JP2000018160A - Reciprocating compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrain leakage of high pressure gas by preventing deformation of the valve seat or the like so as to improve freezing capability and durability. SOLUTION: Discharge holes 29b, 30b of stopper plates 29, 30 are disposed in generally opposite positions of an anti-intake valve side outer edge portion E1 and a tip outer edge portion E2 of discharge valves 27a, 28a. Therefore, a contact area of a partition portion S between the discharge valves 27a, 28a and intake valves 27d, 28d and the stopper plates 29, 30 is not decreased by the discharge holes 29b, 30b, thereby seat performance is improved. As a result, when pressure difference is generated between the discharge chamber and the compression chamber, valve seats 27, 28 and the valve plates 29, 30 get less likely to be deformed to the side of the compression chamber. Accordingly, amount of the high pressure gas which leaks from the discharge chamber to the intake chamber and the compression chamber is reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating compressor such as a swash plate compressor, a oscillating plate compressor, and a row compressor (crank compressor).

[0002]

2. Description of the Related Art A conventional reciprocating compressor is disclosed in
There is a swash plate type compressor described in Japanese Patent No. 563.

[0003] This swash plate type compressor is fixed to a cylinder block having a plurality of compression chambers and a cylinder block.
A cylinder head having a discharge chamber and a suction chamber;
A valve plate separating the suction chamber and the compression chamber, a plurality of discharge ports for discharging the refrigerant gas in the compression chamber to the discharge chamber, and a plurality of suction ports for sucking the refrigerant gas in the suction chamber into the compression chamber; A plurality of discharge valves for opening and closing the discharge port,
A plurality of suction valves for opening and closing the suction port and a plurality of stoppers for suppressing the opening amount of the discharge valve are provided.

The plurality of discharge valves and the plurality of suction valves are cut into a single valve sheet in a tongue shape. The discharge valve and the suction valve are adjacent to each other.

[0005] The plurality of stoppers are formed on a single stopper plate disposed between the valve seat and the cylinder head.

The stopper plate has a suction port and a discharge hole for allowing the refrigerant discharged from the discharge port to escape.

[0007] A discharge port and a suction valve escape hole are formed in the valve plate.

As described above, one valve seat having a plurality of discharge valves and a plurality of suction valves is used, and one stopper plate having a plurality of stoppers is used. Therefore, the number of parts is reduced. Moreover, the assembling can be performed simply by sequentially stacking the valve plate, the valve seat, and the stopper plate on the cylinder block, and the assembling property is greatly improved.

[0009]

FIG. 7 is an enlarged plan view showing a part of a stopper plate of a conventional reciprocating compressor.

The discharge valve and the suction valve 127b are formed on the same valve seat, and the discharge valve and the suction valve 127b are adjacent to each other (however, since the discharge valve and the stopper 129a have substantially the same shape, FIG. The discharge valve is hidden under the stopper 129a and cannot be seen).

In the figure, the hatched portions indicate the discharge valve and the suction valve 127b.
Is a partition portion S. A discharge hole 129b for allowing the refrigerant discharged from the discharge port to escape is formed so as to surround the discharge valve. As shown in FIG.
b and the partition S are partially overlapped.

As described above, the discharge hole 129b and the partition S
Are superimposed, for example, during a suction stroke, when a pressure difference between the discharge chamber and the compression chamber 111 occurs, the valve seat, the valve plate, and the like easily deform to sink into the compression chamber 111, The high-pressure gas in the discharge chamber may leak to the compression chamber 111 or the suction chamber.

When the amount of leakage of the high-pressure gas increases, the flow rate of the refrigerant decreases, the refrigerating capacity decreases, the discharge temperature increases, and there arises a problem that the oil deteriorates and the durability decreases.

The present invention has been made in view of such circumstances, and an object thereof is to prevent deformation of a valve sheet and the like, suppress leakage of high-pressure gas, and improve refrigeration capacity and durability. An object of the present invention is to provide a reciprocating compressor.

[0015]

According to a first aspect of the present invention, there is provided a reciprocating compressor comprising: a cylinder block having a plurality of compression chambers; and a high-pressure chamber and a low-pressure chamber fixed to the cylinder block. A plurality of discharge ports for discharging the refrigerant gas in the compression chamber to the high-pressure chamber, a plurality of suction ports for sucking the refrigerant gas in the low-pressure chamber into the compression chamber, and a valve. A plurality of discharge valves formed in a tongue shape on a seat to open and close the discharge port, and a plurality of discharge valves formed in a tongue shape on the valve seat or another valve seat to open and close the suction port adjacent to the discharge valve. A plurality of suction valves, a plurality of stoppers formed on a stopper plate for suppressing the opening of the discharge valve, and a refrigerant gas discharged from the discharge port formed on the stopper plate to the high-pressure chamber; In reciprocating compressors and a gas discharge hole, the discharge hole is characterized in that it substantially opposite the anti-suction valve side outer edge of the discharge valve.

As described above, the discharge hole is located substantially opposite to the outer edge of the discharge valve on the side opposite to the suction valve, and the contact area between the partition between the discharge valve and the suction valve and the stopper plate is reduced by the discharge hole. Therefore, the seating property between the stopper plate and the partition between the discharge valve and the suction valve is improved. As a result, when a pressure difference occurs between the high-pressure chamber and the compression chamber, the valve seat, the valve plate, and the like hardly deform toward the compression chamber, and the amount of high-pressure gas leaking from the high-pressure chamber into the low-pressure chamber or the compression chamber is reduced.

According to a second aspect of the present invention, there is provided a reciprocating compressor comprising: a cylinder block having a plurality of compression chambers; a cylinder head fixed to the cylinder block and having a high pressure chamber and a low pressure chamber; A plurality of discharge ports for discharging the high-pressure chamber into the high-pressure chamber, a plurality of suction ports for suctioning the refrigerant gas from the low-pressure chamber into the compression chamber, and a discharge port formed in a tongue shape on a valve seat. A plurality of discharge valves that open and close, and a plurality of suction valves that are formed in a tongue shape on the valve seat or another valve seat and that open and close the suction port adjacent to the discharge valve, and that are formed on a stopper plate; A reciprocating compressor comprising: a plurality of stoppers for suppressing an opening amount of a discharge valve; and a discharge hole formed on the stopper plate, for discharging refrigerant gas discharged from the discharge port to the high-pressure chamber. Oite, the discharge hole is characterized in that it substantially opposite the tip edge portion of the discharge valve.

As described above, the discharge hole is located at a position substantially opposite to the outer edge of the distal end of the discharge valve, and the contact area between the partition between the discharge valve and the suction valve and the stopper plate is increased, thereby improving the sheetability. As a result, when a pressure difference occurs between the high-pressure chamber and the compression chamber, the valve seat, the valve plate, and the like hardly deform toward the compression chamber, and the amount of high-pressure gas leaking from the high-pressure chamber into the low-pressure chamber or the compression chamber is reduced.

According to a third aspect of the present invention, there is provided a reciprocating compressor comprising: a cylinder block having a plurality of compression chambers; a cylinder head fixed to the cylinder block and having a high pressure chamber and a low pressure chamber; A plurality of discharge ports for discharging the high-pressure chamber into the high-pressure chamber, a plurality of suction ports for suctioning the refrigerant gas from the low-pressure chamber into the compression chamber, and a discharge port formed in a tongue shape on a valve seat. A plurality of discharge valves that open and close, and a plurality of suction valves that are formed in a tongue shape on the valve seat or another valve seat and that open and close the suction port adjacent to the discharge valve, and that are formed on a stopper plate; A plurality of stoppers for suppressing the opening amount of the discharge valve,
In the reciprocating compressor formed in the stopper plate and having a discharge hole for allowing the refrigerant discharged from the discharge port to escape to the high-pressure chamber, the discharge hole has an outer edge of the discharge valve opposite to the suction valve. It is characterized by being substantially opposed to the outer edge of the tip.

As described above, the discharge hole is located at a position substantially opposite to the outer edge of the discharge valve on the side opposite to the suction valve and the outer edge of the distal end, and the contact area between the partition between the discharge valve and the suction valve and the stopper plate increases. Sheet properties are improved. As a result, when a pressure difference occurs between the high-pressure chamber and the compression chamber, the valve seat, the valve plate, and the like hardly deform toward the compression chamber, and the amount of high-pressure gas leaking from the high-pressure chamber into the low-pressure chamber or the compression chamber is reduced.

[0021]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 2 is a longitudinal sectional view showing the entire swash plate type compressor according to one embodiment of the present invention.

The front cylinder block 1 and the rear cylinder block 2 are joined to each other via an O-ring 38. Joined cylinder block 1,
A front head (cylinder head) 4 is fixed to one end of the valve 2 via a valve plate 3, a valve seat 27 and a stopper plate 29, and a rear head (a cylinder head) to the other end via a valve plate 5, a valve seat 28 and a stopper plate 30. The cylinder head 6 is fixed.

A drive shaft 7 is disposed at the center of the cylinder blocks 1 and 2, and a swash plate 8 is fixed to the drive shaft 7. The drive shaft 7 and the swash plate 8 are rotatably supported by bearings 9 and 10. The swash plate 8 is accommodated in a swash plate chamber 37 formed in the cylinder blocks 1 and 2.

The cylinder blocks 1 and 2 are provided with a plurality of cylinder bores 11. The cylinder bores 11 are parallel to the drive shaft 7 and are arranged at predetermined intervals in a circumferential direction around the drive shaft 7. Each cylinder bore 11
A piston 12 is slidably accommodated therein. Compression chambers 21 and 22 are formed in each cylinder bore 11 on both sides of the piston 12. The piston 12 is connected to the swash plate 8 through substantially hemispherical shoes 19 and 20,
The piston 12 rotates as the swash plate 8 rotates.
Reciprocate inside.

FIG. 1 is an exploded perspective view showing a valve plate, a valve seat, and a stopper plate. FIG. 3 is a plan view of the valve plate, the valve seat, and the stopper plate when they are overlapped. FIG. Enlarged plan view,
FIG. 5 is a sectional view taken along the line VV in FIG. 3, and FIG.
It is sectional drawing which follows the VI line.

The substantially disk-shaped valve plates 3 and 5 include:
Discharge ports 3a and 5a for discharging the refrigerant gas from the compression chambers 21 and 22 to the discharge chamber (high-pressure chamber) 24, and a suction valve escape hole 3 for allowing the suction valves 27d and 28d to escape to the compression chamber during suction.
b, 5b and bolt through holes 3c, 5c, respectively.

Tongue-shaped discharge valves 27a, 28a and tongue-shaped suction valves 27d, 28d are formed in the substantially disk-shaped valve seats 27, 28, respectively, and bolt through holes 27c, 28c are formed. Is provided. Discharge valve 2
The suction valves 7a and 28a and the suction valves 27d and 28d are adjacent to each other via a partition portion S as shown in FIGS. The discharge valves 27a and 28a are located radially inward of the suction valves 27d and 28d.

A substantially disk-shaped stopper plate 29, 30
Are provided with stoppers 29 corresponding to the discharge valves 27a and 28a.
a and 30a are formed, and suction ports 29d and 30d for sucking the refrigerant gas in the suction chamber (low-pressure chamber) 23 into the compression chambers 21 and 22 are formed. Furthermore,
Discharge valves 27a, 28 are provided on stopper plates 29, 30.
Substantially L-shaped discharge holes (holes) 29b, 30b substantially facing the outer edge E1 on the side opposite to the suction valve and the outer edge E2 at the front end are formed. Therefore, the contact areas between the partition portions S of the valve seats 27 and 28 and the stopper plates 29 and 30 are not cut by the discharge holes 29b and 30b.

The stoppers 29a and 30a protrude toward the discharge chamber 24 at a predetermined angle or an arbitrary curvature with respect to the discharge valves 27a and 28a in the closed state (see FIG. 5).
a, 28a, the amount of opening or deformation is suppressed.

The stopper plates 29 and 30 are provided in the compression chamber 2
The deformation caused by the compression pressures of the suction chamber 2 and the suction chamber 2
3 has a thickness (rigidity) that does not allow communication with the third member, that is, a thickness (rigidity) sufficient to receive a compressive pressure. In this way, instead of providing the stopper plates 29 and 30 with the same rigidity as that of the conventional valve plate that can receive the compressive pressure, the thickness of the valve plates 3 and 5 is reduced.
It was smaller than the thickness of 9,30.

As shown in FIG. 5, the discharge ports 3a, 5a
The discharge valves 27a and 28a are disposed to face each other.
When a and 28a are opened, the compression chambers 21 and 22 communicate with the discharge chamber 24 via the discharge ports 3a and 5a of the valve plates 3 and 5 and the discharge holes 29b and 30b of the stopper plates 29 and 30.

Also, as shown in FIG.
d, 30d and suction valves 27d, 28d face each other, and when the suction valves 27d, 28d open, the stopper plates 29,
30 through the suction ports 29d, 30d and the suction valve relief holes 3b, 5b in the valve plates 3, 5.
The suction chamber 23 communicates with the suction chambers 1 and 22.

Next, the operation of the swash plate type compressor of this embodiment will be described.

When the drive shaft 7 rotates, the swash plate 8 also rotates integrally. The rotation of the swash plate 8 causes the piston 12 to reciprocate in the cylinder bore 11. When the swash plate 8 rotates by １ ／, when the piston 12 is located closest to the valve plate 3 (left side in FIG. 2) (when the piston 12 is located at the top dead center on the compression chamber 21 side), the piston 12 moves to the position shown in FIG. 2 (right side in FIG. 2), the suction stroke is completed on the compression chamber 21 side, and the compression stroke is completed on the compression chamber 22 side. When the swash plate 8 further rotates by か ら from this state, the suction stroke is completed on the compression chamber 22 side, and the compression stroke is completed on the compression chamber 21 side.

In the suction stroke, the suction valves 27d and 28d are elastically deformed toward the suction valve relief holes 3b and 5b, and
9d and 30d are opened, and low-pressure refrigerant gas flows from the suction chamber 23 to the compression chambers 21 and 22 through the suction ports 29d and 30d and the suction valve relief holes 3b and 5b.

In the compression stroke, the discharge valves 27a and 28a are elastically deformed toward the discharge chamber 24 by the refrigerant gas compressed in the compression chambers 21 and 22, and are compressed through the discharge ports 3a and 5a and the discharge holes 29b and 30b. High-pressure refrigerant gas is discharged from the discharge chambers 21 and 22 to the discharge chamber 24. At this time, the entirety of the discharge valves 27a, 28a comes into contact with the stoppers 29a, 30a, and the opening or deformation of the discharge valves 27a, 28a is suppressed.

According to the swash plate type compressor of this embodiment, as described above, the discharge holes 29b, 30b are formed in the discharge valves 27a, 2b.
8a is located substantially opposite to the outer edge E1 on the side opposite to the suction valve and the outer edge E2 at the front end, and the discharge valves 27a and 28a and the suction valve 2
Partition S between 7d and 28d and stopper plate 27
Since the contact area between the contact holes d and 28d is not reduced by the discharge holes 29b and 30b, the sheet property is improved. As a result, for example, when a pressure difference occurs between the discharge chamber 24 and the compression chambers 21 and 22 in the suction stroke, the valve seats 27 and 28 and the valve plates 3 and 5 become less likely to deform toward the compression chambers 21 and 22. The amount of high-pressure gas leaking from the discharge chamber 24 into the suction chamber 23 and the compression chambers 21 and 22 is reduced.

In the above embodiment, the ejection holes 29
b and 30b have been described as being formed at positions substantially opposite to the outer edge E1 and the outer edge E2 of the discharge valves 27a and 28a on the side opposite to the suction valve. Outer edge E of the discharge valves 27a and 28a on the side opposite to the suction valve
2 or at a position substantially opposed to the outer edge portion E2 of the tip (not shown).

In the above embodiment, the discharge valve 27
Although the description has been given of the case where the valve seats 27 and 28 having both the suction valves 27a and 28d and the suction valves 27d and 28d are used. May be used. In this case, the valve plates 3 and 5 can be omitted.

According to these modifications, the same effects as those of the above embodiment can be obtained.

Although the swash plate compressor is used as the reciprocating compressor in each of the above embodiments, the application of the present invention is not limited to this case. It can be applied to various reciprocating compressors such as a row compressor (crank compressor).

[0043]

As described above, the first, second or third aspect of the present invention is described.
According to the reciprocating compressor of the invention, the contact area between the partition between the discharge valve and the suction valve and the stopper plate is not reduced by the discharge hole, and the sheet properties are improved. When a pressure difference occurs, the valve seat, the valve plate, and the like are less likely to deform toward the compression chamber, and the amount of high-pressure gas leaking from the high-pressure chamber into the low-pressure chamber or the compression chamber can be reduced. As a result, it is possible to prevent a decrease in the refrigerant flow rate by suppressing a decrease in the refrigerant flow rate, and to prevent an increase in the discharge temperature, thereby preventing oil deterioration and, consequently, durability.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view showing a valve plate, a valve seat, and a stopper plate.

FIG. 2 is a longitudinal sectional view showing the entire swash plate type compressor according to one embodiment of the present invention.

FIG. 3 is a plan view when a valve plate, a valve seat, and a stopper plate are stacked.

FIG. 4 is an enlarged plan view showing a part of a stopper plate.

FIG. 5 is a sectional view taken along line VV of FIG. 3;

FIG. 6 is a sectional view taken along the line VI-VI of FIG. 3;

FIG. 7 is an enlarged plan view showing a part of a stopper plate of the conventional reciprocating compressor.

[Explanation of symbols]

 1, 2 cylinder block 3, 5 valve plate 3a, 5a discharge port 4 front head 6 rear head 24 discharge chamber 23 suction chamber 27, 28 valve seat 27a, 28a discharge valve 27d, 28d suction valve 29, 30 stopper plate 29a, 30a stopper 29b, 30b Discharge holes 29d, 30d Suction port E1 Outer edge of the discharge valve on the side opposite to the suction valve E2 Outer edge of the discharge valve S Partition part

 ──────────────────────────────────────────────────の Continuing from the front page (72) Inventor Ichi Tabata 39, Higashihara, Chiyo-ji, Odai-gun, Osato-gun, Saitama Prefecture Inside of Xexel Gangnam Plant (72) Katsuhiko Arai, Katsuhiro Arai 39, Chiyo-Higashi, Chiyo, Konan-cho, Osato-gun, Saitama Address F-term in Zexel Gangnam Plant (reference) 3H003 AA03 AB07 AC03 AD01 CC02 CC11 CC12 3H076 AA06 BB22 BB26 CC07 CC20 CC43 CC94 CC95

Claims (3)

[Claims] 1. A cylinder block having a plurality of compression chambers, a cylinder head fixed to the cylinder block and having a high pressure chamber and a low pressure chamber, and a plurality of cylinder heads for discharging refrigerant gas in the compression chamber to the high pressure chamber. A plurality of suction ports for sucking the refrigerant gas from the low-pressure chamber into the compression chamber; a plurality of discharge valves formed in a tongue shape on a valve seat to open and close the discharge port; A plurality of suction valves formed in a tongue-like shape on a seat or another valve seat to open and close the suction port adjacent to the discharge valve; and a plurality of suction valves formed on a stopper plate for suppressing an opening amount of the discharge valve. A reciprocating compressor having a stopper, and a discharge hole formed in the stopper plate, for discharging refrigerant gas discharged from the discharge port to the high-pressure chamber, wherein the discharge hole is provided Reciprocating compressor which is characterized in that substantially opposite the anti-suction valve side outer edge of the discharge valve. 2. A cylinder block having a plurality of compression chambers, a cylinder head fixed to the cylinder block and having a high pressure chamber and a low pressure chamber, and a plurality of cylinder heads for discharging refrigerant gas in the compression chamber to the high pressure chamber. A plurality of suction ports for sucking the refrigerant gas from the low-pressure chamber into the compression chamber; a plurality of discharge valves formed in a tongue shape on a valve seat to open and close the discharge port; A plurality of suction valves formed in a tongue-like shape on a seat or another valve seat to open and close the suction port adjacent to the discharge valve; and a plurality of suction valves formed on a stopper plate for suppressing an opening amount of the discharge valve. A reciprocating compressor having a stopper, and a discharge hole formed in the stopper plate, for discharging refrigerant gas discharged from the discharge port to the high-pressure chamber, wherein the discharge hole is provided Reciprocating compressor which is characterized in that substantially opposite the tip edge portion of the discharge valve. 3. A cylinder block having a plurality of compression chambers, a cylinder head fixed to the cylinder block and having a high pressure chamber and a low pressure chamber, and a plurality of cylinder heads for discharging refrigerant gas in the compression chamber to the high pressure chamber. A plurality of suction ports for sucking the refrigerant gas from the low-pressure chamber into the compression chamber; a plurality of discharge valves formed in a tongue shape on a valve seat to open and close the discharge port; A plurality of suction valves formed in a tongue-like shape on a seat or another valve seat to open and close the suction port adjacent to the discharge valve; and a plurality of suction valves formed on a stopper plate for suppressing an opening amount of the discharge valve. A reciprocating compressor, comprising: a stopper; and a discharge hole formed in the stopper plate and allowing a refrigerant discharged from the discharge port to escape to the high-pressure chamber. Reciprocating compressor, characterized in that it substantially opposite to the anti-suction valve side outer edge and the tip edge portion of the discharge valve.