in an engaged state in an operating state. There is.

Next, the operation of this embodiment will be explained with reference to FIGS. 1 and 2. In FIG. 1, the configuration of the main parts is the same as the conventional example, so the main shaft 4 is bent and the crank pin 4a is bent by the first bearing 5a by the same mechanism as explained in the conventional example.
As shown in FIG. 2 (D), in the operating state, the main shaft 4 is bent and the crank pin 4a has an inclination angle. On the other hand, the slider driving surface 3a of the slider 3 is
Due to the provision of the flexible structure space 3b, the rigidity is weakened and elastically deformed by the action of the radial gas load. Therefore, the slider driving surface 3a of the slider 3
Although the slider 3 is inclined according to the inclination of the crank pin drive surface 4b of the crank pin 4a, as shown in FIG.
The slider outer peripheral surface 3e is parallel to the first bearing 5a. On the other hand, since the swing bearing 2C, the first bearing 5a, and the second bearing 6a are set in parallel, the shaft, that is, the slider outer peripheral surface 3e, and the bearing, that is, the swing bearing 2, are arranged in parallel.
It remains parallel to C.

FIG. 3 shows a second embodiment of the present invention. In the first embodiment, the slider 3 is provided with a flexible structure space 3b, but in this embodiment, a flexible structure space is provided in the boss portion 2b of the oscillating scroll 2. The difference is that In Fig. 3, (A) is the boss portion 2.
(B) is a vertical cross-sectional view of the boss portion 2b.

In FIGS. 3A and 3B, a hollow cylindrical flexible structure space 2d, which is a ring-shaped deep groove, is provided in the boss part 2b from the opening side of the boss part 2b to the outer periphery of the rocking bearing 2C. There is. The rest of the configuration is the same as the conventional example, so the explanation thereof will be omitted.

In addition, in Fig. 3, (C) is the boss part 2 in the stopped state.
b etc. are shown in cross section, and (D) is a cross section of the boss portion 2b etc. in an operating state.

In the operating state shown in FIG. 3(D), the main shaft 4 is bent;
The crank pin 4a has an inclination angle, and this inclination angle is transmitted from the slider 3 because the crank pin drive surface 4b of the crank pin 4a is in surface contact with the slider drive surface 3a of the slider 3. The slider outer peripheral surface 3e also has the same inclination angle. On the other hand, the rigidity of the swing bearing 2C of the boss portion 2b is weakened due to the flexible structure space 2d provided on the outer periphery, and the swing bearing 2C of the boss portion 2b is elastically deformed by the action of the radial direction gas load, and the slider outer peripheral surface 3e of the slider 3 is Since they have the same inclination angle, that is, the shaft or slider outer peripheral surface 3e and the bearing or the swing bearing 2c have the same inclination angle in the swing bearing portion, a relative parallel relationship is maintained.

As described above, by forming a flexible structure space in the slider or boss part, an effect of correcting the inclination due to the action of the radial gas load or an effect of following the inclination is generated, and the shaft and the oscillating The relative parallelism of the dynamic bearings is maintained. Furthermore, these effects are effective even when the operating conditions change, the radial gas load changes, and the inclination of the crank pin changes.

In the above embodiment, a flexible structure space is provided to provide a flexible structure, but it is also possible to create a flexible structure by making the wall thickness thinner closer to the end of the boss portion of the oscillating scroll.

In addition, a relief is provided in the half area of the inner surface of the boss part of the orbiting scroll on the side closer to the end of the boss part, and a hollow cylindrical bearing member is press-fitted into the inner surface of the boss part of the orbiting scroll. It may also be used as a swing bearing.

As mentioned above, one way to increase the load capacity of the swing bearing is to keep the shaft and the bearing relatively parallel in the swing bearing and to effectively utilize the entire length of the bearing in the width direction. This is a method of obtaining maximum load capacity, in other words, a method of avoiding uneven contact within the bearing. Apart from this, in the embodiment described below, there is a method of increasing the bearing load capacity, which is used for integrating the oil film pressure, by lowering the rigidity of the bearing in the vicinity of the maximum oil film pressure generation area.

FIG. 4 shows another embodiment of the present invention, in which (A) is a longitudinal cross-sectional view of the slider 3, and (B) is a cross-sectional view thereof. The other configurations are the same as in FIG. 1. In FIG. 4, the slider 3 is provided with another flexible structure space 3c in the form of a through hole, in addition to the already explained flexible structure space 3b. This flexible structure space 3c has a maximum oil film pressure generation area 3 of the slider outer peripheral surface 3e of the slider 3 inside the slider 3.
It is formed near d, and the maximum oil film pressure generation area 3d
It plays the role of reducing the rigidity of the surrounding area.

The vicinity of the maximum oil film pressure generation area 3d of the slider 3 has a flexible structure space 3c, so the rigidity is weakened and is elastically deformed by the maximum oil film pressure, so that the maximum oil film pressure generation area 3
d expands as shown by the solid line in FIG. 5, increasing the contact area in the sliding direction. In Fig. 5, the broken line shows the distribution of oil film pressure (vertical axis) when the flexible structure space 3C is not provided in the slider 3, and the solid line shows the distribution of the oil film pressure (vertical axis) with respect to the sliding direction position of the bearing (horizontal axis) when the flexible structure space 3C is provided. . The load capacity of the bearing is expressed by the size of the contact area in Fig. 5, so by providing the flexible structure space 3C, the load capacity can be increased from 20 to 30
%improves.

〔Effect of the invention〕

As described above, according to the present invention, the boss portion of the slider or the oscillating scroll is configured to have a flexible structure to compensate for the inclination of the crank pin. The effect of increasing the load capacity of the swing bearing section can be obtained.

Further, since the flexible structure space is provided in the vicinity of the maximum oil film pressure generation area of the slider, there is an effect of increasing the load capacity of the swing bearing portion.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view of the main parts of a scroll compressor according to an embodiment of the present invention, FIG. 2 is a sectional view showing the flexible structure space of the slider and its operation, and FIG. 3 is another embodiment of the present invention. FIG. 4 is a sectional view showing the flexible structure space of the boss part and its operation according to an example. FIG. 4 is a sectional view showing the flexible structure space near the maximum oil film pressure generation area of the slider. FIG. FIG. 6 is a vertical sectional view of the main parts of a conventional scroll compressor, and FIG. 7 is a sectional view showing the relationship between a crank pin and a slider. In the figure, 1... fixed scroll, 1a... plate-shaped spiral tooth, 2... oscillating scroll, 2a... plate-shaped spiral tooth, 2
b... Boss portion, 2c... Rocking bearing, 3... Slider 2d3b... Flexible structure space, 3c... Flexible structure space, 3d... Maximum oil film pressure generation area, 4... main shaft,
4a... Crank pin, 5a... First bearing, 6a...
...Second bearing. Note that the same reference numerals in the figures indicate the same or equivalent parts. Agent Masuo Oiwa Figure 1 Figure 2 (B) Figure 3 ρΦMori D 1 Gin Morisun Figure 2 (A) (C) (D)

Claims (2)

[Claims] (1) A fixed scroll and an oscillating scroll that are intermeshed with each other so that their plate-like spiral teeth form a compression chamber, are rotatably supported at substantially multiple locations, and are rotationally driven by an electric motor; The main shaft has a crank pin provided at its end on the compression mechanism side, and a slider is engaged with the crank pin so as to be able to reciprocate and slide in the axial direction. In a scroll compressor that is rotatably engaged with an oscillating bearing formed on the inner surface of a boss disposed on the opposite side, the slider or the boss section of the oscillating scroll is connected to the crank pin. A scroll compressor characterized by having a flexible structure to compensate for inclination. (2) A fixed scroll and an oscillating scroll that are intermeshed with each other so that their plate-like spiral teeth form a compression chamber, and a main shaft that is rotationally driven by an electric motor and has a crank pin at the end on the compression mechanism side. and a slider engaged with the crank pin so as to be able to reciprocate and slide freely in the axial direction, and the slider is provided with an inner surface of a boss portion disposed on a surface opposite to the plate-like spiral teeth of the oscillating scroll. 1. A scroll compressor which is rotatably engaged with a swing bearing formed in the slider, characterized in that a flexible structure space is formed in the vicinity of the maximum oil film pressure generation region of the slider.