JPS60122287A - Discharge valve apparatus of compressor - Google Patents

Abstract

PURPOSE:To improve discharge efficiency by reducing the contact width of the oil-film seal of the contact surface between the valve and the valve seat of a discharge valve for a compressor incorporated into refrigeration cycle, thus preventing the delayed opening of the discharge valve. CONSTITUTION:A valve seat 22 having a nearly circular form is installed onto the peripheral edge part on the discharge side of a discharge port 1, and a convex part is formed onto a valve 18a arranged between a discharge valve press 19, in order to prevent the contact width of the oil-film seal in the vicinity of the top part of the valve seat 22 from increasing, and the valve 18a is brought into contact outside the top part of the valve seat 2. While, the contact inside the top part of the valve seat 22 is permitted by forming a concaved part onto a valve 18c.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a discharge valve device used in a compressor incorporated in a refrigeration cycle, for example, and particularly to improvement of discharge efficiency.

[Prior art]

FIG. 1 is a cross-sectional view of the main parts of a conventional compressor discharge valve device shown in Japanese Patent Publication No. 57-12909.
1) is a discharge port (2) formed in the housing wall (1a).
) is a discharge valve seat located at the discharge side periphery of the discharge port (11), and is integrally formed in a protruding manner with the housing wall (1a).
Moreover, its cross-sectional shape has a semicylindrical curvature. (
3) is a discharge valve holder, and (4) is one end of which is attached to the housing wall (
a discharge valve made of an elastic material fixed to ia), provided between the discharge valve seat (2) and the discharge valve holder (3);
The discharge port (1) is opened and closed in response to a pressure difference in a compression chamber (not shown).

The discharge valve device of a conventional compressor has two or more <44 configurations, for example, when the gas compressed in a compression chamber (not shown) reaches a predetermined discharge pressure, a discharge port (1
) The discharge valve (4), which is in close contact with the discharge valve seat (2) provided on the discharge side, moves to the open side due to the above discharge pressure, and the discharge valve (4) and the discharge valve seat (2) The compressed gas is discharged through the gap. Thereafter, as the pressure in the compression chamber decreases, the discharge valve (4) moves to the closing side, seats on the discharge valve seat (2), and moves to the compression stroke of the compression chamber again. This series of operations is then performed continuously.

In order to perform this series of operations smoothly, especially the discharge valve (
4) and the discharge valve seat (2), it is important to prevent gas backflow when the discharge valve (4) is closed and delay in opening when the discharge valve (4) is open. Discharge valve seat (
At the contact part with the discharge valve (2), the cross-sectional shape of the discharge valve seat (2) has a semicylindrical curvature, and the outer surface has a curvature surface, as well as an oil film to improve the gas sealing property. ) is made into an annular contact part, and the diameter connecting the apex of the discharge valve seat (21) is made larger than the diameter of the discharge port (1), so that the discharge valve (4) and the discharge valve seat (2) are in contact with each other in an annular manner. The contact pressure was increased.

However, in the conventional compressor discharge valve device as described above, for example, when the gas compressed in the compression chamber is discharged, lubricating oil is also discharged together with the gas, so the discharge valve (
4) and the discharge valve seat (2), the oil film spreads in a band-like manner and exceeds the desired sealing contact width.As a result, when the discharge valve (4) is opened, the above-mentioned band-like Due to the oil film that spread over the area, the oil film resistance increased, causing a problem that caused a delay in opening.

This has caused an increase in compressor input in conventional devices.

Further, when the discharge valve (4) breaks the oil film and moves to the open side, the resistance of the oil film is large, which causes noise to be generated when the oil film is broken.

[Overview of the invention]

This invention was made for the purpose of improving the problems that the conventional discharge valve device of a compressor had. By reducing the curvature of the oil film compared to the oil film seal produced by a flat discharge valve, opening delay in the opening operation of the discharge valve can be prevented, and a discharge valve device of a compressor with excellent discharge efficiency can be achieved. This is a proposal.

[Embodiments of the invention]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The compressor discharge valve device of the present invention will be described in detail below with reference to the drawings.

FIG. 2 is a schematic configuration diagram of a compressor according to an embodiment of the present invention, in which an electric motor consisting of a stator 021° and a rotor U31 is housed in a closed container ALL, and a crankshaft (141 and Cylinder scream and piston (
161 and a vane (not shown) that divides the compression chamber into a high pressure chamber and a low pressure chamber.

Further, side housings (17a) and (Bb), which form a compression chamber and also serve as bearings on the crankshaft side, are arranged at both ends of the cylinder.

The refrigerant drawn from the suction pipe (not shown) is led to the compression chamber, and is compressed by the cylinder (151° vane (not shown)) and the piston rotated eccentrically by the crankshaft side driven by the electric motor. When the operation is performed and the compression chamber pressure becomes a little higher than the internal pressure of the closed container OD, the discharge valve a & opens and gas flows out into the discharge muffler from the discharge port provided in the side housing (17a). (I.W.
A discharge valve holder α(2) is provided to restrict the movement of the valve. The sound of the discharged refrigerant gas is reduced in the discharge muffler,
It flows out into the closed container QD, passes through the discharge pipe, and is led to the heat exchanger, thus forming a refrigeration cycle.

FIG. 3 is an enlarged perspective view of a discharge valve device according to an embodiment of the present invention, and the detailed structure of the main parts of the present invention will be described later, so it is omitted.

In Fig. 3, the discharge port part installed in the side housing (17a) has two discharge valves (181 and a discharge valve holder (19+).
is the side housing (17a) with bolts (211 etc.)
Fixed.

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

FIG. 4 is a sectional view showing the main part of the first embodiment of the present invention, and (1) is a discharge port formed in the housing (17a). (The second one is the almost circular discharge valve seat.

It is located at the discharge side periphery of the discharge port (1) and has a cross-sectional shape with approximately the same curvature. 09) is a discharge valve holder, (18a) is a discharge valve composed of an elastic thin plate, and the corresponding part of the discharge valve seat (support) is press-formed.
A partially convex portion is provided, and its corner portion is seated outside the apex of the discharge valve seat curvature surface.

The first embodiment of this invention is constructed as described above, and its basic operation is almost the same as that of the conventional device explained in FIG. It has a sealing property that prevents refrigerant gas from flowing back into the room, and when the discharge valve (18a) is opened, the discharge valve (18a)
) and the discharge valve seat (2), and the amount of lubricating oil film, that is, the contact area including the oil film seal contact and thickness, By providing a convex part on (XSa), the amount of oil film in contact with the seal is reduced, the amount of reduction suppresses the amount of oil film formed on the contact part, and the oil film resistance when the discharge valve (ISa) is opened is reduced. This prevents opening delays. Also, when the discharge valve (18a) breaks the oil film formed to prevent backflow and shifts to the opening operation, noise is generated, but by reducing the oil film resistance, the noise can be completely suppressed.

Next, a second embodiment of the present invention will be described with reference to FIGS. 5 and 6. FIG. 5 is a sectional view of its configuration.

FIG. 4 is a schematic assembly diagram of the discharge valve device. In Fig. 5 and Fig. 6, the discharge valve (28b) has a hole in the corresponding part of the discharge port fi+, and a compression chamber (not shown) is formed at the contact part with the discharge valve (zsb) and the discharge valve seat @. 1) It seals the refrigerant gas flowing into the compression chamber from the high pressure area outside. Discharge valve (28
The discharge valve seat a) is seated on the outside of the apex of the curvature cross section of the discharge valve seat (18
b) The opening delay can be prevented and noise can be suppressed. Naturally, the structure must be such that the space between the discharge valve (2sb) and the discharge valve seat (sha) opens before the space between the 2nd discharge valve (zsb) and (ZSa) opens.

This can be easily constructed if the oil film contact area between the discharge valve (2Sa) and (zsb) is larger than the oil film contact area between the discharge valve (2sb) and the discharge valve seat (2).

In the first and second embodiments of the present invention, as described above, the curvature surface of the discharge valve seat is formed by providing an image portion in the discharge valve seat corresponding portion of the discharge valve or by using a plurality of discharge valves having different shapes. Since it is structured to sit on the outside of the apex, it limits the oil film layer that forms between the discharge valve seat and the discharge valve, which are the contact parts, and reduces the oil film resistance when the discharge valve shifts to the opening operation. Therefore, the delay in opening of the discharge valve can be prevented. Since the energy required to destroy the oil film layer when the discharge valve operates is reduced, it also has the effect of suppressing the noise generated when the oil film layer is destroyed.

Next, another embodiment of the present invention will be described with reference to FIGS. 7 and 8. FIG. 7 is a cross-sectional view showing a third embodiment of the present invention. (1) is a discharge port formed in the housing (17a). (Company) is a discharge valve seat located at the discharge side peripheral edge of the above-mentioned discharge port tit, and has a cross-sectional shape with approximately the same curvature. (19+ is the discharge valve holder, (18c) is the discharge valve,
A corresponding portion of the discharge valve seat (17o) is provided with a partially convex portion, and the corner portion thereof is seated inside the apex of the curvature surface of the discharge valve seat.

The third embodiment of the present invention is constructed as described above, and its operation is similar to that of the device of the first embodiment explained in FIG. 4. The discharge valve (18c) has a sealing property that prevents gas from flowing back into the compression chamber from the opening of the discharge valve (18c).
c) and the contact pressure determined by the interaction between the internal and external pressure difference of the contact surface with the discharge valve seat (2) and the contact area including the oil film amount, that is, the oil film thickness.

By providing a convex portion on the discharge valve (18c), the amount of oil film in contact with the seal is reduced, and by the amount of reduction, the amount of oil film formed on the contact portion is suppressed, and the oil film during the opening operation of the discharge valve (18c) is reduced. Because it reduces resistance.

This ensures that there is no opening delay. Also, the discharge valve (1
8c) generated noise when it broke the oil film formed to prevent backflow and shifted to the opening operation.

By reducing oil film resistance, noise can be suppressed.

Furthermore, FIG. 8 shows a cross-sectional view of the configuration of a fourth embodiment of the present invention, in which the tip of the discharge valve Qsd) is seated inside the apex of the curvature cross section of the discharge valve seat (170). Similarly to the third embodiment, the opening delay of the discharge valve (18d) can be prevented and noise can be suppressed.

As described above, in the third and i4 embodiments of the present invention, curved portions are provided in the corresponding parts of the discharge valve seat (2) of the discharge valves (18c) (18d), and the curved portions are provided inside the apex of the discharge valve seat curvature surface. The seated structure reduces the oil film seal contact 1] formed between the contact part, the discharge valve seat and the discharge valve, and reduces the oil film resistance when the discharge valve shifts to the opening operation. Therefore, the delay in opening of the discharge valve can be prevented. Furthermore, since the energy that destroys the oil film layer when the discharge valves (18C) and (18d) operate is reduced, it also has the effect of suppressing the noise generated when the oil film layer is destroyed.

Next, a fifth embodiment of the present invention is shown in FIGS. 9 to 11 and will be described in detail. FIG. 9 is a sectional view showing a fifth embodiment of the present invention, in which (1) is a discharge port formed in a housing (2). (321 is a discharge valve seat located at the peripheral edge of the discharge port (1) and has a protrusion formed integrally with the housing surface; αIll is a discharge valve holder; +311
Reference numeral 1 denotes a thin plate-shaped discharge valve, which is seated near the apex of the protrusion of the discharge valve seat C32), and the valve seat seating tube (38a) has a cross section of a curved surface with a radius of curvature ρ1. FIG. 10 is a block diagram of the discharge valve device taken at a cross section that differs by 90 degrees from that in FIG. have different radii of curvature ρ2. FIG. 11 is a perspective view of the discharge valve (2).

The valve seat #r (3sa) has a curved surface and is an ellipsoid (to)
The radius of curvature ρ in the X direction and the radius of curvature ρ2 in the Y direction are different.

The fifth embodiment of the present invention is constructed as described above, operates almost the same as the device of the first embodiment explained in FIG. (The contact line (to) 321 has a substantially oval shape as shown in FIG. 11, and has a sealing property that prevents gas from flowing back into the compression chamber from the high pressure part outside the reverse compression chamber. In addition, the discharge valve example In the opening operation of the discharge valve example, since the annular contact line (3!19) has a substantially elliptical shape and is not in the same plane and has ridges, The contact width for the oil film seal is reduced at the lower part of the discharge valve mc+a, so that there is no delay in opening.Also, the discharge valve (to) breaks the oil film formed to prevent backflow and shifts to the opening operation. The noise generated when the oil film is removed is also reduced due to the reduction in oil film resistance.Furthermore, since the contact force between the discharge valve (to) and the discharge valve seat (32i) is approximately elliptical, This has the advantage that the direction in which the valve 08) starts to open is constant, the acoustic characteristics of the discharged gas noise are uniform, and the variations in the noise level are reduced.

The fifth embodiment of this invention is as described above.

By forming the seating part on the discharge valve seat S4 when the discharge valve is open by a curved surface having anisotropy, and making the contact line with the discharge valve seat (toward) an annular line with approximately elliptical ridges. , the contact period for the oil film seal when the discharge valve (to) transitions to the opening operation is reduced at the lower part of the discharge valve seat c12).

This prevents a delay in the opening of the discharge valve (38) and increases the efficiency of the compressor. In addition, since the energy required to destroy the oil film layer when the discharge valve operates is reduced, it has the effect of suppressing the noise generated when the oil film is destroyed, and the direction in which the discharge valve begins to open remains constant. Variation in noise level is reduced.

Next, the sixth to tenth embodiments of this invention are shown in FIGS. 12 to 1.
Figures A and B shown in Figure 8 and explained in detail are a cross-sectional view of a configuration and a perspective view of a discharge valve showing a sixth embodiment of the present invention, and (1) is a discharge port formed in the housing 01.

(421) is a discharge valve seat located at the discharge side peripheral edge of the second discharge port (1) and integrally molded with the upper housing (47I) and having a cross-sectional shape with approximately the same curvature.

[91 is a discharge valve valve, (4) is a flat discharge valve similar to the one shown in Fig. 1, (4shi is a discharge valve seat (4';! J) It is a groove provided so as to intersect with the concentric circumference.

The sixth embodiment of the present invention is constructed as described above, and its operation is almost the same as that of the device of the first embodiment explained in FIG. The contact pressure determined by the interaction between the internal and external pressure difference of the contact surface between the discharge valve (4) and the discharge valve seat (421) and the contact area including the amount of oil film, that is, the thickness of the oil film, is determined by 2) By providing a groove in the direction that intersects the circumference concentric with the discharge port (1), the contact width for oil film sealing is reduced, suppressing the amount of oil film and, as a result, reducing the total contact pressure. Valve (4)
Avoid opening delays! can do. Also·
Since the opening operation of the discharge valve (4) is performed smoothly, the noise during the opening operation of the discharge valve (4) can be suppressed to a low level.
Ru. Furthermore, the two grooves (O) and the discharge valve seat (Q)
By providing this, the direction in which the discharge valve (4) starts to open is kept constant.

A compressor with less variation in acoustic characteristics can be provided. However, the depth of the groove in this discharge valve seat (42) is to improve gas sealing when the discharge valve (4) is closed, so it is not advisable to make it too deep. Needless to say.

Furthermore, FIG. 13 to FIG. 16 are the seventh to FIG.
81410, and FIGS. 13 and 14 show a discharge valve 1ffl (421 grooves (seventh and eighth embodiments of this invention in which four grooves are arranged approximately radially with respect to the discharge port). As an example, FIGS. 15 and 16 show the ninth and tenth embodiments of the present invention, in which substantially radial grooves (45) are alternately arranged inside and outside the apex of the discharge valve seat C4.

Now, to explain the improvements in noise characteristics according to the sixth to tenth embodiments of the present invention, Figures 17 and 18 show the noise characteristics B of these embodiments and the conventional noise M-characteristic A.
This shows a comparison of Fig. 17 shows a groove (451) corresponding to Fig. 12, Fig. 14, and Fig.
．． 8th. This is the IOth embodiment, and it can be seen that the noise level and noise are improved compared to the conventional example A. Figure 18 shows the 13th groove where the groove (45) is not biased.
7. Corresponding to FIG. This is the ninth embodiment, and it can be seen that the C noise level is improved compared to conventional example A.

As described above, in the sixth to tenth embodiments of the present invention, a groove (45I) is provided in the discharge valve seat (421) so as to intersect with the circumference concentric with the discharge port, so that the discharge valve (4) can be opened easily. The delay can be improved.Also, as a result of smoothing the opening operation of this discharge valve (4), it has the effect of reducing the noise during the opening operation of the discharge valve.In addition, this groove (45; If provided, the direction in which the discharge valve (4) starts to open will be made constant, and it will also have the effect of suppressing variations in IJii and sound during the discharge valve opening operation.

Here, the strength of the lubricating oil film between the discharge valve seat and the discharge valve, which is a main part of the present invention, will be briefly explained with reference to FIG. 19. Fig. 19 conceptually shows the contact state between the discharge valve seat (■) and the discharge valve t511 and the oil film state due to the surface tension of lubricating oil. Fig. 19+11 shows a conventional example corresponding to Fig. 1. , (2) of the same figure corresponds to the i41 of this invention corresponding to FIG.
(3) shows the third embodiment of this invention corresponding to No. 7-1, and (4) of the same figure shows the fifth embodiment of this invention corresponding to FIG. 11. - Also, FIG. 5(5) shows a sixth embodiment of the present invention corresponding to FIG. 12.

Next, when considering the ease of opening of the discharge valve, the ease of opening α becomes like a mountain.

However, ΣFThe surface tension of the oil ΣP: The differential pressure between the internal pressure Pc and the external pressure I'd. The surface tension ΣF and differential pressure ΣP of the oil are expressed by equations (2) and (3).

ΣF =2πra−F・・・・・・・・・・・・・・・
・・・・・・・・・・・・・・・・・・・・・・・・
... (2) Σ△P=πr2・△P...
・・・・・・・・・・・・・・・・・・・・・・・・
・・・・・・・・・・・・・・・ (3) However, a: average oil film r: average oil film rlJ Next, (2) (Substituting equation 31 into equation (1) and rearranging, (4 ) is as follows.

Therefore, the ease with which the discharge valve opens α is proportional to ri.

Here, the ease of opening α of the conventional example shown in FIG. 19 (1). and the ease of opening α of each of the embodiments shown in (2) to (5) of the figure. ~α.

will be explained below. In addition, small numbers ■～■ are shown in the same figure (
1 shift corresponding to 1) to (5) is shown. In the case of Fig. 19 (2).

As can be seen from (2) in the same figure.

%<:2 "Q) 'r■>' (Since each condition of ri is satisfied, α. becomes smaller than α. as shown below.

Next, in the case of Figure 19 (3), as can be seen from Figure 19 (3).

”■＜2　”(j)”　■-’CD Each condition is satisfied.

r■〉When figure r■, α■〈α■ So, α. is conditionally α. become smaller. In addition.

In a normal compressor, the above condition is satisfied and is not a substantial condition.

Next, in the case of Fig. 19 (4), as can be seen from the same figure.

α■kua■+r■kur■ If each of the conditions is satisfied, So, α is conditionally α. become smaller.

■ Next, in the case of Figure 19 (5), as shown in Figure 19 (51).

a■〈a■+　r(1)　=　l■ Each condition is satisfied.

So, α. is α. become smaller.

As explained above, Fig. 19+31. +41 is a conditional clause, and other examples are unconditional as shown in Figure 19 (1)
Each discharge valve becomes easier to open compared to the discharge valve of . In addition, regarding sealability, the present invention can be implemented by appropriately selecting the dimensions of each part within a range that does not impair refrigeration performance.

〔Effect of the invention〕

As explained above, this invention compares the oil film sole contact caused by the contact between the discharge valve and the discharge valve seat with the oil exchange seal contact 11 caused by a discharge valve whose discharge valve seat has the same curvature and is flat. By reducing this, it is possible to prevent opening delays in the opening operation of the discharge valve and to improve the discharge efficiency.

[Brief explanation of drawings]

Fig. 1 is a partial cross-sectional view showing the main parts of a conventional compressor discharge valve device, Fig. 2 is a schematic configuration diagram showing the entire compressor in which the discharge valve device of the present invention is installed, and Fig. A13 is a diagram showing the present invention. FIG. 2 is an enlarged perspective view showing the entire discharge valve device. Figure 4, Figure 1m5 is a cross-sectional view of the main parts showing the first and second embodiments of this invention, Figure 6 is an exploded perspective view of the main parts of the thing shown in Figure 5, Figures 7 and 8. 9 and 10 are cross-sectional views of the main parts of the third and fourth embodiments of the present invention, respectively, and FIGS. Figures 1 and 12 are exploded explanatory views of the main parts of the fifth embodiment of the present invention. Figures 12A and B are cross-sectional views of the main parts and the discharge valve seat of the zero embodiment of the invention. A perspective view of. 13 to 16 respectively show discharge valve seats of seventh to tenth embodiments of the present invention, and FIG. 7 corresponds to FIGS. 12, 14, and 16. No. 6 of this invention
．． 8th. FIG. 18 is a diagram showing the noise characteristics of the tenth embodiment, and FIG.
FIG. 19 is a diagram showing the noise characteristics of the fire example, and FIG. 19 is a graph showing the oil film strength of each example of the invention. In the figure, (1) is the discharge port, (4), (1B), (18
a), (18b), (18c). (18+1), C4H6 is the discharge valve, (17a)・t
2'/), t4'/) is the housing, 09 is the discharge valve holder, C2+, C'2J, +44 is the discharge valve seat + (4
51 is the sea. In Figure 2, the same symbol indicates the same or equivalent EIV. Agent Masu Oiwa) & Figure 1! Fig. 2 Fig. 14 Fig. 5 Fig. 6 Fig. 7 Fig. 8 Fig. 9 Fig. 1- Fig. 11 Fig. 12 Fig. 12 A Fig. 12 B Fig. 13 Fig. 14 Fig. 15 Fig. 16 Fig. ? Figure 17. Great frequency (7-1z)? Figure 19 50 j (J Continued from page 1 0 Inventor Kazuhiro Nakane Oganai, Shizuoka City 0 Inventor Osamu Iwabuchi 3-1 Oshika, Shizuoka City Mitsubishi Electric Co., Ltd. Company Shizuoka Works 3-1 No. 1 Mitsubishi Electric Corporation Shizuoka Works Procedural Amendment (Voluntary) 1. Indication of the case Patent application Shoyu♂-z3oor/32, title of invention Compressor discharge valve device: 34 amended Amended Description 1, Title of Invention: Discharge Valve Device for Compressor 2, Claims (1) Discharge valve that presses dregs compressed in a compression chamber against the discharge valve seat. A discharge valve device for a compressor configured to discharge out of the compression chamber against the pressing force of The discharge valve seat f has a discharge port communicating with the pressure ring chamber, and the cross-sectional shape of the peripheral edge of the discharge side has a curvature. Location Completely equipped with a discharge valve that opens and closes according to the pressure in the compression chamber, oil film seal contact r1]-4 caused by contact between the discharge valve and the discharge valve seat.
A discharge valve device for a compressor, characterized in that the curvature of the discharge valve seat is reduced compared to the oil film produced during seal contact by a flat discharge valve. (2) The contact area between the discharge valve and the discharge valve seat,” 2.111
A discharge valve device for a pressurized material machine as claimed in claim 1, characterized in that the discharge valve seat is positioned outwardly or inwardly from the top of the discharge valve seat. (3) Place the discharge valve in the corner! Claim 1, characterized in that the corner portion is brought into contact with the discharge valve seat.
A discharge valve device for a compressor as described in 1. (4) The entire corner of the discharge valve is formed by concave or convex molding as a 4f characteristic %i! - + Range of requirements Compression-like discharge valve device 1 according to item 3. (51) The corner portion of the discharge valve is constructed of a combination of a discharge valve with perforation and a discharge valve without perforation.All features and scope of claims. (6) The discharge valve makes contact with the discharge valve seat. A discharge valve device for a compressor according to claim 1, wherein the seating portion of the discharge valve is formed of a curved surface having an anisotropic peak.
. (7) A discharge valve arrangement for a compressor according to claim 1, wherein the seating portion of the discharge valve is approximately elliptical. (8) A discharge valve device for a compressor according to claim 1, which is characterized in that the Jffi1 direction of the discharge valve seat is unevenly distributed. (9) Discharge valve The pressurized discharge valve device according to claim 8, characterized in that the seat is provided with one or more grooves. A discharge valve device for a pressurizing machine according to claim 1, characterized in that an extending groove is formed on its surface. A discharge valve device for a compressor according to claim 10. u2 The entire groove of the discharge valve seat is arranged alternately on the inside and outside of the top of the valve seat. Discharge valve device for a pressure h machine according to claim 10. 3. Detailed Description of the Invention [Technical Field of the Invention] This invention relates to a discharge valve device used in a compressor incorporated in a refrigeration cycle. [Prior Art] Figure 1 shows, for example, the main parts of a conventional compressor discharge valve device shown in Japanese Publication No. 57-12909. In the cross-sectional view, (
1) The housing wall (1a) K-formed discharge port, (
2) is a discharge valve seat located at the discharge side periphery of the discharge port (11), which is protrusively molded integrally with the housing W (Ia), and whose cross-sectional shape has a hook-and-hook curvature. .(3) is a discharge valve foot; (4) is a discharge valve made of an elastic material, one end of which is fixed to the housing wall (1a); 3), and opens and closes the discharge port (1) according to the pressure difference in the compression chamber (not shown). Conventional compressor discharge valve devices have one or more discharge valve devices. It is configured as,
For example, the scum compressed by a compressed falcon (not shown) is 79r.
When the discharge pressure reaches a certain level, it is connected to the compression chamber: II! The discharge port (41) that is in tight fluid contact with the discharge valve seat (2) installed on the discharge side of the IJ moves to the open side due to the above discharge pressure, and the discharge valve (4) and the discharge valve 1 made with a(2)
- Dregs under a pressure of 1 s6 is discharged from the gap. Thereafter, the pressure in the compression chamber decreases, and the discharge valve (4) closes (
After 1411K of operation, the discharge valve seat (2) is seated, and the process moves to the compression stroke of the compression chamber. This series of operations is then performed continuously. In order to perform this series of operations smoothly, especially the discharge valve (
4) and the discharge valve seat (2), it is important to prevent the backflow of waste when the discharge valve (4) is in the closed state and the delay in opening when the discharge valve (4) is in the open state. Discharge valve seat (
2), the cross-sectional shape of the discharge valve seat (2) has a hook-shaped curvature, and the curvature surface is also rounded on the outer jacket surface. , the contact part with the discharge valve (4) - type contact, and the diameter of the discharge valve (4) and the discharge valve is made larger than the diameter of the entire discharge port CI which fully accommodates the apex of the discharge valve seat (2). I tried to increase the contact pressure on seat (2). However, in the conventional compressor discharge valve device as described above, when the dregs compressed by the compressor is discharged, the lubricating oil is also discharged together with the gas, so the discharge valve ( 4) and the discharge valve seat (2), the oil film spreads in a band-like manner and exceeds the desired sealing contact width.
As a result, the oil film resistance increases due to the oil film formed by the above-mentioned band-shaped manual force when opening the discharge valve 41, causing a problem in which a delayed opening sound is generated. This has caused the total input to the compressor to increase in conventional devices. Further, when the discharge valve (4) breaks the oil film and moves to the open side, the resistance force of the oil film is large. When the oil slick spreads, it is the cause of all the noise. [Summary of the Invention] This invention solves the problems that the conventional compressor discharge valve device described above had. It was done for the purpose of reshaping. Oil film seal contact caused by contact between discharge valve and discharge valve seat+
iJf, the curvature of the discharge valve seat is equal and reduces the oil film seal contact "1" that occurs with a flat discharge valve, thereby preventing opening vibration during the opening operation of the discharge valve and improving discharge efficiency. This project proposes a single-shift compressor discharge valve system. [Embodiments of the Invention] The compressor discharge valve system f- of the invention C will be described in detail below with reference to one drawing. FIG. 2 is a schematic diagram of a compressed four-twin engine according to an embodiment of the present invention, in which a stator (++2) is housed in a closed container (Qll). The electric motor consisting of the rotor U31 is fully housed, and the compression operation is performed by the crankshaft 04 and cylinder Q5 driven by this electric motor, the piston (llj), and the vane (not shown) that divides the pressure chamber into a cylinder pressure chamber and a low pressure chamber. Side housings (17a) and (17b), which form a compression chamber and also serve as bearings for the crankshaft I, are placed at both ends of the cylinder.Suction pipe (not shown) The refrigerant drawn from the press II'+
In the room! The crankshaft I is run over and driven by an electric motor.
The piston (161 and cylinder a9) rotates eccentrically by
．． When the compressing operation is performed by a vane (not shown) and the pressure in the pressure chamber Q11 becomes slightly higher than the internal pressure of the closed container Q11, the discharge valve α scoop opens and the discharge port is discharged from the discharge muffler from the discharge port provided in the side housing (17a). Dregs flow out into Qv. A discharge valve leg (il) is provided to completely regulate the movement of the discharge valve Q81 at this time.The discharged refrigerant gas, which has been reduced in the discharge muffler, flows into the closed container 01) and is discharged. All of the pipes are routed to the heat exchanger and the refrigeration cycle is completed. FIG. 3 is an enlarged perspective view of a discharge valve device according to an embodiment of the present invention, and the detailed structure of the main parts of the present invention will be described later, so it is omitted. In Fig. 3, the discharge port provided in the side housing (17a) is fixed to the side housing (17a) (4) with the discharge valve θ & and the discharge valve foot α9 using bolts (1), etc. In the following, the discharge valve device of the pressure feeder according to the embodiment of the invention of C will be explained in detail according to the detailed drawings. Fig. 4 is a cross-sectional view of the main part structure showing the entire embodiment of the invention of year 1. (1) is a discharge port molded in the housing (17a). ■ is a nearly circular discharge valve convex. The above discharge port (located at the peripheral edge of the discharge side of +1, Ij1 surface shape has approximately the same curvature Q!J is a discharge valve leg, and (18a) is a discharge valve made of a thin plate that provides elasticity.The corresponding part of the discharge valve seat is partially convexed by pressing etc. The corners of the corners are curved according to the 11th rule from the JU point of the curvature surface of the discharge valve seat.
1. As explained in Figure 1, the operation is almost the same as that of the conventional device, but a compression chamber (not shown) is formed at the contact part with the discharge valve (18a) and the discharge valve seat (c). This seals off refrigerant scum that flows back into the pressure chamber from the high pressure area outside. In addition, the resistance force when the discharge valve (18) shifts to the opening operation depends on the amount of oil film at the contact part between the discharge valve (18a) and the discharge valve seat e2, T, that is, the oil film seal contact period and the oil film thickness. However, by providing a convex portion on the discharge valve (18a), the amount of oil film is completely suppressed by reducing the amount of oil film in the seal, thereby reducing the oil film resistance during the opening operation of the discharge valve (18a). , only a delay in opening occurs.In addition, when the discharge valve (18a) or the oil film formed to prevent backflow moves to the opening operation, a sound is generated. By reducing the oil film resistance, noise can be completely suppressed.Next, the five causes of total sugar according to the second embodiment of the present invention are shown and explained in Fig. 6. Fig. 5 shows the structure rU no. Figure 6 is a schematic assembly diagram of the discharge valve device. In Figures 5 and 6, the discharge valve (28b) has a hole corresponding to the discharge port (11). (281)) and discharge valve seat (
22, the refrigerant gas flowing into the compression chamber from the madder pressure section outside the pressure chamber (not shown) is completely sealed. The discharge valve (28a) is located outside the apex of the curvature cross section of the discharge valve seat (2).
As in the first embodiment, the opening delay of the discharge valve (18b) can be completely prevented, and hfi if
K suppression? Ijll'V can. Naturally, before the gap between the discharge valves (28b) and (28a) opens, the discharge valve (
28b) and the discharge valve seat 03 must be open. This can be easily configured as long as the oil film contact area between the discharge valves (28a) and (28b) is larger than the oil film contact area between the discharge valve (28b) and the discharge valve seat 02. In the first and second embodiments of the invention of C, as described above, a curved portion is provided in the portion corresponding to the discharge valve seat of the discharge valve, and a discharge valve with a different shape of the inclined plate is used. Since the Tsugezo seat is seated on the outside of the apex of the curvature surface of the discharge valve seat, the oil film layer formed between the discharge valve seat and the discharge valve, which is the contact area, is limited.
Since the oil film resistance when the discharge valve shifts to the opening operation is reduced, a delay in opening of the discharge valve can be prevented. Furthermore, since the energy required to suppress the total amount of oil film when the discharge valve operates is reduced, it also has the effect of suppressing the noise generated when the discharge valve breaks down. Next, another embodiment of the present invention will be described with reference to FIGS. 7 and 8. FIG. 1 is a sectional view showing a third embodiment of the present invention, in which (1) is a housing (17a) having a discharge port formed in K. Q4 is a discharge valve seat, which is located at the periphery of the discharge valve 1 of the discharge port (1), and has the same curvature throughout the entire circumference. The oil is discharged by the discharge valve '111' (18 is the discharge valve, and the corresponding part of the discharge valve seat aZ has a partially convex part, and the corner part is inside the J shell point of the curvature surface of the discharge valve seat (111jC seat). The third embodiment of the present invention is constructed as described above, and its operation is almost the same as that of the device of the first practical example explained in Fig. 4. The scum flowing back into the compression chamber from the madder pressure section outside the pressure equalization chamber (not shown) is sealed at the contact portion with the discharge valve (18c) and the discharge valve seat c!z. (The resistance force when the valve 18 shifts to the opening operation is determined by the amount of oil film at the contact area between the discharge valve (180) and the discharge valve seat 0z, that is, the thickness of the oil film at the inner pot where the oil film seal is in contact. However, by providing a convex portion on the discharge valve (18C), the oil film seal width is completely suppressed and the amount of oil film is completely suppressed, and the oil film resistance sound during the opening operation of the discharge valve (18C) is reduced, so the opening delay is reduced. In addition, when the discharge valve (ISC) shifts to opening operation due to the oil film formed to prevent backflow, noise may be generated, or the noise may be reduced due to the reduction in oil film resistance. Furthermore, FIG. 8 is a complete cross-sectional view of the configuration of the embodiment of the fourth embodiment of the invention of C, in which the tip of the discharge valve (18d) is aligned with the curvature cross section of the discharge valve seat 123. It is seated at 1+111'K of the apex, and the discharge valve (1B
The opening delay in a) can be completely prevented and the noise can be completely suppressed. As explained above, in the third and fourth embodiments of the present invention, a curved portion is provided at the corresponding portion of the discharge valve seat (2z) of the discharge valve (180% 18d), and the inner 111
11, the oil film layer formed between the discharge valve seat and the discharge valve, which are the contact parts, is limited. Since the oil film resistance when the discharge valve shifts to the opening operation is reduced, a delay in opening of the discharge valve can be prevented. In addition, this reduces the chance of the oil film layer being completely destroyed when the discharge valves (18C) and (18d) operate. It is also effective in suppressing the noise generated during its destruction. Next, a fifth embodiment of the present invention is shown in FIGS. 9 to 11 and will be described in detail. Figure 9 is a cross-sectional view of the fifth embodiment of the present invention, in which (1) is a discharge port formed in the housing (271). 1 is a discharge valve seat having a protrusion molded integrally with the housing (2 parts), u!1 is a discharge valve foot, (to) is a thin plate-shaped discharge valve, and the apex of the protrusion of the discharge valve seat 03 is The valve seat seating portion (38a), which is seated nearby, has a cross section that is a curved surface with a radius of curvature ρ1.The ilO diagram shows a configuration in which the discharge valve device is cut at a cross section that is 90′ different from that in FIG. In the figure, the cross section of the valve seat seating area (38a) of the thin plate discharge valve ■ is as follows:
The radius of curvature ρ2 is different from ρ1 in all directions. Figure 11 is a perspective view of the discharge valve (c), and shows the valve seat position P'.
3i (38a) forms a curved surface. It is a part of the surface of the ellipsoid (to), and the radius of curvature in the X direction is ρ
1 and the radius of curvature ρ2 in the Y direction is different. The fifth embodiment of the invention is constructed as described above. Its operation is almost the same as that of the device of the first embodiment explained in Fig. 4, and the contact line C31 of the discharge valve (to) with the discharge valve seat has a substantially elliptical shape as shown in Fig. 11. Is the scum flowing back into the compression chamber from the high pressure area outside the compression chamber? It has a sealing property that prevents Moreover, in the opening operation of the discharge valve (2), the annular contact line OI has no substantially elliptical shape, does not exist in the same plane, and is undulating. The contact width for the oil film seal during the opening operation is reduced at the lower part of the discharge valve seat O3, so that there is no delay in opening.Also, the discharge valve (to) seals the oil film formed to prevent backflow. The noise that was generated when the valve breaks and moves to the opening operation is also reduced due to the reduction in oil film resistance.Furthermore, the contact point between the discharge valve (end) and the discharge valve seat C32 has a substantially elliptical annular shape. Therefore, the opening direction of the discharge valve (to) is constant, and the acoustic characteristics of the discharged waste noise are uniform, which has the advantage of reducing fluctuations in the noise level.The fifth embodiment of the present invention has been described above. The seating part of the discharge valve (to) on the discharge valve seat C32 is formed by an anisotropic omnidirectional curved surface, and the entire contact line with the discharge valve seat O3 is an annular line with elliptical undulations. By this,
The contact width for the oil film seal when the discharge valve (to) transitions to the opening operation is reduced at the lower part of the discharge valve seat 3z. This prevents delays in the opening of the discharge valve (to), making the compressor highly efficient. In addition, since the energy that destroys the oil film layer when the discharge valve (to) operates is reduced, it also has the effect of completely suppressing the noise generated when it is destroyed, and the direction in which the discharge valve (to) begins to open is roughly constant. As a result, fluctuations in the noise level become smaller. Next, sixth to tenth embodiments of the present invention are shown in Figs. 12 to 18 and will be described in detail. Figure 12A. B is a cross-sectional view showing an embodiment of the glue 16 of the present invention, as well as a perspective view of the discharge valve seat. (1) is the discharge port formed in the housing (4nK). A discharge valve seat is located at the peripheral edge of the discharge side of the housing i4D and has a cross-sectional shape of approximately the same curvature as integrally formed with the housing i4D. 09 is a discharge valve leg, and (4) is the same as shown in FIG. A flat discharge valve similar to that, 09 is provided on the discharge valve seat 0z,
This is a groove provided so as to intersect with a circumference concentric with the discharge port (1). The sixth embodiment of the present invention is constructed as described above, and its operation is almost the same as the device of the first embodiment described in FIG. The resistance force when the small discharge valve (41) moves to the opening operation is mainly determined by the oil film seal contact and the oil film thickness at the contact part between the discharge valve (4) and the discharge valve seat 02, but the above-mentioned By providing a groove on the discharge valve seat u2 in the circumferential direction concentric with the discharge port (11) and in the vertical direction, the width of the oil film seal can be reduced and the amount of oil film can be suppressed. Since the oil film resistance is completely reduced, it is possible to prevent the opening delay noise of the discharge valve (41) from occurring.Also, since the opening operation of the discharge valve (41) is performed smoothly, the noise caused when the discharge valve (4) is opened is reduced. Furthermore, by providing the above-mentioned grooves @ 9 discharge valves unevenly, the direction in which the discharge valve 141 starts to open is completely constant. However, the depth of the groove 09 of the discharge valve seat 02 should not be too deep for the reason of improving gas sealing performance when the discharge valve (4) is closed. Needless to say. Also, Figures 13 to 16 are the seventh to seventh figures of this invention.
FIG. 13 shows a similar 10th embodiment. FIG. 14 shows the first groove G151 of the present invention arranged approximately radially with respect to all discharge ports of the discharge valve seat. Fig. 15 and Fig. 16 show a ninth example of the present invention in which approximately radial grooves (45) are arranged alternately on the inside and outside of the apex of the discharge valve seat (42+). This is the 10th embodiment.Here, we will explain the improvements in noise characteristics according to the 6th to 10th embodiments of the present invention.
Figure 8 shows the noise of these examples! It shows a comparison between temporality B and conventional noise characteristic A. FIG. 17 shows FIGS. 12 and 14 in which the grooves 09 are provided unevenly. 6. Corresponding to FIG. Silk 8. This is the tenth embodiment, and it can be seen that the noise level and its dispersion are improved compared to the conventional example AVc. Figure 18 shows fk(4
7. Corresponding to Figures 13 and 15, which are not biased.
This is the ninth embodiment, and it can be seen that the noise level is improved compared to the conventional example. As explained above, in the sixth to tenth embodiments of the present invention, a groove (49) is provided in the discharge valve seat (44) so as to intersect with the circumference concentric with the discharge port. In addition, as a result of smoothing the opening operation of this discharge valve (4), it has the effect of reducing noise during the opening operation of the discharge valve.Also, it is possible to make the groove (49) unevenly provided. If vc'1-, the direction in which the discharge valve (4) starts to open is made constant, and the sound effect that suppresses the variation in noise during the discharge valve opening operation is also increased. A brief explanation of the amount of oil film UVc of 4'i4 lubricating oil between the tray discharge valve seat and the discharge valve is shown in Fig. 19. Fig. 19 shows the discharge valve seat side and the discharge valve (51).
Fig. 19 (11 shows a conventional example corresponding to Fig. 1, and Fig. 2 (2) shows a conventional example corresponding to Fig. 4). (3) shows the third embodiment of the invention corresponding to FIG. 1. FIG. 4 (4) shows the fifth embodiment of the invention corresponding to FIG. 11. Embodiment FIG. 5 shows a sixth embodiment of the invention corresponding to FIG. 12.Next, let us consider the ease with which the discharge valve can be opened. α is K as shown in equation (1). The tension ΣF and the differential pressure ΣP are as shown in equations (21 and (3)).
△P: πr 211 (Pa-Pc) -=-(31 However, a: Average oil film radius r: Average oil film radius Next, substituting (2H3+ equation into (11) and rearranging it gives equation (・1). Therefore, the ease of opening α of the discharge valve is proportional to 1%. Here, the ease of opening α of the discharge valve in Figure 19 (11) is The ease of opening of each example shown in ~α■
will be explained below. In addition, the subnumbers ■～■ are shown in the same figure (
1) to (5)K indicate the corresponding values. In the case of Figure 19 (2), it can be seen from Figure 19 (2). Since the conditions 8■<+8■ and ■-relaxation hold, the following trace α■ is smaller than α■. Next, in the case of Figure 19 (3), as can be seen from Figure 19 (3). '@〈2'''(1+・”CL)〈r(il
Each condition is satisfied. r(? 2 '■ When α■〈α■ and t, C, α
■ is conditionally smaller than α■. Note that in a normal pressure machine (9), all of the above conditions are satisfied, so they are not substantial conditions. Next, in the case of jJt19 diagram (4), it can be seen from the same diagram. The following conditions are satisfied: 0■ku8■・1■〈1■. Therefore, α■ becomes smaller than α■ with the conditional clause. Next, in the case of Fig. 19 (5), as can be seen from Fig. 19 (5). Each of the conditions 0■〈a■・r■−r■ is satisfied. Therefore, α■ is smaller than α■. As explained above, Fig. 19+31. i41 is a conditional clause, and other examples are unconditional as shown in Figure 19 (1).
This means that each discharge valve is more likely to become isolated than the other discharge valves. In addition, with regard to sealing performance, this problem can be achieved by appropriately selecting the dimensions of each part within a range that does not impair refrigeration performance. [Effects of the Invention] As explained above, the present invention is effective against oil film seal contact caused by contact between a discharge valve and a discharge valve seat. By reducing the curvature of the discharge valve seat compared to when the oil film seal is in contact with the same and flat discharge valve, opening delay in the opening operation of the discharge valve can be prevented and discharge efficiency can be improved. 4. Brief explanation of the drawings Figure 1 is a partial sectional view showing the main parts of the discharge valve system of a conventional compressor, and Figure 2 shows the entire compressor in which the discharge valve system of the present invention is installed. 3 is an enlarged perspective view showing the entire discharge valve device of the present invention. Fig. 4 and Fig. 5 are cross-sectional views of the first and second embodiments of the present invention. Figure 8 shows the third and fourth parts of this invention.
Figures 9 and 10 are cross-sectional views of the main parts of the fifth embodiment of the present invention. FIGS. 12A and 12B are exploded explanatory diagrams of essential parts for explaining the fifth embodiment.
A cross-sectional view of the main parts and a perspective view of the discharge valve seat showing the embodiment, Part 1
3 to 16 are perspective views showing all discharge valve seats of the first to tenth embodiments of the present invention, and FIG. 1γ is a perspective view of the discharge valve seats of the present invention corresponding to FIGS. 6. 8th
．． Figure 18 is a diagram showing the noise characteristics of the example of the drive 10.
Figure 3. 7. of this invention corresponding to FIG. FIG. 19 is a diagram showing the noise characteristics of the ninth embodiment, and is an explanatory diagram for explaining how to increase the oil exchange strength and full stop light T of each embodiment of the present invention. In the figure, (1) is the discharge port, ! 41. (181, (
18a), (1817,) (18c), (18d)
, (l is the discharge valve, (17a), (27), +
4n&ma housing, eel equipped with discharge valve, (2'a,
θ21. +421 is a discharge valve seat, and 09 is a groove. Note that the same line numbers in Figure 1 are the same or different (1' indicates the minute).
. Agent Masuo Oiwa 211 Figure 5 Figure 6

Claims (9)

[Claims] (1) The gas compressed in the compression chamber is resisted by the pressure force of the discharge valve that presses the discharge valve seat and by the adhesive force of the oil film seal of the lubricating oil attached near the contact area between the discharge valve seat and the discharge valve. A discharge valve device for a compressor configured to discharge air to the outside of a compression chamber includes a discharge valve seat having a discharge port communicating with the compression chamber and having a curvature in cross-section at a peripheral edge of the discharge side; Completely equipped with a discharge valve that is pressed into contact with a part of the valve seat and opens and closes the discharge port according to the pressure in the compression chamber.・During contact with an oil film seal caused by contact between the discharge valve and the discharge valve seat. A discharge valve device for a compressor, characterized in that the curvature of the discharge valve seat is equal and reduced by sinking during oil film seal contact caused by a flat discharge valve. (2) The discharge valve device for a compressor according to claim 1, wherein the contact position between the discharge valve and the discharge valve seat is located outside or inside the top of the discharge valve seat. . (3) The discharge valve device for a compressor according to claim 1, wherein the discharge valve has a corner and is brought into contact with the discharge valve seat at the corner. (4) The discharge valve device for a compressor according to claim 3, wherein the corner portions of the discharge valve are formed by concave or curved molding. (5) A discharge valve device for a compressor according to claim 3, wherein the corner portion of the discharge valve is constructed by a combination of a discharge valve having perforations and a discharge valve without perforations. (6) The discharge valve device for a compressor according to claim 1, wherein the seating portion of the discharge valve where the discharge valve contacts the discharge valve seat is constituted by a curved surface having anisotropy. (7) The discharge valve device for a compressor according to claim 1, wherein the seating portion of the discharge valve is approximately elliptical and has scales. (8) A discharge valve device for a compressor according to claim 1, wherein the height of the discharge valve seat in the circumferential direction is made non-uniform. (9) A discharge valve device for a compressor according to claim 8, characterized in that one or more grooves are provided in the discharge valve seat. A discharge valve device for a compressor according to claim 1, wherein the discharge valve seat has a groove on its surface that extends substantially radially with respect to the discharge port. (Ill) A discharge valve device for a compressor according to claim 10, characterized in that the grooves of the discharge valve seat are arranged asymmetrically. Claim 1 characterized in that the
A discharge valve device for a compressor according to item 0.