JPS63248991A - Scroll type compressor - Google Patents

Abstract

PURPOSE:To obtain the high compression rate with a simple structure by fitting the swirl bearing part of a turning scroll and the eccentric bearing part of a main shaft through an inclined bush having a bearing surface inclined for the revolution axis center. CONSTITUTION:A scroll type compressor compresses coolant gas by the cooperation with a fixed scroll 2 by the turning movement of a swirl scroll 1 by a main shaft 7. A cylindrical inclined bearing surface 22 which is inclined for the main shaft 7 is formed on the boss 21 of the swirl scroll 1, and also an inclined bush 23 fitted with the bearing surface 22 has an inclined cylindrical surface 24 having the equal inclination, and further a cylindrical bearing surface 25 coaxially with an eccentric shaft 7a is provided, and these are fitted in slidable ways. Therefore, the swirl scroll 1 is shifted in the radial and axial directions by the centrifugal force due to the dead weight of the swirl scroll 1 which is generated in the turning movement and the inclined bearing surface 22, and the swirl eccentricity quantity is automatically adjusted, and the lap surfaces 1a, 1c and 2a, 2c of the both scrolls 1 and 2 can be surely sealed. Therefore, the high compression rate can be obtained.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to the structure of an orbiting drive mechanism for an orbiting scroll of a scroll compressor used in a refrigeration device such as an air conditioner.

BACKGROUND OF THE INVENTION Scroll compressors have been described in numerous patents and documents, including US Pat. No. 8,011,82, and their operating principles are well known.

Compared to other types of compressors, scroll type compressors have many advantages, such as having a continuous compression operation, resulting in less fluctuations in drive torque and vibration, and the relative speed of the sliding parts being small, making them superior in high-speed performance. There are advantages. Therefore, the use of scroll compressors has been rapidly increasing in recent years.

An example of a conventional scroll compressor will be described below with reference to the drawings.

FIG. 7 is an explanatory diagram of the operating principle of the scroll compressor, and the operating principle will be explained below. FIG. 7 shows a state in which the orbiting scroll 1 is orbiting clockwise with a center-to-center distance e (hereinafter referred to as eccentricity e) with respect to the fixed scroll 2. The volume of the sealed space 3 formed by both scrolls 1 and 2 gradually decreases, and the fluid sucked from the suction port 4 is compressed in the sealed space 3 in a sealed state, and the sealed space 3 communicates with the central discharge port 5. This causes the compressed fluid to be discharged. Thereafter, this operation is repeated to compress the fluid.

The scroll compressor with the above operating principle is constructed as shown in FIG. 8, where 1 is an orbiting scroll having a spiral wrap 1a and an end plate 1b;
2 is a spiral wrap 2a.

A fixed scroll having an end plate 2b, 3 a closed space, 4 a suction port, 5 a discharge boat, 6 a frame, 7 a main shaft having an eccentric shaft 7a, 8 a motor, 9 a rotation prevention mechanism for the orbiting scroll 1, 1o is a closed container, 11 is an inhalation tube, 1
2 is a discharge pipe.

In the scroll compressor configured as described above, the main shaft 7 is rotated by the motor 8, and the orbiting scroll 1 is rotated by an eccentric amount e of the eccentric shaft 7a with respect to the fixed scroll 2 without rotating by the rotation prevention mechanism 9. The fluid taken into the closed space 3 through the suction pipe 11 and the suction port 4 is compressed, and is discharged from the discharge boat 5 into the closed container 10 and further discharged from the discharge pipe 12 to the outside.

Problems to be Solved by the Invention However, in the case of the scroll compressor configured as described above, the eccentricity e of the main shaft 7 and the wrap 1a (or 2a
) and the inner dimension between the wraps 1a (or 2a) are e≦(b-t)/2, and the difference between the left side and the right side, that is, the wrap side gap C1
is 0 to several tens of micrometers, and the wrap tip gap C2 between the tip 1C of the wrap 1a of the orbiting scroll 1 and the end plate 2b of the fixed scroll 2, and the tip 2C of the wrap 2a of the fixed scroll 2 and the end plate 1b of the orbiting scroll 1. The wrap tip clearance C3 between the orbiting scroll 1 and the fixed scroll 2 is also set to O~several tens of μm, so that the wrap Ia of the orbiting scroll 1 and the fixed scroll 2,
It is possible to prevent the compressed fluid in the sealed space 3 formed by the wrap 1a (or 2a) from leaking from the side of the wrap 1a (or 2a) to other rooms, but in order to maintain such a relationship, the above-mentioned Ensure that each dimension of t, b, and e is high,
Height of laps 1a and 2a.

It is necessary to ensure a high degree of shape purity, contour degree, and combination accuracy of both scrolls. However, the shape of the scroll member is complex, making it difficult to process with high precision, and the productivity is poor.

Therefore, conventionally, each of the gaps CI, C2,
C3 was often set at 40 to 60 μm. or,
Some products have gaps in only one direction (e.g. C
Although there are methods to adjust 1) by creating grooves using eccentric pushers, etc., sufficient leakage prevention effects have not been achieved.

In addition, if the dimensional relationship is fixed as described above, when the compressor is used in a refrigeration system, etc., if the refrigerant is compressed in a liquefied state or if foreign matter is caught between both scrolls, In some cases, the scrolls were unable to escape through the narrow gap, causing damage or damage to the walls and end plates of both scrolls.

In view of the above-mentioned problems, the present invention has been developed to easily and automatically adjust the above-mentioned turning eccentricity θ, and also to automatically adjust the gap at the tip of the lamp, so that the amount of turning eccentricity and the turning eccentricity that can reliably seal the lamp wall surface and the tip of the wrap are provided. A scroll compressor having an automatic axial gap adjustment mechanism is provided.

Means for Solving the Problems In order to solve the above-mentioned problems, the scroll compressor of the present invention has a structure in which one of the orbiting bearing of the orbiting scroll and the eccentric bearing of the main shaft is provided with an inclined bearing surface, and the other is provided with an inclined bearing surface. An inclined push is formed on a bearing surface parallel to the spindle rotation axis, and has a bearing surface inclined with respect to the spindle rotation axis on either the inner or outer circumferential surface so that the inclined bearing surfaces fit together. It is interposed between the swivel bearing and the eccentric bearing.

Function Since the present invention has the above-mentioned configuration, the orbiting scroll is moved in the radial direction and axial direction by the centrifugal force generated by the orbiting scroll's own weight and the inclined bearing surface during the orbiting motion of the orbiting scroll, so that the orbiting of the orbiting scroll is prevented. A rotating amount automatic adjustment mechanism that allows the eccentricity e to be easily and automatically adjusted to ensure sealing of the wrap sides of both scrolls, and between the ramp tip of the orbiting scroll and the fixed scroll end plate, and between the ramp tip of the fixed scroll and the orbiting scroll end plate. This feature also includes an automatic axial gap adjustment mechanism that reliably seals the gap.

EXAMPLE Hereinafter, a scroll compressor according to an example of the present invention will be described with reference to the drawings.

FIG. 1 shows an automatic adjustment mechanism for the amount of rotation and the axial clearance of a scroll compressor in one embodiment of the present invention. The same parts as in the conventional example described above are denoted by the same reference numerals, and the explanation thereof will be omitted.

In FIG. 1, 7a is an eccentric shaft of the main shaft 7, 21 is a boss as a driving element of the orbiting scroll 1, and the boss 21 has a cylindrical inclined bearing surface 22 which is inclined with respect to the axis of the main shaft 7.
is formed, and an inclined pusher 23 is fitted into this inclined bearing surface 22. This inclined push 23 has an inclined cylindrical surface 24 having the same inclination angle as the inclined bearing surface 22 on its outer circumference, and a cylindrical bearing surface 25 coaxial with the eccentric shaft 7a on its inner circumference. The inclined bearing surface 22 of the boss 21 of the orbiting scroll 1 and the inclined cylindrical surface 24 of the inclined push 23 are slidably fitted together, and the cylindrical bearing surface 26 of the inclined push 23 is slidably fitted.
It is now slidable on the eccentric shaft 7a of the main shaft 7.

The operation of the above configuration will be explained with reference to FIGS. 2 and 3. FIGS. 2(a) and 2(b) show the state of the drive coupling portion at very low speed when stopped or immediately after starting. In Fig. 2(a), the axis 01 of the main shaft 7 is separated from the axis 02 by an eccentric amount e.
An eccentric shaft 7a having an axis 7a is located, and the inclined push 23 is interposed so that the center o3 of the orbiting scroll 1 is substantially coaxial with the axis o2.

At that time, there is a gap x1 between the side surfaces of the wraps 1a and 2a of both scrolls 1 and 2, and a wrap tip 1 of both scrolls 1 and 2.
A gap y1 between c and 2c and the mating end plates 1b and 2b is provided with a gap (about 1 order) sufficient to prevent liquid compression during startup and the like. FIG. 2(b) shows the positional relationship of each axis and the force acting on the drive connection at that time. Due to the rotation of the main shaft 7 in the direction of arrow A, the eccentric shaft 7a receives approximately a centrifugal force Fr due to the weight of the orbiting scroll 1 and a compressive force Fp due to the gas trapped in the closed space 3 formed by both scrolls 1 and 2. acts, and the resultant force FT becomes the force acting on the bearing of the drive connection. However, when stopped or when rotating at an extremely low speed immediately after starting, these forces Fr.

Fp and FT are zero or extremely small forces, so the center 03 of the orbiting scroll 1 is the axis Q2 of the eccentric shaft 7a.
The gap between both scrolls 1.2, "1 + 71", is almost on the same line as the initial setting value.

FIGS. 3(a) and 3(b) show the state of the connecting portion during one rotation at a predetermined number of rotations. As the rotation speed increases, the centrifugal force Fr of the orbiting scroll 1 increases, and since the centrifugal force Fr acts on the inclined bearing surface 22 of the boss 21 of the orbiting scroll 1, the centrifugal force Fr along the inclined surface increases. The force F3 causes the orbiting scroll 1 to move diagonally. Accordingly, the gap x2 on the side of the lamp between the neck rolls 1 and 2 and the gap y2 on the tip of the wrap decrease, the gas trapped in the sealed space 3 is compressed, and the compressive force Fp required for this decreases.

As the centrifugal force Fr and the compressive force Fp increase, the resultant force F7 thereof, that is, the force acting on the inclined bearing surface 22, further increases, and the component force Fs acting along the inclined surface also increases. Therefore, the orbiting scroll 1 moves in the direction of arrow B, and the gap X 2 between both scrolls 1 and 2 is created.

Since y2 is further reduced, the sealing performance between the sealed spaces 3 is improved, the leakage of gas to the low pressure chamber side is small, and an efficient compression action is performed.

From the above, the initial gap x1. If y1 and the inclination angle are set appropriately (for example, if the inclination angle is 45°, xl""1), the movement of the orbiting scroll 1 along the inclined surface will be facilitated by the gaps x1 (!2) and yl (y2). Both become zero, the leakage of compressed gas to the low pressure chamber side is significantly reduced, and a compressor with high compression efficiency can be obtained.

FIGS. 4 to 6 show other embodiments of the drive connection portion forming the automatic rotation amount and axial gap adjustment mechanism of the scroll compressor of the present invention, respectively. In Figure 4, the end is the main axis 7
The eccentric shaft has an eccentric amount e at the center of the bearing, and has the same inclination angle as the inclined bearing surface 22 of the post 21 of the orbiting scroll 1 in the first embodiment. 23b is a 1f-1 bush having an inclined inner diameter surface, and 21b is a boss of the orbiting scroll 1. Fig. 6 and Fig. 6 are the same as the above-mentioned Fig. 1 to Fig. 3.
Eccentric bearings 7e, 7 corresponding to the eccentric shaft 7a shown in the embodiment of the figure
d is formed in a concave shape at the tip of the main shaft 7, and conversely, the orbiting shafts 2IC and 21d, which correspond to the boss 21a of the orbiting scroll 1, are formed in a protruding shape. Inclined push 23 (1
! , 23d. In the embodiment shown in FIGS. 4 to 6, the resultant force F7 of the centrifugal force Fr and the compressive force Fp acts on the inclined bearing surface as in the first embodiment, and the orbiting scroll 1 moves along the inclination. It moves in the direction of arrow B to reduce the gap "1171" between both scrolls 1 and 2, realizing a highly efficient compressor.

Effects of the Invention As described above, the present invention has a bearing configuration in which the orbiting bearing of the orbiting scroll and the eccentric bearing of the main shaft are fitted through an inclined push having a bearing surface inclined with respect to the rotation axis. By using the centrifugal force generated when the main shaft rotates and the compressive force generated when compressing the gas, the compressed gas in the closed space formed by the ramp and end plate of the orbiting scroll and fixed scroll is transferred to the wrap side and the ramp tip surface. It is possible to prevent leakage from occurring, and a high compression rate can be obtained with a simple configuration.

[Brief explanation of drawings]

FIG. 1 is a vertical sectional view of the main parts of a scroll compressor according to the first embodiment of the present invention, and FIG. Figure 2 (b) is a plan view showing the axial center position relationship and force relationship in Figure 2 (-), Figure 3 (body) is the state of the drive connection part in Figure 1 when operating at a predetermined rotation speed. Fig. 3(b) is a vertical cross-sectional view showing the third
Plan view showing detailed positional relationships and force relationships in figure (-), No. 4
6 to 6 are longitudinal cross-sectional views of the drive connection portion of a scroll compressor according to other embodiments of the present invention, FIG. 7 is a plan view showing the compression principle of the scroll compressor, and FIG. 8 is a conventional FIG. 2 is a longitudinal cross-sectional view of a scroll compressor. 1...Orbiting scroll, 2...Fixed scroll, 3-...Enclosed space, 7...Main shaft, 7a
'... Eccentric shaft, 21...-Pos, 23...
...Incline push. Name of agent: Patent attorney Toshio Nakao and one other person
2 or 7 Scroll 7a--Go button shaft 2f--E

Claims (1)

[Claims] A scroll compressor that includes a fixed scroll and an orbiting scroll, and compresses gas by sequentially decreasing the volume of a closed space formed by the orbiting scroll as the main shaft rotates, thereby reducing the volume of the enclosed space surrounded by both scrolls. One of the orbiting bearing of the orbiting scroll and the eccentric bearing of the main shaft is formed as an inclined bearing surface, and the other is formed as a bearing surface parallel to the rotation axis of the main shaft, and either of the inner circumferential surface and the outer circumferential surface Scroll-type compression characterized in that an inclined pusher having a bearing surface inclined with respect to the main shaft rotation axis on one side is interposed between a swivel bearing part and an eccentric bearing part so that the inclined bearing surfaces fit together. Machine.