KR870001339Y1 - Discharging valve device for a compressor - Google Patents

Abstract

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Description

Discharge valve device of the compressor

1 is a partial sectional view showing a main portion of a discharge valve device of a conventional compressor.

2 is a schematic configuration diagram showing the entire compressor in which the discharge valve device of the present invention is installed.

Figure 3 is an enlarged perspective view showing the entire discharge valve device of the present invention.

4 and 5 show a first embodiment of the present invention, each of which is a sectional view of each main part viewed from different directions.

6 is a partially exploded perspective view for explaining the first embodiment of the present invention.

7a and 7b is a sectional view showing the main portion and the discharge valve seat showing a second embodiment of the present invention.

8 to 11 are perspective views showing the discharge valve seat of the third to sixth embodiments of the present invention, respectively.

12 is a noise characteristic diagram of the second, fourth, and sixth embodiments of the present invention corresponding to FIGS. 7, 9, and 11.

13 is a noise characteristic diagram of the third and fifth embodiments of the present invention corresponding to FIGS. 8 and 10.

14 is an explanatory diagram of the oil film strength according to each embodiment of the present invention.

The present invention relates to, for example, a discharge valve device for use in a compressor installed in a refrigeration cycle, and more particularly, to an improvement in discharge efficiency.

1 is a sectional view of the main part of a discharge valve device of a conventional compressor disclosed in Japanese Patent Application Publication No. 1982-12909, where (1) is a discharge port formed in the housing wall 1a, and (2) is a discharge valve. It is a seat seat, is located in the periphery of the discharge side of the said discharge port 1, is protruded integrally with the said housing wall 1a, and the cross-sectional phenomenon is the semicircle curvature. (3) is a discharge valve presser, (4) is a discharge valve composed of an elastomeric material whose one end is fixed to the housing wall (1a), and is provided between the discharge valve seat (2) and the discharge valve presser (3), The discharge port 1 is opened and closed in accordance with the pressure difference in the compression chamber (not shown).

The discharge valve device of the conventional compressor is configured as described above. For example, when the gas compressed in the compression chamber (not shown) reaches a predetermined discharge pressure, the discharge valve is provided on the discharge side of the discharge port 1 circulating with the compression chamber. The discharge valve 4 in close contact with the seat 2 is operated toward the open side by the discharge pressure, and the compressed gas is discharged from the gap formed between the discharge valve 4 and the discharge valve seat 2. After that, when the compression of the compression chamber decreases, the discharge valve 4 is operated to close, seats on the discharge valve seat 2, and shifts to the compression stroke of the compression chamber again. This series of operations is performed continuously.

In order to facilitate such a series of operations, particularly in the discharge valve 4 and the discharge valve seat 2, the gas backflow when the discharge valve 4 is closed and the opening in the open state are prevented from being delayed. The important point is that, in the contact portion between the discharge valve 4 and the discharge valve seat 2, the cross-sectional shape of the discharge valve seat 2 is a semi-circular curvature, together with an oil film for enhancing gas sealing property. By providing a curvature surface on the surface, the contact portion with the discharge valve 4 is an annular contact, and the diameter connecting the vertex portion of the discharge valve seat 2 is again the diameter of the discharge port 1. It was made larger so that the contact pressure of the discharge valve 4 and the discharge valve seat 2 may be raised.

By the way, in the discharge valve apparatus of the conventional compressor as described above, for example, when the compressed gas is discharged from the compression chamber, the discharge valve 4 and the discharge valve seat 2 are simultaneously discharged with lubricating oil together with the gas. ), The oil film spreads in a band shape and exceeds the desired sealed contact width, and as a result, when the discharge valve 4 is opened, the oil film resistance increases and the opening is delayed due to the oil film spread in the band shape. there was.

Therefore, in the conventional apparatus, it is the cause which increases the pressure of a compressor.

Moreover, since the resistance of the oil film is large when the discharge valve 4 breaks the oil film and moves toward the open side, noise is generated when the oil film is destroyed.

The present invention is made for the purpose of improving the problems of the conventional discharge valve device of the compressor, and the oil film sealing contact width caused by the contact between the discharge valve and the discharge valve seat has the same curvature as the discharge valve seat. The present invention proposes a discharge valve device for a compressor that is excellent in discharge efficiency by preventing the delay of opening in the opening operation of the discharge valve by delaying the oil film sealing contact width caused by the flat discharge valve.

Next, the discharge valve device of the present invention compressor will be described in detail with reference to the drawings.

2 is a schematic configuration diagram of a compressor according to an embodiment of the present invention, in which a motor consisting of a stator 12 and a rotor 13 is accommodated in a sealed container 11, The compression operation is performed by vanes (not shown) which divide the driven crankshaft 14, the cylinder 15, the piston 16, and the compression chamber into a high pressure chamber and a low pressure chamber. Moreover, the side housings 17a and 17b which form the compression chamber and serve as the bearings of the crankshaft 14 are arrange | positioned at the cylinder both ends.

The refrigerant guided by the suction pipe (not shown) is led to the compression chamber, and the compression operation is performed by the piston 16, the cylinder 15, and the vane which are eccentrically rotated by the crankshaft 14 driven by the electric motor. When the pressure in the compression chamber is slightly higher than the internal pressure of the container 11, the discharge valve 18 opens to discharge gas into the discharge muffler 20 from the discharge port formed in the side housing 17a. In order to regulate the movement of the valve 18, a discharge valve presser 19 is provided. The discharge refrigerant gas with reduced noise in the discharge muffler flows into the sealed container 11 and passes through the discharge pipe to form a foreign refrigeration cycle with a heat exchanger.

3 is an enlarged perspective view of a discharge valve device according to an embodiment of the present invention, and detailed configuration of the discharge valve of the present invention will be described later, and thus description thereof will be omitted.

In FIG. 3, in the discharge port portion provided in the side housing 17a, the discharge valve 18 and the discharge valve presser 19 are fixed to the side housing 17a by bolts 21 and the like.

Next, the discharge valve device of the compressor according to the embodiment of the present invention will be described in detail with reference to the following detailed drawings.

Next, the first embodiment of the present invention is shown in FIGS. 4 to 6 and will be described in detail. 4 is a cross-sectional view showing the first embodiment of the present invention, and (1) is a discharge port formed in the housing 17a. (22) is a discharge valve seat located in the periphery of the discharge port (1), the discharge valve seat having a discharge portion integrally formed with the housing (17a), (19) is a discharge valve presser, (28) is a thin discharge valve The valve seat seating position 28a has a curved surface with a radius of curvature ρ ₁ seated near the apex peak of the discharge valve seat 22. Fifth Fourth help art discharge valve apparatus turn is 90 ° and the configuration of cutting to a different cross-section, the cross-section of the valve seat seating location (28a) of the discharge valve 28 of the thin plate has a different radius of curvature and ρ ₁ ρ ₂ Has 6 is a perspective view of the discharge valve 28, wherein the valve seat seating position 28a forms a curved surface and is part of the surface of the ellipsoid 30, the radius of curvature ρ ₁ in the X direction and the radius of curvature ρ _{2 in the} Y direction. This is different.

The first embodiment of the present invention is constructed as described above, the operation of which is basically the same as the conventional device described in FIG. The contact line 29 of the discharge valve 28 to the discharge valve seat 22 is substantially elliptical, as shown in FIG. 6, and has a sealing property to prevent gas flowing back into the compression chamber from the high pressure portion outside the compression chamber. Have In addition, in the opening operation of the discharge valve 28, since the annular contact line 29 is substantially elliptical and is not in the same plane but is wave-shaped, the discharge valve 28 is in operation. The contact width for sealing the oil film is reduced at the lower portion of the discharge valve seat 22 so that the opening is not delayed. In addition, the noise generated when the discharge valve 28 breaks the oil film formed for preventing the backflow and shifts to the opening operation is also reduced by the decrease in the oil film resistance. In addition, since the contact position of the discharge valve 28 and the discharge valve seat 22 is formed in an approximately elliptical annular shape, the direction in which the discharge valve 28 starts to open is constant, and the acoustic characteristics of the discharge gas noise are uniform and the noise level is It has the advantage that the nonuniformity of is small.

According to the first embodiment of the present invention, as described above, the seated portion of the discharge valve 28 on the discharge valve seat 22 is formed by a curved surface having anisotropy, and the discharge valve seat 22 is separated from the discharge valve seat 22. By making the contact line an annular line having a substantially elliptical curve, the contact width for oil film sealing when the discharge valve 28 transitions to the opening operation is reduced in the lower portion of the discharge valve seat 22, and the discharge valve 28 This prevents delays in opening and makes the compressor more efficient. In addition, since the energy for breaking the oil film layer when the discharge valve 28 operates is reduced, it also has an effect of suppressing the noise generated at the time of the destruction, and the direction in which the discharge valve 28 starts to open is constant. As a result, the nonuniformity of the noise level becomes small.

Next, the second to sixth embodiments of the present invention will be shown in FIGS. 7 to 11 and will be described in detail. FIG. 7 (a) and FIG. 7 (b) are a sectional view of a configuration and a discharge valve seat showing a second embodiment of the present invention. (1) is a discharge port formed in the housing 17a, and (22) is a discharge valve which is located in the periphery of the discharge side of the discharge port 1, and has a cross-sectional shape which is formed integrally with the housing 17a and has approximately the same curvature. Sheet. Denoted at 19 is a discharge valve presser, 18 is a flat discharge valve as shown in FIG. 1, 23 is formed at the discharge valve seat 22, and a groove is formed so that the discharge port 1 is concentric with the circumference. to be.

The second embodiment of the present invention is constructed as described above, and the operation is performed substantially the same as the apparatus of the first embodiment described in FIGS. 4 and 5. In addition, the resistive force when the discharge valve 18 transitions to the opening operation is mainly determined by the oil film sealed contact width and the oil film thickness at the contact portion between the discharge valve 18 and the discharge valve seat 22, but the discharge valve seat ( Since the grooves are formed in the direction in which the discharge port 1 and the concentric circumference cross each other, the oil film resistance during the opening operation of the discharge valve 18 is reduced, so that opening of the discharge valve 18 can be prevented from being delayed. . Moreover, since the operation | movement which opens the discharge valve 18 becomes smooth, the noise at the time of the operation which opens the discharge valve 18 can be suppressed low. Further, by forming the groove 23 at one side of the discharge valve seat 22, it is possible to provide a compressor in which the direction in which the discharge valve 18 starts to be opened is constant and the nonuniformity in acoustic characteristics is small. However, the depth of the groove 23 of the discharge valve seat 22 is not preferable to make it too deep for the reason that the gas tightness when the discharge valve 18 is closed is good.

8 to 11 show the third to sixth embodiments of the present invention, and FIGS. 8 and 9 show that the grooves 23 of the discharge valve seat 22 are disposed substantially radially with respect to the discharge port. Embodiments of the third and fourth embodiments of the present invention, and FIGS. 10 and 11 are fifth embodiments of the present invention in which substantially radial grooves 23 are arranged alternately inside and outside of the apex of the discharge valve seat 22. , Sixth embodiment.

Here, the improvement of the noise characteristic of the thing by the 2nd-6th implementation of this invention is shown, FIG. 12, FIG. 13 shows the comparison of the noise characteristic B of these Example with the conventional noise characteristic A. FIG. FIG. 12 is the second, fourth, and sixth embodiments corresponding to FIGS. 7, 9, and 11 in which the grooves 23 are disposed on one side, and the noise level and the It can be understood that the nonuniformity is improved.

FIG. 13 shows the third and fifth embodiments corresponding to FIGS. 8 and 10 in which the groove 23 is not biased to one side, and it can be understood that the noise level is improved in comparison with the conventional A. FIG.

As described above, in the second to sixth embodiments of the present invention, since the groove 23 is formed in the discharge valve seat 22 to intersect the circumference of the discharge port, the opening of the discharge valve 18 is delayed. That can be improved. As a result of smooth operation of opening the discharge valve, it has an effect of reducing noise during the operation of opening the discharge valve. In addition, if the groove 23 is formed, the direction in which the discharge valve 18 starts to be opened is made constant, which also has the effect of suppressing the nonuniformity of noise during the operation of opening the discharge valve.

Here, the oil film strength of the lubricating oil between the discharge valve seat and the discharge valve forming the main part of the present invention will be briefly described with reference to FIG. FIG. 14 conceptually shows a contact state between the discharge valve seat 50 and the discharge valve 51. In FIG. 14, (1) corresponds to the conventional example corresponding to FIG. 1, and (2) corresponds to FIG. A first embodiment (3) of a design of the present invention shows a second embodiment of the present application corresponding to FIG.

Next, when the discharge valve is easy to open, the degree of easy opening (α) becomes as in the formula (1).

Easy to open: α = (One)

only, : Surface tension of lubricant

: Pressure difference between internal pressure Pc and external pressure Pd

In addition, the surface tension of the lubricant And pressure difference Is the same as (2) and (3).

(2)

(3)

A: average oil film width

r: change average film

Next, substituting equation (2) and equation (3) into equation (1) results in (4).

(4)

Therefore, the degree (alpha) which is easy to open of a discharge valve becomes proportional to a / r.

Here, the degree of easy opening α 1 of the conventional example of FIG. 14 (1) and the degree of easy opening α 2 and α 3 of each of the embodiments shown in the drawings (2) and (3) will be described next. In addition, small numbers (1) through (3) represent values corresponding to the drawings (1) to (3).

In the case of Fig. 14 (2), as can be seen from the figure,

a② <a①, r②> rⓛ

Each condition of is true,

Α② becomes conditionally smaller than α①.

Next, FIG. 14 shows that in the case of (3), as shown in FIG.

a③ <a①, r③ = r①

Each condition of is true,

Α③ becomes smaller than α①.

As described above, Fig. 14 (2) is conditional, and (3) is unconditionally compared with the discharge valve of Fig. 14 (1), so that each discharge valve is easy to open. In addition, with regard to the sealing property, the present invention can be carried out by appropriately selecting the dimensions of each part within a range that does not impair the freezing performance.

As described above, according to the present invention, since the oil film resistance when the discharge valve is shifted to the opening operation is reduced, opening of the discharge valve can be prevented from being delayed. In addition, since the energy for destroying the oil film layer when the discharge valve is operated is reduced, the noise generated at the time of the breakdown is suppressed, and the direction in which the discharge valve starts to open becomes constant, so that the effect of suppressing the noise nonuniformity is also reduced. have.

Claims (7)

A discharge valve seat having a discharge port circulating with the compression chamber, the discharge valve seat having a curvature in the cross-section of the discharge side, and a discharge valve for pressing and contacting a part of the discharge valve seat to open and close the discharge port according to the pressure in the compression chamber. And discharge the gas compressed in the compression chamber out of the compression chamber against the pressing force of the discharge valve which presses the discharge valve seat and the oil film adhesion force of the lubricating oil attached near the contact portion between the discharge valve seat and the discharge valve. In the discharge valve device of a compressor, an oil film in the case where the oil film sealing contact width generated by the contact between the discharge valve and the discharge valve seat is generated by the discharge valve seat and the flat discharge valve having the same curvature as the discharge valve seat. The discharge valve is reduced in comparison with the closed contact width, and the discharge valve is in contact with the discharge valve seat The discharge valve device of the compressor, characterized in that the seating portion (着 座 部) configured by a curved surface having an anisotropy. The discharge valve apparatus of a compressor according to claim 1, wherein the seating portion of the discharge valve is substantially elliptical. The discharge valve apparatus of a compressor according to claim 1, wherein the height of the discharge valve seat in the circumferential direction is made nonuniform. 4. The discharge valve apparatus of a compressor according to claim 3, wherein one or a plurality of grooves are formed in the discharge valve seat. 2. The discharge valve apparatus of claim 1, wherein the discharge valve seat is formed with a groove extending in a radial direction with respect to the discharge port on its surface. 6. The discharge valve apparatus of a compressor according to claim 5, wherein the grooves of the discharge valve seat are asymmetrically arranged. 6. The discharge valve apparatus of a compressor according to claim 5, wherein the grooves of the discharge valve seat are alternately arranged inside and outside the apex of the valve seat.