JPH03141885A - Rotary compressor - Google Patents

Abstract

PURPOSE:To enhance the volume efficiency by furnishing communicating parts to the internal circumference of a roller and grooves formed from a plurality of a seal parts at each end face of a roller on its bearing side, the roller being accommodated rotatably in a crank of a shaft, wherein the grooves with seal parts stretche in the circumferential direction and reduce the section area as going apart from the communication parts. CONSTITUTION:Grooves 20-24-27 and ones 28-32-35 in the equal number are provided at the end faces 19a, 19b of a roller 19 which contact bearings 7, 8 for a shaft 3, wherein the roller 19 is held rotatably by a crank 3c of the shaft 3. of the shaft 3. These grooves 20-35 are formed from communication parts 20a-35a to the inside circumference of the roller 19 and also seal part 20b-35b, 20c-35c which extend in the circumferential direction from said communication parts 20a-35a and reduce the section area while going apart from the communication parts 20a-35a. Accordingly an oil pressure force is generated by the wedge effect due to the seal parts with rotation in both directions caused by spiral rotating of the roller 19 round its own axis, which ensures high level retention to accomplish enhancement of the volume efficienecy.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a rotary compressor used in a refrigeration cycle or the like, and particularly relates to the configuration of a mechanical part with good volumetric efficiency.

Prior Art A conventional configuration will be explained with reference to FIGS. 3, 4, 6, and 6.

1 is a sealed casing, 2 is an electric motor section, and shaft 3
The cylinder 4, roller 6, vane 6, main bearing 7.
It is connected to a mechanical part main body 9 constituted by a sub-bearing 8. The shaft 3 is a main shaft 3a.

It consists of a subshaft 3b, and a crank 3C eccentric by E from the axes of the main shaft 3a and subshaft 3b. A hole 3e is formed in the center of the shaft 3, and an oil supply hole 3f and an oil supply groove 3q are provided in the crank 3c. 10 is a spring provided on the back side of the vane. 11a, 11bld Inside the cylinder 4, a roller 6, a vane 6, a main bearing 7. These are a suction chamber and a compression chamber formed by the sub-bearing 8. Each end face 5a of the roller 6 faces the main bearing 7 and the sub-bearing 8.

Tapers sc and sd whose cross-sectional area decreases from the inner circumferential side toward the outer circumferential device are provided on the inner circumferential side of 6b. 12 is an oil supply am connected to the shaft 3. Reference numeral 13 denotes a suction pipe, which communicates with the suction chamber 11a via the auxiliary bearing 8 and the suction passage 14 of the cylinder 4. Reference numeral 16 denotes a discharge hole, which communicates with the inside of the sealed casing 1 via the discharge valve 16. 1
Reference numeral 7 denotes a discharge pipe that opens into the sealed casing 1.

18 is lubricating oil.

The direction of the solid arrow in FIG. 6 indicates the direction of movement of the roller 6, which is pressed at a certain point during the operation of the compressor.
8 indicates the direction of flow. Also, so and sf are the taper 5c of the roller 6.

Of 6d, this is a portion (5f not shown) whose cross-sectional area gradually decreases in the direction of the broken arrow, and 5q.

6h is a portion (sh is not shown) whose cross-sectional area is gradually increased.

Next, the compression mechanism of the rotary compressor will be explained.

Refrigerant gas from the cooling system (not shown) is supplied to the suction pipe 1
3. Suction chamber 11a inside cylinder 4 guided from suction hole 14
leading to. The refrigerant gas that has reached the suction chamber 11a is transferred to the shaft 3
The compression chamber 11b is partitioned by a roller 6 and a vane 6, which are rotatably housed in the crank 3C, and is gradually compressed by the rotational movement of the shaft 3 as the motor section 2 rotates.

The compressed refrigerant gas is once discharged into the sealed casing 1 through the discharge hole 16 and the discharge valve 16, and then through the discharge pipe 17.
to the cooling system.

Further, the high-pressure lubricating oil 18 in the sealed casing 1 containing the refrigerant is supplied to the hole 3e of the shaft 3 by the oil supply mechanism 12, and is supplied to the sliding parts of the main bearing 7 and the sub-bearing 8. The oil is supplied to the inner peripheral side of the crank 3C and the roller 6 through the oil supply hole 3f and the oil supply groove 3q, and after lubricating the roller end surfaces 5a and 5b, it reaches the suction chamber 11a and the compression chamber 11b, and then from the discharge hole 15 to the sealed casing 1. The liquid is discharged inside and returns to the lower part of the opening and closing casing 1.

At this time, as the shaft 3 rotates, the roller 6 rotates and revolves around the crank 3c while considering the direction, and as a result, the locus of one point on the roller 6 becomes a spiral. Therefore, the moving direction of the roller 6 is the same as that of the shaft 3.
For example, if the direction of the spiral movement of the roller 6 is the direction shown by the arrow in FIG.

Since the end faces sa and sb of the roller 6 are provided with tapers so and sd, 60 and 6f are formed in the tapers sc and sd.
Only the lubricating oil 18 flows into the vicinity of.

The cross section becomes tapered from the inner diameter side toward the outer diameter side, and hydraulic pressure is generated due to the wedge effect.

(However, 6f' is a part opposite to 50' of the taper 6d, and is not shown.) Therefore, the hydraulic pressure in the vicinity of 6e and 6f of the tapers 6C and 6d is balanced, and as a result, the roller 6 and The roller 6 is held so that the clearance δ8 and δb between the main bearing 7 and the sub-bearing 8 become δ4=δb. By the way, the roller end surface 5a.

6b from the crank 3C side to the suction chamber 11a.

The amount of lubricating oil that has entered the refrigerant solution flowing into the compression chamber 11b is proportional to the cube of the clearance. Therefore, δ1+δb
= constant, the amount of inflow is minimum when δ4 = δb9.As a result, by providing the tapers sc and sd, a highly efficient EE compressor with good volumetric efficiency is provided.

For example, it is shown in Japanese Utility Model Publication No. 61-20317.

Problems to be Solved by the Invention In such a conventional structure, like a small compressor with a small cylinder capacity for refrigeration, the wall thickness of the roller (expressed as (outer diameter - inner diameter)/2) is thin, and high pressure during operation is required. In a compressor with a high ratio of pressure to low pressure (compression ratio), even if a taper is provided to equalize the clearance between the roller end face and the main bearing, and between the roller and the sub-bearing, in reality, the clearance is provided around the entire circumference. The clearance of the tapered part increases by the taper amount, and the sealing distance of the non-tapered flat surface becomes shorter around the entire circumference, so the amount of lubricating oil containing refrigerant dissolved into the suction chamber and compression chamber increases. Even if a taper is provided, leakage loss does not decrease.

There was a problem that the volumetric efficiency did not improve much.

In addition, the conventional structure utilizes the wedge effect of the lubricating oil that enters the taper, and this wedge effect occurs in the orbital motion component of the spiral motion of the roller accompanying the rotational motion of the shaft. Taper of the roller crank because the cross-sectional area does not change in the circumferential direction! Regarding the component of rotational motion around the eagle.

This does not occur and the wedge effect is small. It was a cabinet. The hydraulic pressure generated by the wedge effect is only at one location on the end face of the roller, and is not generated at most locations.

Furthermore, since the tapered portion itself has a shape that communicates in the circumferential direction, the pressure generated by the wedge effect escapes in the circumferential direction, and the pressure generated by the wedge effect is low. As a result, the stability of the roller due to the wedge effect is not sufficient, resulting in a problem that the effect of improving volumetric efficiency is small.

Another conventional example is one in which several grooves are provided on the end surface of a roller, the convergence of which narrows from the inner circumference to the outer circumference. Is it growing?
Or, because the curve is curved in the same direction in either direction of the circumference, it is difficult to generate a sufficient wedge effect against the movement of the roller whose rotation direction changes during one rotation.
In addition, the hydraulic pressure is generated at only one location on the roller, which again poses a problem in that the stability of the roller is not sufficient.

The present invention solves the above-mentioned drawbacks of the conventional example, and aims to improve the volumetric efficiency more than the conventional example, and also allows the suction chamber and compression chamber to be used even in small compressors with thin roller walls and compressors with variable rotation speed. The purpose is to minimize the amount of lubricating oil that has entered the refrigerant solution.

Means for Solving the Problems The present invention provides, on each end face of the roller, a communicating portion with the inner peripheral side of the roller, and a plurality of seals extending approximately in the circumferential direction and decreasing in cross-sectional area as the distance from the communicating portion increases. It is equipped with a groove formed by a stop part.

Effect of the present invention Due to the above-mentioned groove bottom, the lubricating oil flowing into the groove flows in the direction of the smaller cross-sectional area regardless of which direction the roller rotates in response to the rotational component of the roller arm movement. Hydraulic pressure will be generated in either of the sealing parts of the groove.
Can generate large hydraulic pressure. The housing is where the hydraulic pressure is generated.

This occurs at two or more locations on each roller end face. Furthermore, since the lubricating oil that has flowed into the sealing portion of the groove has no place to escape, the hydraulic pressure can be maintained at a high level.

Therefore, the hydraulic pressure generated on both end faces of the roller is large and distributed over the roller end face, and the generated hydraulic pressure can be maintained at a high level, and the clearances δ8 and δb between the roller and the main bearing and sub bearing are reduced to prevent leakage. It is ensured that δ6=δb is the smallest. Furthermore, the groove.

The glass seal distance provided over the entire circumference is longer than in the case of a taper, and as a result, the amount of oil flowing into the compression chamber and suction chamber is reduced, improving volumetric efficiency and reducing leakage losses.

Example Examples will be explained below with reference to FIGS. 1 and 2.

Incidentally, the same parts as in the conventional example are given the same reference numerals, and the description thereof will be omitted.

A roller 19 is rotatably held by the crank 30 of the shaft 3 as in the conventional case. The end surfaces 19a and 19bVCIri of the roller 19 are there.

- The same number of grooves 20-24-27 and grooves 28-32-36 are provided. The grooves 20 to 36 extend from the communicating portions 20a to 36a with the inner peripheral side of the roller 19 and from the communicating portions 20a to 35a along the circumferential direction, and decrease in cross-sectional area as they move away from the communicating portions 20a to 35a. Sealing portions 20b to 36b
and 2oc to 36c.

In this configuration, the refrigerant gas sucked through the suction pipe 13 is compressed in the same way as in the conventional case and is discharged through the discharge pipe 17 to the cooling system.

In addition, the high-pressure lubricating oil 18 in the sealed casing 1 into which the refrigerant has been dissolved also lubricates the drawing part main body 9 as in the conventional case, but the lubricating oil 18 that has flowed into the inner peripheral side of the roller 19
After lubricating parts a and 19b, return to the lower part of the sealed casing as in the conventional case.

As the shaft 3 rotates, the roller 19 rotates as in the conventional case.
The roller 19 performs a revolution movement and an autorotation movement, and as a result, the roller 19 performs an arm movement. The direction of the arm movement at a certain moment is the direction of the solid arrow, as in the conventional case, and the direction in which the lubricating oil 18 flows due to the movement of the roller 19 is the direction of the broken arrow.

At this time, in the grooves 20 to 27 on the end surface 19a of the roller 19, the sealing parts 20c, 21c, 23b, and 24b among the sealing parts 20b to 27b, 20(+ to 27c).

26b, 26b, 26c, and 27c have a reduced cross-sectional area with respect to the flow direction of the lubricating oil 18 indicated by the dashed arrow direction, and the lubricating oil 18 flowing from the communicating portions 20a to 27a generates hydraulic pressure. .

That is, among grooves 20 to 27, grooves other than groove 22.

Hydraulic pressure is generated in one or both of the sealing portions 20b to 27b and 20a to 27c, and the position where the hydraulic pressure is generated is distributed over the roller end surface 19a, unlike the conventional case where the hydraulic pressure is generated only at one location. Also, the grooves 28 to 35 on the end surface 19b are located at symmetrical positions to the groove 3 in the same way as the grooves 20 to 27 on the end surface 19a.
In grooves other than 0, sealing parts 28b to 35b, 28C to 35
Hydraulic pressure is generated at one or both of the end faces 19a and 19b.

Furthermore, roller 19 is spinning! Regarding the rotational component forming 17I, the sealing part 20 whose cross-sectional area decreases approximately in the circumferential direction
b to 35b, 20c, and 36c, a hydraulic pressure due to a wedge effect is generated in either direction of rotation. In addition, the hydraulic pressure is applied to the sealing parts 20b to 35b,
Since it occurs near 20c to 35c, there is no escape for the hydraulic pressure, and the hydraulic pressure is kept high. Therefore, the end surface 19a of the roller 19.

At 19b, hydraulic pressure of the same magnitude is always generated at dispersed positions, resulting in a balance. Dimensions. This hydraulic pressure is higher than the conventional one due to the hydraulic pressure generated by the rotation component and the hydraulic pressure that is kept high without escaping.
= δb, and the 1-volume efficiency is improved.

Furthermore, since the grooves 20 to 36 are provided all around the circumference, the sealing distance is longer than if the grooves are tapered, thereby reducing the amount of lubricating oil flowing into the compression chamber and suction chamber. This improves volumetric efficiency even in small compressors and the like, where the roller wall thickness is thin.

In this embodiment, the cross-sectional area was changed by the groove width, but it may also be changed by the groove depth.

Effects of the Invention Effects of the Invention As is clear from the above description, the present invention has a cylinder, a main bearing and a sub-bearing fixed to the end face of the cylinder, a cylinder that rotates and slides within the main bearing and the sub-bearing, and has a crank. A shaft, a roller rotatably housed in the crank of the shaft, a vane that contacts the roller and slides back and forth in a groove provided in the cylinder, and an end surface facing the main bearing and sub-bearing of the roller, respectively. , the communication part with the inner peripheral side of the roller.

Since it is equipped with a groove formed by a button and a plurality of sealing parts that extend approximately in the circumferential direction and whose cross-sectional area decreases as the distance from the communication part increases, Since hydraulic pressure is also generated, the hydraulic pressure becomes high, and the hydraulic pressure is generated at two or more locations on each end face.

Furthermore, since the lubricating oil that has flowed into the sealing part has no place to escape, the generated hydraulic pressure can be maintained high, so the clearance between the roller end face, main bearing, and sub-bearing can always be maintained evenly, reducing leakage loss. decreases and improves volumetric efficiency. In addition, the groove is not buttoned all around the circumference, so the sealing distance is long, and even a small, high compression ratio compressor with a thin roller wall can provide a compressor with high volumetric efficiency.

[Brief explanation of the drawing]

FIG. 1 is a front view of a roller of a rotary compressor showing an embodiment of the present invention, FIG. 2 is an enlarged sectional view of the mechanical part of the present invention, and FIG.
Figure 4 is a longitudinal cross-sectional view of a conventional rotary compressor, Figure 4 is a view along the line IV-IV' in Figure 3, Figure 5 is an enlarged cross-sectional view of the mechanical part in Figure 3, and Figure 6 is a vertical cross-sectional view of a conventional rotary compressor. FIG. 3 is a front view of a conventional roller. 3...Shaft, 3C...Crank,
4...Cylinder, 6...Vane, 7.
...Main bearing, 8. Mountain...Sub bearing, 19...
・o-7, 19a, 19b...Roller end surface, 2
0~24~27.28~32~36...Groove, 2
0a~24a~27a, 28a~32a~36a...
...Communication portion, 20b to 24b to 27b. 20c-24c-270.28b-32b-36b. 28c to 32c to 36a... Sealing portion.

Claims (1)

[Claims] a cylinder; a main bearing and a sub-bearing fixed to an end surface of the cylinder; a shaft that rotates and slides within the main bearing and the sub-bearing and has a crank; and a roller that is rotatably housed in the crank of the shaft. , a vane that contacts the roller and slides back and forth in a groove provided in the cylinder; and a communication portion with the inner peripheral side of the roller on each of the end surfaces of the roller facing the main bearing and the sub-bearing. and a rotary compressor including a groove formed by a plurality of sealing portions extending substantially circumferentially and decreasing in cross-sectional area as the distance from the communication portion increases.