JP2000087889A - Rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce the leakage quantity of operating gas caused by the size of a spring hole inner side part biting into a blade groove between the side faces of a blade and the blade groove. SOLUTION: A coil spring 5 for energizing a blade 4 onto the roller side is provided on the base end part 42 side of the blade 4. A cylinder 1 has a blade groove 6 for guiding the blade 4 slidably, and a spring hole 8A for receiving the coil spring 5. The diameter of an outer side part 82 of the spring hole 8A almost corresponds to the diameter of a fixed part 52 larger than the diameter of a body 50 in the coil spring 5. The diameter of an inner side part 84 of the spring hole 8 is smaller than the diameter of the outer side part 82. The diameter of the inner side part 84 can therefore be made relatively smaller than the conventional one.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a (rolling piston type) rotary compressor in which a blade groove for guiding a blade and a spring hole for receiving a coil spring for urging the blade are formed in a cylinder. Regarding improvement.

[0002]

2. Description of the Related Art FIG. 4 shows a compression mechanism of a general (rolling piston type) rotary compressor.
In FIG. 4, the rotary compressor includes a pair of cylinders 1 stacked with a partition plate 9 therebetween. next,
As shown in FIGS. 4 and 5, each cylinder 1 has a substantially cylindrical shape, and a drive shaft 2 penetrates the inside thereof. A main bearing 2 supporting the drive shaft 2 with a pair of cylinders 1 interposed therebetween.
0 and an auxiliary bearing 22 are provided.

In each cylinder 1, a roller 3 is provided. These rollers 3 are mounted eccentrically with respect to the rotation axis of the drive shaft 2, and are configured to roll on the inner peripheral surface 10 of the cylinder 1 with the rotation of the drive shaft 2 as shown in FIG. ing. A blade 4 is slidably attached to each cylinder 1 in the radial direction. As shown in FIGS. 5 and 6, these blades 4 are configured such that the tips 40 abut on the outer peripheral surface of the roller 3. In addition, what is indicated by reference numeral 24 in FIG. 5 is a suction pipe.

Further, a coil spring 5 (see FIG. 7) for urging the blade 4 toward the roller 3 is provided on the base end 42 side of each blade 4. Each cylinder 1 has a blade groove 6 for slidably guiding the blade 4 and a spring hole 8 for receiving the coil spring 5.

As shown in FIG. 8, the spring hole 8 has an inner portion 80 that cuts into the blade groove 6 on the inner peripheral surface 10 side (left side in FIG. 8) of the cylinder 1 and an outer peripheral surface 1 of the cylinder 1.
And an outer portion 82 opened to two sides. A longitudinal through hole 7 for inserting a cutting tool for forming the blade groove 6 is formed on the spring hole 8 side at the end of the blade groove 6.

Next, as shown in FIG. 7 and FIG. 8, the coil spring 5 has a
And a fixing portion 52 having a diameter D1 (> D3) formed at one end of the main body 50 and fitted to the outer portion 82 of the spring hole 8.

Here, the blade 4 reciprocates with a stroke 2e twice as large as the eccentricity e of the roller center 3C with respect to the cylinder center 1C shown in FIG. Along with this,
As shown in FIG. 7, the coil spring 5 has a maximum length L during operation.
And a minimum length L0 (= L-2e). FIGS. 5, 6 and 8 show the blade 4
Shows the state in which the coil spring 5 projects most into the cylinder 1 and the coil spring 5 is at the maximum length L during operation.

As shown in FIG. 8, when the coil spring 5 is in the state of the maximum operation length L, the distal end portion 51 has a spring hole 8.
And extends into the blade groove 6. This is because the coil spring 5 maintains contact with the base end portion 42 of the blade 4 even in the state of the maximum operation length L.

In this case, as shown in FIG. 8 (a), the spring hole 8 has a uniform diameter D1 '(the diameter of the fixing portion 52 of the coil spring 5) throughout the outer portion 82 to the inner portion 80. D1).

[0010]

The conventional rotary compressor as described above has the following problems. That is, in FIG. 5, the pressure Pm of the discharge-side compression chamber of the compression chamber partitioned by the cylinder 1, the roller 3, and the blade 4 is higher than the pressure Ps of the suction-side compression chamber.
The discharge pressure Pd outside the cylinder 1 may be higher or lower than the discharge pressure Pd depending on the process of the compressor.

Then, the pressure P of the discharge side compression chamber is
Due to the pressure difference between m and the discharge pressure Pd, a slight leak (in / out) of the working gas occurs through the blade groove 6 and the spring hole 8 of the cylinder 1, which causes a reduction in the efficiency of the compressor.

In particular, as shown in FIG.
Is most protruded into the cylinder 1, the sealing area between the side surfaces of the blade 4 and the blade groove 6 is reduced, and the size of the inner portion 80 of the spring hole 8 biting into the blade groove 6 is also reduced.
This causes the leakage of the working gas as described above (see the arrow in FIG. 8A).

The present invention has been made in view of the above points, and reduces the amount of working gas leakage due to the size of the inner portion of the spring hole that bites into the blade groove, thereby achieving a highly efficient rotary. An object is to provide a compressor.

[0014]

A first means comprises a substantially cylindrical cylinder whose end is closed, a crankshaft penetrating the cylinder, and an inner periphery of the cylinder with the rotation of the crankshaft. A roller configured to roll the surface, and slidably mounted in the cylinder in the radial direction,
A blade having a distal end contacting an outer peripheral surface of the roller; and a coil spring provided on a base end side of the blade and biasing the blade toward the roller, wherein the cylinder slides the blade. The cylinder has a blade groove for movably guiding, and a spring hole for receiving the coil spring. The spring hole of the cylinder has an inner portion that bites into the blade groove on the inner peripheral surface side of the cylinder, and an outer periphery of the cylinder. And a diameter of the inner part is smaller than a diameter of the outer part.

According to the first means, the amount of leakage of the working gas caused by the size of the inner portion of the spring hole that bites into the blade groove is reduced by making the diameter of the inner portion of the spring hole smaller than the diameter of the outer portion. Can be reduced.

According to a second means, in the first means, the diameter of the spring hole gradually decreases from the outer portion toward the inner portion.

According to a third aspect, in the first aspect, the diameter of the spring hole is continuously reduced from the outer portion toward the inner portion.

[0018]

Next, an embodiment of the present invention will be described with reference to the drawings. 1 to 3 are views showing an embodiment of a rotary compressor according to the present invention. Note that, in the embodiment of the present invention shown in FIGS.
The same components as those of the general rotary compressor shown in FIGS. 4 to 7 are denoted by the same reference numerals, and will be described with reference to FIGS. 4 to 7 as appropriate.

[First Embodiment] First, a first embodiment of the present invention will be described with reference to FIGS. 1, 2 and 4 to 7. First, as shown in FIG.
The compression mechanism includes a pair of cylinders 1 stacked with a partition plate 9 interposed therebetween.

Next, as shown in FIGS. 4 and 5, each cylinder 1 has a substantially cylindrical shape, and a drive shaft 2 penetrates the inside thereof. Further, the drive shaft 2 is sandwiched between the pair of cylinders 1.
Are provided with a main bearing 20 and a sub-bearing 22 for supporting the bearing. That is, each cylinder 1 includes a partition plate 9 and a bearing 20,
Both ends are closed by 22.

Each cylinder 1 is provided with a cylindrical roller 3. These rollers 3 are mounted eccentrically with respect to the rotation axis of the drive shaft 2, and are configured to roll on the inner peripheral surface 10 of the cylinder 1 with the rotation of the drive shaft 2 as shown in FIG. ing. A blade 4 is slidably attached to each cylinder 1 in the radial direction. These blades 4 are shown in FIGS.
As shown in FIG. 2, the tip portion 40 comes into contact with the outer peripheral surface of the roller 3. In addition, what is indicated by reference numeral 24 in FIG. 5 is a suction pipe.

In FIG. 5, the pressure Pm of the discharge side compression chamber among the compression chambers partitioned by the cylinder 1, the rollers 3 and the blades 4 is higher than the pressure Ps of the suction side compression chamber, but the pressure outside the cylinder 1 is reduced. The pressure Pd may be higher or lower than the discharge pressure Pd depending on the process of the compressor (the position of the roller 3 in the cylinder 1).

A coil spring 5 (see FIG. 7) for urging the blade 4 toward the roller 3 is provided on the base end 42 side of each blade 4. By the urging force of the coil spring 5, the contact between the tip portion 40 of the blade 4 and the roller 3 is maintained. Each cylinder 1 has a blade groove 6 for slidably guiding the blade 4 and a spring hole 8A for receiving the coil spring 5.

The blade groove 6 penetrates through the cylinder 1 in the thickness direction and extends from the middle of the cylinder 1 in the radial direction to the inner peripheral surface 10 as shown in FIGS. I have. 1 and 2, the spring hole 8A is located on the inner peripheral surface 10 side of the cylinder 1 (the left side in FIGS. 1 and 2).
5 has an inner portion 84 that bites into the blade groove 6 and an outer portion 82 that opens to the outer peripheral surface 12 side of the cylinder 1. A vertical through hole 7 for inserting a cutting tool for forming the blade groove 6 is formed on the spring hole 8A side at the end of the blade groove 6.

Next, as shown in FIGS. 1 and 7, the coil spring 5 includes a main body 50 having a diameter D3 and a fixing portion 52 having a diameter D1 (> D3) formed at one end of the main body 50. Have. In this coil spring 5, the main body 50 is extendable and contractible in the spring hole 8A, and the fixing portion 52 is fitted to the outer portion 82 of the spring hole 8A.

Here, the blade 4 reciprocates with a stroke 2e which is twice the eccentricity e of the roller center 3C with respect to the cylinder center 1C shown in FIG. Along with this,
As shown in FIG. 7, the coil spring 5 has a maximum length L during operation.
And a minimum length L0 (= L-2e). 1, 5 and 6 show the blade 4
Shows the state in which the coil spring 5 projects most into the cylinder 1 and the coil spring 5 is at the maximum length L during operation.

As shown in FIG. 1, when the coil spring 5 is in the state of the maximum operation length L, the distal end portion 51 has a spring hole 8.
A extends to the inside portion 84 of A and enters the blade groove 6. This is because, as described above, the coil spring 5 maintains contact with the base end portion 42 of the blade 4 even in the state of the maximum operation length L.

The spring hole 8A according to the present embodiment is
As shown in (a), the outer portion 82 has the same diameter D1 'as the conventional one (slightly smaller than the diameter D1 of the coil spring fixing portion 52), but the inner portion 84 has the same diameter as the outer portion 82. It has a diameter D2 smaller than D1 '. That is, the diameter of the spring hole 8A of the present embodiment is reduced by one step from the outer portion 82 to the inner portion 84. In this case, the diameter D2 of the inner portion 84 of the spring hole 8A is equal to the coil spring body 50.
The diameter D of the coil spring body 50 to such an extent that
Must be set larger than 3.

Next, the operation and effect of this embodiment having the above configuration will be described. As described above, in the state where the blade 4 projects most into the cylinder 1, the sealing area between the side surfaces of the blade 4 and the blade groove 6 decreases,
The size of the inner portion 84 of the spring hole 8A that has penetrated the blade groove 6 may also contribute to the leakage (in / out) of the working gas through the blade groove 6 of the cylinder 1 and the spring hole 8A.

However, according to the present embodiment, the spring hole 8
By making the diameter D2 of the inner portion 84 of A smaller than the diameter D1 'of the outer portion 82, the diameter D2 of the inner portion 84 can be made relatively smaller than before. For this reason, the amount of leakage of the working gas due to the size of the spring hole inner portion 84 that bites into the blade groove 6 can be reduced, and a more efficient rotary compressor than before can be provided.

[Second Embodiment] Next, a second embodiment of the present invention will be described with reference to FIG. In this embodiment,
As shown in FIG. 3, instead of the spring hole 8A, a spring hole 8B tapered toward the inner peripheral surface 10 of the cylinder 1 is provided, and the spring hole 8B is replaced with the coil spring 5. The first embodiment differs from the first embodiment in that a coil spring 5A corresponding to the shape of 8B is used.
This is the same as the first embodiment shown in FIGS. 2 and 4 to 7.

Specifically, as shown in FIG. 3, the spring hole 8B of the present embodiment extends from the outer portion 82 toward the inner portion 86 (strictly, interrupted by the through hole 7). The diameter continuously decreases.

The coil spring 5A according to the present embodiment has the distal end 53
The main body 58 on the side continuously decreases in diameter toward the distal end portion 53 corresponding to the shape of the spring hole 8B. The main body 56 of the coil spring 5A on the fixing portion 52 side has a uniform diameter D3, similarly to the main body 50 of the coil spring 5 described above.

Next, the operation and effect of this embodiment having the above configuration will be described. According to the present embodiment,
The diameter of the inner portion 86 of the spring hole 8B is changed to the diameter D of the outer portion 82.
By making it smaller than 1 ′, the diameter of the inner part 86 can be made relatively smaller than before. Further, since the coil spring 5A whose diameter is reduced toward the distal end portion 53 is used, the diameter of the inner portion 86 of the spring hole 8B can be further reduced as compared with the case of the first embodiment.

For this reason, the amount of leakage of the working gas due to the size of the spring hole inner portion 86 that bites into the blade groove 6 is further reduced as compared with the case of the first embodiment, and a more efficient rotary A compressor can be provided.

The spring hole 8A whose diameter decreases by one step from the outer portion 82 toward the inner portion 84, the outer portion 82
Although the case where the spring hole 8B whose diameter continuously decreases from the inside toward the inside portion 86 is provided, the spring hole whose diameter gradually decreases from the outside portion to the inside portion over a plurality of steps is provided. Is also good.

[0037]

According to the present invention, it is possible to provide a high-efficiency rotary compressor by reducing the amount of leakage of the working gas due to the size of the inner portion of the spring hole that bites into the blade groove.

[Brief description of the drawings]

FIG. 1 (a) shows a first example of a rotary compressor according to the present invention.
(B) is a cross-sectional view of a main part in the embodiment of FIG.
FIG. 3 is a diagram illustrating a cross section taken along the line B, omitting a blade.

FIGS. 2 (a) and 2 (b) are FIGS. 1 (a) and 1
The figure which shows the part shown to (b) by cylinder single body.

FIG. 3 (a) shows a second example of the rotary compressor according to the present invention.
(B) is a cross-sectional view of a main part in the embodiment of FIG.
The figure which omits a blade in the 1-B1 line cross section.

FIG. 4 is a longitudinal sectional view showing a compression mechanism of a general rotary compressor to which the present invention is applied.

FIG. 5 is a sectional view taken along line VV of FIG. 4;

FIG. 6 is a vertical sectional view showing the periphery of a blade of the rotary compressor shown in FIG. 4;

FIG. 7 is a side view showing a coil spring for urging the blade in the rotary compressor shown in FIG. 4;

8 (a) is a cross-sectional view of a main part of a conventional rotary compressor, and FIG. 8 (b) is a cross-sectional view taken along line B2-B2 of FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Cylinder 10 Inner peripheral surface 12 Outer peripheral surface 2 Crankshaft 3 Roller 4 Blade 40 Tip 42 Base end 5,5A Coil spring 50,56,58 Body 51,53 Tip 52 Fixed part 6 Blade groove 8,8A, 8B Spring hole 80,84,86 Inner part 82 Outer part D1 Diameter of fixed part of coil spring D1 'Diameter of outer part of spring hole D2 Diameter of inner part of spring hole D3 Diameter of body of coil spring

Claims (3)

[Claims] 1. A substantially cylindrical cylinder having both ends closed, a crankshaft penetrating the cylinder, and an inner peripheral surface of the cylinder rolling with the rotation of the crankshaft. A roller, a blade slidably mounted in the cylinder in a radial direction, a tip of which is in contact with an outer peripheral surface of the roller; and a blade provided on a base end side of the blade, the blade being connected to the roller. A cylinder spring having a blade groove for slidably guiding the blade, and a spring hole for receiving the coil spring. On the peripheral surface side, an inner portion that bites into the blade groove, and an outer portion that opens to the outer peripheral surface side of the cylinder, wherein the diameter of the inner portion is smaller than the diameter of the outer portion Rotary compressor, characterized in that there. 2. The rotary compressor according to claim 1, wherein said spring hole gradually decreases in diameter from said outer portion to said inner portion. 3. The rotary compressor according to claim 1, wherein the diameter of the spring hole decreases continuously from the outer portion toward the inner portion.