WO1999014494A1

WO1999014494A1 - Valve structure and compressor

Info

Publication number: WO1999014494A1
Application number: PCT/JP1998/004113
Authority: WO
Inventors: Katsutoshi Enomoto; Kiyoshi Yoshii; Makoto Tabata; Katsuhiko Arai
Original assignee: Zexel Corporation
Priority date: 1997-09-18
Filing date: 1998-09-11
Publication date: 1999-03-25
Also published as: JPH1193840A

Abstract

A valve structure and a compressor, in which a large seating area is ensured for a reed valve and flexure of the reed valve at the time of seating is prevented to improve durability of the reed valve. Specifically, a reciprocating compressor comprising cylinder blocks (1, 2) wherein compressing chambers (21, 22) are formed, cylinder heads (4, 6) wherein discharge chambers (24) are formed, valve plates (3, 5) wherein two discharge ports (3a, 5a) providing communication between the compressing chambers (21, 22) and the discharge chambers (24) are formed, and discharge valve sections (27a, 28a) which open and close the two discharge ports (3a, 5a), wherein the two discharge ports (3a, 5a) are aligned in the lengthwise direction of the discharge valve sections (27a, 28a).

Description

Description Valve structure and compressor Technical field

The present invention relates to a valve structure and a compressor having the valve structure. Background art

FIGS. 8 (a) and (b) show the relationship between the reed valve of the conventional reciprocating compressor and the port of the valve plate. FIG. 8 (a) is a plan view and FIG. 8 (b) ) Is a cross-sectional view taken along line 8B-8B in FIG. 8 (a). The valve plate 503 is provided with a port 503a having a round hole, for example, a discharge port. When the reed valve 527, for example, the discharge valve is opened (elastically deformed) as shown by the two-dot chain line in FIG. 8 (b), the compression chamber and the discharge chamber communicate with each other through the port 503a, High-pressure refrigerant gas is discharged from the compression chamber to the discharge chamber.

To reduce the size of the reed valve 527, there is a method of reducing the width H of the reed valve 527. Incidentally, a method of reducing the longitudinal dimension of the reed valve 527 is also conceivable, but the smaller the size, the more difficult it is to open the reed valve 527, so this method cannot be adopted.

9 (a) to 9 (c) show the relationship between the reed valve having a reduced width and the port of the valve plate. FIG. 9 (a) is a plan view and FIG. 9 (b) Fig. 9 (a) is a cross-sectional view taken along line 9B-9B, and Fig. 9 (c) is a cross-sectional view showing a state where the lead valve is bent.

As shown in Fig. 9 (a), as the width dimension H of the reed valve 627 becomes smaller, the port 603a is made elongated. Port 6 03 a By doing so, the same opening area as the port 503 is secured. However, the seating area of the reed valve 6

7 The impact force when sitting is increased.

Further, since the port 603a is a long hole along the longitudinal direction of the reed valve 627, the reed valve 627 is bent as shown in FIG. 9 (c), and stress concentration due to the bending is reduced. Occurs.

As a result, the reed valve 6 27 is easily damaged, and the durability is reduced. For example, the tip of the reed valve 627 sometimes cracked during high-speed operation. Disclosure of the invention

The present invention has been made in view of such circumstances, and its purpose is to secure a wide seating area of the lead valve, prevent the lead valve from bending when seated, and improve the durability of the lead valve. An object of the present invention is to provide a valve structure and a compressor that can be improved.

According to a first aspect of the present invention, there is provided a valve structure for controlling a flow of a fluid between a first chamber and a second chamber, wherein A partition member between the second chamber, a valve port formed in the partition member, and allowing the fluid to flow from one of the first chamber and the second chamber to the other chamber; A valve structure comprising a reed valve for opening and closing a valve port is provided.

A valve structure according to a first aspect of the present invention is characterized in that the valve port includes a plurality of ports arranged along a longitudinal direction of the reed valve.

According to this valve structure, since the plurality of ports are disposed along the longitudinal direction of the reed valve, the seating area of the partition member around the port on which the reed valve is seated increases, and the seating of the reed valve increases The impact of time is reduced, Also, the lead valve is less likely to bend and the durability of the reed valve is improved.

It is preferable that at least one of the plurality of ports is formed as a long hole.

According to this preferred aspect, a large channel area of the valve port can be easily secured by the long hole, and the seating portion of the lead valve secured between the long hole and the other hole allows The seating area of the reed valve is increased, the impact when the reed valve is seated is reduced, the reed valve is less likely to bend, and the durability of the reed valve is further improved.

More preferably, the plurality of ports include a plurality of ports formed in a row.

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According to this preferred aspect, it is easy to form the port at a position corresponding to the lead valve.

More preferably, the plurality of ports formed in one row are two elongated holes.

According to this preferred aspect, it is possible to secure a sufficient flow passage area for the port and a sufficient seating area.

Alternatively, the plurality of ports formed in one row are three elongated holes.

According to this preferred embodiment, it is possible to secure a sufficient flow passage area and a sufficient seating area in the port, and it is difficult for the reed valve to be bent in one layer.

Alternatively, the plurality of ports are preferably a plurality of ports formed in a plurality of rows.

According to this preferred aspect, since the plurality of port forces are arranged in a plurality of rows along the longitudinal direction of the lead valve, the seating area of the lead valve is larger, and The shock is further reduced and the reed valve is more It becomes difficult to bend and the durability of the reed valve is further improved.

More preferably, the plurality of ports are a plurality of long holes formed in parallel with each other.

According to this preferred aspect, since the plurality of ports are arranged along the longitudinal direction of the lead valve, the seating area of the reed valve is increased, and the impact when the lead valve is seated is reduced. In addition, the lead valve hardly bends, and the durability of the lead valve is improved.

For example, the plurality of long holes formed in parallel with each other are two long holes.

Preferably, the plurality of ports are ports formed in a portion of the partition member where the tip side of the reed valve is seated, and have an opening area smaller than the opening areas of the other ports of the plurality of ports. Includes ports.

According to this preferred aspect, the opening area of the port facing the front end of the reed valve is smaller than the opening areas of the other ports, so that the seating area at the front end of the lead valve is larger than the seating area at the rear end. The impact will be reduced when the tip of the reed valve is seated.

For example, the plurality of ports are formed as one round hole and one long hole, and the port having the smaller opening area is the round hole. Preferably, the first chamber is a compression chamber of a compressor, the second chamber is a discharge chamber of the compressor, and the partition member is a valve plate.

More preferably, the reed valve is a discharge valve portion formed integrally with a valve sheet disposed on the discharge chamber side of the valve plate. In order to achieve the above object, according to a second aspect of the present invention, a compression chamber for compressing a refrigerant, a discharge chamber from which the compressed refrigerant is discharged from the compression chamber, A partition member disposed between the compression chamber and the discharge chamber, a discharge port formed in the partition member, a discharge port through which the compressed refrigerant passes, and a discharge valve for opening and closing the discharge port Are provided. The compressor according to a second aspect of the present invention is characterized in that the discharge valve is a reed valve, and the discharge port includes a plurality of ports disposed along a longitudinal direction of the discharge valve. I do.

It is preferable that at least one of the plurality of ports is formed as a long hole. BRIEF DESCRIPTION OF THE FIGURES

Fig. 1 (a) is a plan view of the valve plate, valve seat and part of the stopper plate which are overlapped with each other as viewed from the stopper plate side. Fig. 1 (b) is 1B-1B of Fig. 1 (a). FIG. 1 (c) is a sectional view taken along line 1C-1C of FIG. 1 (a).

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

FIG. 3 is an exploded perspective view showing a valve plate, a valve seat, and a stop plate.

4 (a) to 4 (c) are views showing a part of a swash plate type compressor according to a modified example of the first embodiment of the present invention, and FIG. Fig. 4 (b) is a cross-sectional view taken along line 4B-4B in Fig. 4 (a), and Fig. 4 (c) is a plan view of a part of the valve seat and the stopper plate viewed from the stopper plate side. Fig. 4 is a cross-sectional view taken along the line 4C-4C in Fig. 4 (a).

FIGS. 5 (a) to 5 (c) are views showing a part of a swash plate type compressor according to a second embodiment of the present invention, and FIG. Fig. 5 (b) is a cross-sectional view taken along the line 5B-5B in Fig. 5 (a). Figure (c) is a cross-sectional view along the line 5C-5C in Figure 5 (a).

FIGS. 6 (a) to 6 (c) are views showing a part of a swash plate type compressor according to a third embodiment of the present invention, and FIG. 6 (a) is a view showing a valve plate and a valve sheet overlapping each other. 6 (b) is a cross-sectional view taken along line 6B-6B in FIG. 6 (a), and FIG. 6 (c) is a cross-sectional view of the stopper plate as viewed from the stopper plate side. Fig. 6 (a) is a cross-sectional view along the line 6C-6C.

7 (a) to 7 (c) are views showing a part of a swash plate type compressor according to a fourth embodiment of the present invention, and FIG. 7 (a) is a view showing a valve plate, a valve seat and FIG. 7 (b) is a cross-sectional view taken along line 7B-7B of FIG. 7 (a), and FIG. 7 (c) is a plan view of a part of the stop plate seen from the stop plate side. FIG. 7 is a sectional view taken along the line 7 C— 7 C in FIG.

FIGS. 8 (a) and (b) are diagrams showing the relationship between the reed valve of the conventional reciprocating compressor and the port of the valve plate. FIG. 8 (a) is a plan view, and FIG. ) Is a sectional view taken along line 8B-8B in FIG. 8 (a). 9 (a) to 9 (c) are views showing the relationship between the reed valve having a reduced width and the port of the valve plate, wherein FIG. 9 (a) is a plan view and FIG. 9 (b) Fig. 9 (a) is a sectional view taken along the line 9B-9B, and Fig. 9 (c) is a sectional view showing a state in which the reed valve is bent. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 2 is a longitudinal sectional view showing the entire swash plate type compressor according to the first embodiment of the present invention.

The front side cylinder block 1 and the rear side cylinder block 2 are axially opposed to each other and joined to form a cylinder assembly. A front head (cylinder head) 4 is disposed on the front end surface of the cylinder assembly via a valve plate 3, a valve seat 27 and a stopper plate 29, and a valve plate 5 and a valve are disposed on the rear end surface. A rear head (cylinder head) 6 is arranged via a seat 28 and a stopper plate 30.

The shell 13 on the front side is provided on the front head 4 and the shell 14 on the rear side is provided integrally with the head 6, and the front shell 13 and the shell 14 are O-ring 3. They are fitted to each other in the axial direction via 8.

The front head 4, the cylinder blocks 1 and 2, the shells 13 and 14, and the rear head 6 are axially connected by a plurality of through ports 39. 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 connected to the cylinder block 1 by bearings 9 and 10, respectively. , 2 are rotatably supported on the inner walls of the center holes 41, 42 penetrating the center. The swash plate 8 is inclined with respect to the drive shaft 7.

The cylinder blocks 1 and 2 are provided with a plurality of cylinder pores 11. The respective cylinder pores 11 are parallel to the drive shaft 7 and are arranged at predetermined intervals in a circumferential direction around the drive shaft 7. A piston 12 is slidably accommodated in each cylinder bore 11. Disc-shaped projections 15 are provided on both end faces 12 a of the piston 12.

Compression chamber (first chamber) on both sides of piston 1 2 in each cylinder pore 1 1 2 1 and 2 2 are formed. The piston 1 2 has a substantially hemispherical shape 1 9,

The piston 12 is connected to the swash plate 8 via 20, and the piston 12 reciprocates in the cylinder pore 11 as the swash plate 8 rotates.

Fig. 3 is an exploded perspective view showing the valve plate, the valve seat and the stop plate. Fig. 1 (a) is a view of the valve plate, the valve seat and a part of the stop plate overlapping each other, as viewed from the stop plate side. Fig. 1 (b) is a cross-sectional view along the line IB-1B in Fig. 1 (a), and Fig. 1 (c) is a line 1C-1C in Fig. 1 (a). It is sectional drawing which follows.

Discharge ports (ports) 3 a for discharging refrigerant gas from the compression chambers 21 and 22 to the discharge chambers (second chamber, pressure chamber) 24 are provided in the substantially disk-shaped valve plates 3 and 5. , 5a, Suction valve escape holes 3b, 5b and through bolts that allow the suction valve parts 27d, 28d to escape to the compression chambers 21, 22 during the suction stroke

Port through holes 3 c and 5 (: f are respectively formed to insert 39.

As shown in FIG. 1, the discharge ports 3a and 5a are formed of two holes arranged in the longitudinal direction of discharge valve portions 27a and 28a described later.

The suction valve relief holes 3b and 513 are adjacent to the suction ports 29d and 30d via the suction valve portions 27 and 28d, respectively, and the suction valve portions 27d and 28d during the suction stroke. When it opens, it communicates with the suction ports 29 d and 30 d.

The substantially disk-shaped valve seats 27 and 28 have tongue-shaped discharge valve parts (lead valves) 27a and 28a and tongue-shaped suction valve parts 27d and 28d, respectively. Notches are formed, and bolt through holes 27c and 28c are formed.

The substantially disk-shaped stopper plates 29 and 30 include groove-shaped stoppers 29 a and 30 a for suppressing the opening or deformation of the discharge valve portions 27 a and 28 a, and the suction chamber 23. Suction port for sucking the refrigerant gas into the compression chambers 21 and 22 The ports 29d and 30d and the port through holes 29c and 30c are formed respectively. The bottom surfaces of the stoppers 29a and 30a are inclined at a predetermined angle or an arbitrary curvature with respect to the discharge valve portions 27a and 28a in the closed state. In addition, ejection holes 29b, 30b are formed in the stopper plates 29, 30. The discharge holes 29b and 30b are adjacent to the discharge ports 3a and 5a via the discharge valve portions 27a and 28a, respectively. During the discharge stroke, the discharge valve portions 27a and 28a When opened, it communicates with discharge ports 3a and 5a.

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 pore 11. When the swash plate 8 makes a half turn from the position where the piston 1 2 comes closest to the valve plate 3 (the position of the top dead center of the piston 1 2 on the compression chamber 21 side), the piston 1 2 moves to the valve plate 5 side. Then, the suction stroke is performed on the compression chamber 21 side until the end, and the compression stroke and the discharge stroke are performed on the compression chamber 21 side until the end. When the swash plate 8 further rotates 1Z2 from this state, the suction stroke is performed on the compression chamber 22 side until the compression stroke and the discharge stroke are completed on the compression chamber 21 side.

In the suction stroke, one of the pressures of the compression chambers 21 and 22 becomes smaller than the pressure of the suction chamber 23, and the suction valve portions 27d and 28d are moved toward the suction valve relief holes 3b and 5b. It is elastically deformed, and one of the compression chambers 21 and 22 communicates with the suction chamber 23 through the suction ports 29 d and 3 Od and the suction valve part relief holes 3 b and 5 b. Low-pressure refrigerant gas flows into one of the compression chambers 21 and 22 from the compressor. At this time, the discharge valve sections 27a and 28a are closed.

When the piston 12 reaches the bottom dead center, the suction stroke ends. At this time, the volume of one of the compression chambers 21 and 22 becomes maximum.

Then, the piston 12 moves from the bottom dead center and enters the compression stroke. Screw As the ton 12 approaches the valve plates 3 and 5, the volume of one of the compression chambers 21 and 22 gradually decreases, and the refrigerant gas in one of the compression chambers 21 and 22 is compressed. At this time, the suction valve portions 27d and 28d and the discharge valve portions 27a and 28a are closed.

When one of the pressures of the compression chambers 21 and 22 exceeds a certain value, the process moves to the discharge stroke, and the discharge valve portions 27a and 28a elastically deform to the stoppers 29a and 30a, and discharge is performed. One of the compression chambers 21 and 22 communicates with the discharge chamber 24 via the ports 3a and 5a and the discharge holes 29b and 30b, and from one of the compression chambers 21 and 22. High-pressure refrigerant gas flows out to the discharge chamber 24. At this time, the discharge valve portions 27a and 28a are pressed against the stoppers 29a and 30a, and the opening amounts of the discharge valve portions 27a and 28a are suppressed.

Then, when the piston 12 reaches the top dead center, the discharge stroke ends. At this time, the projection 15 of the piston 12 enters the suction valve portion relief holes 3b and 5b, and the discharge valve portions 27a and 28a are seated on the valve plates 3 and 5.

Since the discharge ports 3a and 5a are composed of two holes along the longitudinal direction of the discharge valve sections 27a and 28a, the discharge valve sections 27a and 28a have a large seating area and discharge. The impact of the valve portions 27a and 28a when seated is reduced, and the discharge valve is almost completely interposed between the discharge valve portions 27a and 28a. The parts 27a and 28a do not bend.

According to the first embodiment, since the discharge valve portions 27 a and 28 a can secure a wide seating area and prevent the discharge valve portions 27 a and 28 a from bending, the discharge valve portion 27a and 28a can be prevented from being damaged, and the durability can be improved.

Further, in this embodiment, the discharge ports 3a and 5a are constituted by two long holes formed in one row along the longitudinal direction of the discharge valve portions 27a and 28a. The width of the discharge valve sections 27a and 28a can be reduced, and the discharge valve sections 27a and 28a can be reduced in size, so that the discharge valve sections 27a and 28a open. It becomes easier (the valve opening time becomes earlier), and overcompression can be reduced. As a result, the pressure at the time of discharge of the compression chambers 21 and 22 can be adjusted to a suitable level, so that the performance is improved. And reliability is improved.

FIG. 4 is a view showing a main part of a swash plate type compressor according to a modified example of the first embodiment of the present invention. FIG. 4 (a) shows a valve plate, a valve sheet and a stopper plate which overlap each other. Fig. 4 (b) is a cross-sectional view taken along the line 4B-4B in Fig. 4 (a), and Fig. 4 (c) is a diagram in Fig. 4 (a). 4) is a cross-sectional view of FIG. Portions common to the above-described embodiment are denoted by the same reference numerals, and description thereof will be omitted.

In the first embodiment, the discharge ports 3a and 5a are constituted by two long holes formed in one row along the longitudinal direction of the discharge valve portions 27a and 28a. 103a and 105a were composed of three long holes formed in one row along the longitudinal direction of the discharge valve sections 27a and 28a.

According to this modified example, the seating area of the discharge valve portions 27a, 28a becomes larger, so that the impact when the discharge valve portions 27a, 28a are seated is further alleviated. Since the parts 27a and 28a correspond to the two partition parts 140 and 150, the discharge valve parts 27a and 28a are more difficult to bend, and the discharge valve parts 27a and 28 The durability of a is further improved.

FIG. 5 is a view showing a main part of a swash plate type compressor according to a second embodiment of the present invention. FIG. 5 (a) shows one of a valve plate, a valve sheet and a stopper plate which are overlapped with each other. Fig. 5 (b) is a sectional view taken along the line 5B-5B in Fig. 5 (a), Fig. 5 (c) Fig. 5 is a sectional view taken along the line 5C-5C in Fig. 5 (a). Portions common to the above-described embodiments are denoted by the same reference numerals, and description thereof is omitted.

In the first embodiment, the discharge ports 3a and 5a are constituted by two holes arranged in the longitudinal direction of the discharge valve portions 27a and 28a, but in the second embodiment, the discharge ports 203a and 2a are formed. 05a was constituted by two elongated holes parallel to each other along the longitudinal direction of the discharge valve portions 27a and 28a.

According to the second embodiment, the same effects as in the first embodiment can be obtained.

FIG. 6 is a view showing a main part of a swash plate type compressor according to a third embodiment of the present invention, and FIG. 6 (a) shows one of a valve plate, a valve sheet and a stopper plate which overlap each other. Fig. 6 (b) is a cross-sectional view taken along line 6B-6B in Fig. 6 (a), and Fig. 6 (c) is Fig. 6 (a). FIG. 3 is a cross-sectional view taken along line 6C-6C of FIG. Portions common to the above-described embodiments are denoted by the same reference numerals, and description thereof is omitted. In the third embodiment, the discharge ports 303a and 305a are configured by four long holes formed in two rows along the longitudinal direction of the discharge valve portions 27a and 28a.

According to the third embodiment, the larger the seating area of the discharge valve portions 27a and 28a is, the more the impact when the discharge valve portions 27a and 28a are seated is further reduced. Since the discharge valve portions 27a and 28a hit the cross partition portions 340 and 350, the discharge valve portions 27a and 28a are less likely to bend, and the discharge valve portions 27a and 28a Durability is further improved.

FIG. 7 is a view showing a main part of a swash plate type compressor according to a fourth embodiment of the present invention, and FIG. 7 (a) shows a part of a valve plate, a valve sheet and a stopper plate which overlap each other. Fig. 7 (b) is a cross-sectional view taken along line 7B-7B in Fig. 7 (a), and Fig. 7 (c). Fig. 7 is a sectional view taken along the line 7C-7C in Fig. 7 (a). Portions common to the above-described embodiments are denoted by the same reference numerals, and description thereof is omitted.

In the fourth embodiment, the discharge ports 403a and 405b are constituted by two ports formed in one row along the longitudinal direction of the discharge valve portions 27a and 28a. Out of the two ports, the ports located at the front end of the discharge valves 27a and 28a are round holes, and the ports located at the rear end of the discharge valves 27a and 28a are long holes. I made it. Moreover, the opening area of the round hole was made smaller than the opening area of the long hole.

According to the fourth embodiment, the seating area at the front end side of the discharge valve sections 27a, 28a is larger than the seating area at the rear end side, so that the discharge valve sections 27a, 28a The impact at the time of seating of the tip is reduced, and the durability of the discharge valve portions 27a and 28a is further improved.

In each of the above-described embodiments, the discharge port is formed as a port, and the discharge valve portions 27a and 28a are formed as cut valves together with the suction valve portions 27d and 28d as reed valves. However, the scope of application of the present invention is not limited to this, and the port is a suction port in addition to the discharge port, and the reed valve is a suction port in addition to the discharge valve portions 27a and 28a. There are valve parts 27 d and 28 d. Further, the discharge valve and the suction valve serving as the reed valve are not limited to those integrally formed on the valve seat as in each of the above-described embodiments, and the discharge valve and the suction valve are separate and independent components. There may be.

In the above-described embodiment, the case where the valve structure of the present invention is applied to a swash plate type compressor has been described. However, the scope of the present invention is not limited to this. It can be applied to various types of reciprocating compressors such as compressors (crank compressors) and other compressors, and can also be applied to equipment other than compressors. Industrial applicability

ADVANTAGE OF THE INVENTION According to the valve structure of this invention, the seating area of a reed valve becomes large, the impact at the time of seating of a reed valve is eased, and since a reed valve becomes hard to bend, the durability of a reed valve improves. This valve structure can be suitably used for a discharge valve of a compressor, etc., and improves the performance and durability of the compressor.

Claims

The scope of the claims

1. A valve structure for controlling a flow of a fluid between a first chamber and a second chamber, wherein a partition member between the first chamber and the second chamber, and the partition member A valve port formed in the first chamber and the second chamber, and having a valve port for flowing the fluid from one chamber to the other chamber, and a reed valve for opening and closing the valve port.

The valve structure, wherein the valve port comprises a plurality of ports arranged along a longitudinal direction of the reed valve.

2. The valve structure according to claim 1, wherein at least one of the plurality of ports is formed as an elongated hole.

3. The valve structure according to claim 2, wherein the plurality of ports are a plurality of ports formed in one row.

4. The valve structure according to claim 3, wherein the plurality of ports formed in one row are two long holes.

5. The valve structure according to claim 3, wherein the plurality of ports formed in one row are three elongated holes.

6. The valve structure according to claim 2, wherein the plurality of ports are a plurality of ports formed in a plurality of rows.

7. The valve structure according to claim 2, wherein the plurality of ports are a plurality of elongated holes formed in parallel with each other.

8. The valve structure according to claim 7, wherein the plurality of slots are two slots.

9. The plurality of ports are ports formed at a portion of the partition member where the distal end side of the reed valve is seated, and have a smaller opening area than other ports of the plurality of ports. To include 3. The valve structure according to claim 2, wherein:

10. The plurality of ports are formed as one round hole and one long hole, and the port having the smaller opening area is the round hole. Valve structure.

11. The first chamber is a compression chamber of a compressor, the second chamber is a discharge chamber of the compressor, and the partition member is a valve plate. 2. The valve structure according to item 1, wherein

12. The valve according to claim 11, wherein the reed valve is a discharge valve portion formed integrally with a valve seat disposed on the discharge chamber side of the valve plate. Construction.

13. A compression chamber for compressing the refrigerant, a discharge chamber from which the refrigerant compressed from the compression chamber is discharged, a partition member disposed between the compression chamber and the discharge chamber, and the partition member. A compressor comprising: a discharge port, a discharge port through which the compressed refrigerant passes; and a discharge valve that opens and closes the discharge port.

The discharge valve is a lead valve;

The compressor, wherein the discharge port comprises a plurality of ports arranged along a longitudinal direction of the discharge valve.

14. The compressor according to claim 13, wherein at least one of said plurality of ports is formed as an elongated hole.