JPH0513993Y2 - - Google Patents

Description

[Detailed Description of the Invention] Purpose of the Invention (Field of Industrial Application) The present invention relates to a discharge valve structure for a compressor used primarily for vehicle air conditioning.

(Prior Art) Conventionally, in a swash plate compressor, a discharge port is provided through a partition wall between a cylinder block and a discharge chamber, and the discharge port is opened and closed on the discharge chamber side of the partition wall, as shown in FIG. A discharge valve 32 having a constricted shape with a narrow base is provided. The discharge valve 32 is formed to protrude radially from the annular discharge valve plate 31.

Generally, in the manufacturing process of the discharge valve 32, burrs, droop,
In order to remove burrs, etc. or grind, the punched out discharge valve 32 is placed in a processing tank together with a polishing agent such as a polishing aid and silica sand, and rotated, and the gap between the discharge valve 32 and the abrasive is Barrel machining is used to perform surface machining using the relative movement of.

(Problem to be solved by the invention) However, when performing the barrel processing, a plurality of discharge valves 32 are installed in the processing tank, and the tips 32 of the discharge valves 32 are
Since the tip portions 32b are arranged so as to partially overlap, the tip portions 32b are likely to become entangled with each other during processing and may be damaged. When this discharge valve 32 is installed in a swash plate type compressor, since the base part has a narrow constricted shape, the bending performance of the discharge valve 32 is good and the discharge port can be opened and closed effectively. As the discharge port is repeatedly opened and closed, stress may be concentrated on the scratches on the tip 32b, leading to breakage.

Moreover, when the discharge valve 32 is subjected to the barrel processing,
The barrel is not applied uniformly over the entire discharge valve 32, and more of the abrasive collides with the tip portion 32b than the root portion 32a, which tends to cause more barrels to form.For example, the edge of the root portion 32a If the barrel is applied by an appropriate amount so that the end portion becomes a curved surface (see FIG. 5), the peripheral edge of the tip portion 32b will be too barreled and become sharp (see FIG. 6).

By the way, in the swash plate compressor, the discharge valve 3
2 opens the discharge port, a large bending stress is applied to the root portion 32a, so if the barrel is not sufficiently applied to the root portion 32a, there is a risk of breakage. On the other hand, if the barrel is sufficiently applied to the base portion 32a,
As described above, the barrel ends up hanging too much on the tip end 32b. If a discharge valve 32 with a sharp tip 32b due to excessive barrel tension is installed in a swash plate compressor, the discharge valve 32 will repeatedly open and close the discharge port, and as a result, the discharge valve 32 will suffer a large impact when closing the discharge port. There is a problem in that the force causes cracks at the periphery of the tip portion 32b.

Structure of the invention (Means for solving the problem) Therefore, in order to solve the above problem, the present invention provides a discharge port through the partition wall between the cylinder block and the discharge chamber, and a discharge port on the discharge chamber side of the partition wall. In the discharge valve structure of a compressor that is provided with a discharge valve that opens and closes the discharge port, the base of the discharge valve has a constricted shape that is narrower than the tip, and a guide portion that surrounds the discharge valve and the periphery thereof at a distance is provided. A technical measure is adopted in which the distance between the outer edge of the portion that closes the discharge port of the discharge valve and the inner edge of the guide portion is narrower than the distance between the outer edge of the root portion of the discharge valve and the inner edge of the guide portion. did.

(Function) A guide part is integrally formed around the discharge valve whose base is narrowly constricted and surrounds the discharge valve at intervals, so when barrel processing is applied to this discharge valve, the guide part allows the discharge valves to be separated from each other. Entanglement is prevented and the occurrence of scratches is suppressed.

Further, during barrel processing, the amount of abrasive that collides with the discharge valve is regulated by the guide portion. The distance between the outer edge of the portion of the discharge valve that closes the discharge port and the inner edge of the guide portion is narrower than the distance between the outer edge of the root portion of the discharge valve and the inner edge of the guide portion. Barrel engagement at the closing part is suppressed, and the barrel is applied to almost the same extent at all parts of the discharge valve.As a result, the barrel does not apply more to the tip than the root of the discharge valve, and the While maintaining the conventional advantage of good bending performance, there is no risk of the peripheral edge of the tip becoming sharp.

(Example) Hereinafter, an example in which the present invention is embodied in a discharge valve structure of a swash plate compressor will be described with reference to FIGS. 1 and 2.

As shown in FIG. 2, both ends of the cylinder blocks 1, 2, which are disposed opposite each other in the front and rear, are closed by front and rear housings 5, 6 via front and rear valve plates 3, 4 as partition walls. A swash plate chamber 9 is formed at the joint between the cylinder blocks 1 and 2, and a swash plate 7 fixed to a drive shaft 10 passing through the center of the cylinder blocks 1 and 2 is accommodated therein.

Five pairs (only one pair is shown) of cylinder bores 8 are bored in the cylinder blocks 1 and 2 parallel to the drive shaft 10 and at radial positions centered on the drive shaft 10, and each cylinder bore 8 has a double-ended cylinder bore 8. A piston 11 is inserted. Each piston 11 is anchored to the swash plate 7 via a hemispherical shoe 12 serving as a bearing device, and is capable of reciprocating movement within the cylinder bore 8 by the rotational force of the swash plate 7.

Suction chambers 13 and 14 are formed on the outer circumferential sides of the front and rear housings 5 and 6, respectively, and a discharge chamber 1 is formed on the center side.
5 and 16 are formed.

In addition, the front and rear valve plates 3, 4 have suction ports 17, 18 for sucking refrigerant gas from the suction chambers 13, 14 to each cylinder bore 8, respectively, and compressed refrigerant from each cylinder bore 8 to discharge chambers 15, 16. Discharge ports 19 and 20 for discharging gas are transparently provided.

Suction valve plates 21 and 22 made of an elastic material are interposed between the front and rear valve plates 3 and 4 and the cylinder blocks 1 and 2, respectively.
Suction valves 21a and 21a, 21a and 22 for opening and closing the suction ports 17 and 18 are provided at positions corresponding to the suction ports 17 and 18 of 22, respectively.
2a is formed.

Housing 5 of front and rear valve plates 3, 4,
On the 6 side, there is an annular discharge valve plate 23 made of an elastic material.
24 and retainer plates 25 and 26 are fixed with bolts 27. As shown in FIG. 1, the discharge ports 19, 20 are arranged in positions corresponding to the respective discharge ports 19, 20 of the discharge valve plates 23, 24 in the form of approximately ladles having approximately circular tips and narrowly constricted bases. Shape-shaped discharge valves 23a, 24a are punched out in a radial manner, and guide portions 2 surrounding the discharge valves 23a, 24a are formed at predetermined intervals around the discharge valves 23a, 24a.
3b and 24b are configured.

Discharge ports 19, 20 of the discharge valves 23a, 24a
The outer edge of the distal end portion that closes the guide portions 23b, 24
The distance C between the inner edges of the guide portions 23b and 24b is smaller than the distance D between the outer edges of the root portions of the discharge valves 23a and 24a and the inner edges of the guide portions 23b and 24b.

Next, the operation and effects of this embodiment configured as above will be explained.

First, when the swash plate 7 is rotated by the rotation of the drive shaft 10, the piston 11 is reciprocated in the left and right directions in FIG. 2 within the cylinder bore 8, and suction, compression, and discharge are performed. In the suction and compression processes, the discharge valves 23a and 24a close the discharge ports 19 and 20, and in the discharge process, the parts of the discharge valves 23a and 24a that are opposite to the discharge ports 19 and 20 receive discharge pressure and close the discharge ports 19 and 20. Open exits 19 and 20.

By the way, in the manufacturing process of the discharge valves 23a, 24a, after the discharge valves 23a, 24a are punched out of an elastic material, burrs, burrs, etc. caused by the punching are removed or ground. Perform barrel processing. In this embodiment, guide portions 23b and 24b are integrally formed around the discharge valves 23a and 24a of the discharge valve plates 23 and 24 to surround the discharge valves 23a and 24a at a predetermined interval. In addition, the guide portions 23b and 24b prevent the discharge valves 23a and 24a from becoming entangled with each other. Therefore, unlike the conventional case, damage caused by the entanglement of the discharge valves does not occur, so the discharge valves 23a, 23a,
24a to the swash plate compressor and discharge ports 19, 2.
Even if the opening and closing of 0 is repeated, the same discharge valves 23a, 24a
There is no local concentration of stress on the material, and there is no risk of breakage.

In addition, in the same barrel processing, the discharge valve 23a,
The amount of abrasive that collides with the guide portion 23b,
24b. Then, the discharge valve 2
The distance C between the outer edge of the distal end portion of the discharge valves 23a, 24a that closes the discharge ports 19, 20 and the inner edge of the guide portions 23b, 24b is equal to the distance C between the outer edge of the root portion of the discharge valves 23a, 24a and the inner edge of the guide portions 23b, 24b. Since the spacing D is narrower than the distance D, the barrels are prevented from being engaged at the portions that close the discharge ports 19 and 20, and the barrels are engaged to approximately the same extent at all locations of the discharge valves 23a and 24a. Therefore, the barrel does not cover the distal end of the discharge valve more than the root of the discharge valve, unlike in the past, and there is no risk that only the peripheral edge of the distal end becomes sharp.

Therefore, the discharge valve plate 2 formed in this way
3 and 24 to the swash plate compressor, and discharge port 1.
When opening and closing of ports 9 and 20 are repeated, the discharge ports 19 and 2
Even if a large impact force is applied when the valve is closed, cracks are less likely to occur on the periphery of the tip, unlike in the conventional discharge valve 32 where the periphery of the tip 32b is sharp. In this way, the discharge valves 23a and 24a of this embodiment maintain the advantage of the conventional discharge valve 32 of good valve bending performance while eliminating the conventional disadvantages.

It should be noted that the present invention is not limited to the configuration of the above-mentioned embodiments, but can be embodied and implemented, for example, as follows.

(1) In the discharge valves 23a and 24a, the distance C between at least part of the outer edge of the portion that blocks the discharge port and the inner edge of the guide portion is narrower than the distance D between the outer edge of the root portion and the inner edge of the guide portion. For example, as shown in FIG. 3, the side edges of the discharge valves 23a, 24a and the guide portions 23b, 2
The distance C between the inner edge of 4b and the inner edge may be narrow.

(2) The present invention can be embodied as a discharge valve structure for various compressors having a discharge valve, such as a swash plate compressor, a swinging inclined plate compressor, and a vane compressor.

Effects of the Invention As detailed above, the present invention prevents the discharge valve from being damaged or its tip becoming sharp when processing the barrel of the discharge valve, thereby preventing the discharge valve from cracking during compressor operation. The valve is less likely to break, has good bending performance, and has the excellent effect of improving the reliability of the discharge valve.

[Brief explanation of drawings]

1 and 2 show an embodiment of the present invention, in which FIG. 1 is a front view of the discharge valve and guide section, FIG. 2 is a vertical sectional view of the central part of the swash plate compressor, and FIG. The figure is a partial front view showing another example of the discharge valve and the guide part, Figures 4 to 6 show the conventional example, Figure 4 is a front view of the discharge valve, and Figure 5 is a view taken in the direction A-A in Figure 4. 6 is an enlarged longitudinal sectional view taken along the line B--B in FIG. 5. 1, 2... cylinder block, 15, 16...
Discharge chamber, 19, 20...discharge port, 23a, 24a
...Discharge valve, 23b, 24b...Guide part, C,
D... Interval.

Claims (1)

[Scope of utility model registration request] In a compressor discharge valve structure in which a discharge port is provided through a partition wall between a cylinder block and a discharge chamber, and a discharge valve for opening and closing the discharge port is provided on the discharge chamber side of the partition wall, the base of the discharge valve is opened from the tip. The discharge valve has a narrow constricted shape, and the discharge valve and a guide part surrounding the circumference at a distance are integrally formed, and the distance between the outer edge of the part that closes the discharge port of the discharge valve and the inner edge of the guide part is set to the discharge valve. The discharge valve structure of the compressor is narrower than the distance between the outer edge of the root part and the inner edge of the guide part.