JPH064378U - Valve structure in compressor - Google Patents

Abstract

(57) [Summary] [Purpose] To provide a valve structure capable of suppressing power loss and noise in a compressor. A valve seat concave surface 13c is formed around a discharge port 13b which connects the cylinder bore 2a and the discharge port 13b. Discharge valve 15 that opens and closes the discharge port 13b
a is elastically deformed and joined to the valve seat concave surface 13c. The valve seat concave surface 13c is recessed along the extending direction of the discharge valve 15a,
The discharge valve 15a is housed within the recess width of the valve seat concave surface 13c.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 According to the present invention, a cylinder bore in a cylinder block accommodating a piston is partitioned by a valve plate, and a port on a valve plate for letting a refrigerant gas into and out of the cylinder bore is opened and closed by a butterfly-type elastic deformation valve. It is about construction.

[0002]

[Prior art]

 In this type of piston type compressor, the gap between the head end surface of the piston at the top dead center position and the valve plate, that is, the top clearance, is made as small as possible to improve the volumetric efficiency. Performance is being improved.

However, if the volumetric efficiency is improved to the limit in consideration of the assembly error, an over-compression phenomenon occurs in which the pressure in the cylinder bore becomes higher than the discharge pressure, and the impact on peripheral equipment due to the discharge of this over-compressed gas. The noise becomes severe due to the impact of the discharge valve that opens and closes the discharge port on the retainer. The cause of this over-compression is the presence of mist-like lubricating oil in the refrigerant gas. That is, when the discharge port is blocked by the discharge valve, the discharge port and the valve plate are in close contact with each other due to the surface tension and adhesive force of the lubricating oil, but the adhesion force due to the lubricating oil is surprisingly strong. Therefore, the discharge valve becomes difficult to separate from the valve plate, overcompression occurs, and power loss and noise are induced.

When the refrigerant gas is introduced into the cylinder bore, the suction port that opens and closes the suction port becomes difficult to separate from the valve plate, and power loss due to suction pressure loss occurs. Japanese Utility Model Application Laid-Open No. 1-127980 discloses a valve structure in which a joint recess is provided in a region around the port facing the elastic deformation valve, and the elastic deformation valve is deformed and brought into close contact with the concave surface of the valve seat. According to this close contact structure, when the elastically deformable valve is separated from the joint recess, the elastic return force of the elastically deformable valve opposes the close contact force of the lubricating oil, and the port is easily opened.

[0005]

[Problems to be solved by the device]

 However, the diameter of the joint recess is smaller than the diameter of the circular tip of the elastic deformation valve, and the deformation region of the elastic deformation valve when it comes into close contact with the joint recess is only the central portion of the circular tip. This deformed state is equivalent to forming a spherical concave portion on a flat plate by elastic deformation, but such elastic deformation is not easy and the sealing property between the joint concave portion and the elastic deformation valve is not good.

An object of the present invention is to provide a valve structure that reduces power loss and noise and is excellent in sealing performance.

[0007]

[Means for Solving the Problems]

 Therefore, in the present invention, a valve seat concave surface is provided in a region on the valve plate facing the elastic deformation valve around the port, the concave direction of the valve seat concave surface is specified as one direction, and the elastic deformation valve is within this concave width. It was stored.

[0008]

[Action]

 The elastically deformable valve is curved in the recess direction within the width of the concave surface of the valve seat and is joined to the concave surface of the valve seat. It is easy to bend the flat plate in one direction, and by appropriately setting the concave shape of the concave surface of the valve seat, the elastically deformed valve curved in one direction is joined exactly to the concave surface of the valve seat. When the elastic deformation valve separates from the concave valve seat surface, this curved elastic deformation force opposes the adhesion force between the elastic deformation valve and the concave valve seat surface due to the lubricating oil, and the elastic deformation valve smoothly separates from the concave valve seat surface. .

[0009]

【Example】

 An embodiment in which the present invention is embodied in a swash plate type compressor will be described below with reference to FIGS.

As shown in FIG. 1, a pair of front and rear cylinder blocks 1 and 2 that are fastened and joined together is supported by a rotary shaft 4 to which a swash plate 3 is fixed. There are formed a plurality of cylinder bores 1a and 2a. A double-headed piston 5 is reciprocally housed in a pair of front and rear cylinder bores 1a and 2a, and a shoe 6 is interposed between the double-headed piston 5 and the swash plate 3. Therefore, when the swash plate 3 rotates, the double-headed piston 5 moves back and forth in the cylinder bores 1a and 2a.

A front housing 7 is joined to an end surface of the cylinder block 1 via a valve plate 8, a pair of valve forming plates 9 and 10 and a retainer forming plate 11, and an end surface of the cylinder block 2 is also connected to the rear housing 12. Are joined together via a valve plate 13, a pair of valve forming plates 14 and 15, and a retainer forming plate 16.

Suction chambers 7a and 12a and discharge chambers 7b and 12b are formed in the housings 7 and 12, respectively. The suction chambers 7a, 12a are connected to the cylinder bores 1a, 2a via suction ports 8a, 13a on the valve plates 8, 13 and the discharge chambers 7b, 12b are discharged ports 8b on the valve plates 8, 13 respectively. It is connected to the cylinder bores 1a and 2a via 13b. The suction ports 8a and 13a are opened and closed by elastic deformation of the suction valves 9a and 14a on the valve forming plates 9 and 14, and the discharge ports 8b and 13b are opened and closed by elastic deformation of the discharge valves 10a and 15a on the valve forming plates 10 and 15. To be done. During the suction stroke of the head end surface 5a side of the double-headed piston 5, the cooling medium gas in the suction chamber 7a pushes the suction valve 9a and is sucked into the cylinder bore 1a. Then, during the discharge stroke of the head end surface 5a side of the double-headed piston 5, the refrigerant gas in the cylinder bore 1a pushes the discharge valve 10a and is discharged to the discharge chamber 7b. Similar suction and discharge are performed on the other cylinder bore 2a side of the double-headed piston 5, and the discharge valves 10a and 15a, which are displaced along with the discharge of the refrigerant gas from the cylinder bores 1a and 2a to the discharge chambers 7b and 12b, form retainers. The retainers 11a and 16a on the plates 11 and 16 are brought into contact with each other.

As shown in FIGS. 1 and 3, a valve seat concave surface 13c is provided in a region of the valve plate 13 around the discharge port 13b where the discharge valve 15a is joined. As shown in FIG. 2, the valve seat concave surface 13c has a rectangular shape and surrounds the discharge port 13b. As shown in FIGS. 3 and 4, the valve seat concave surface 13c is recessed along the extension direction of the discharge valve 15a, and as shown in FIG. 2, the discharge valve 15a has a recess width W of the valve seat concave surface 13c and a recess length. It is stored in H.

Also on the valve plate 8 side, a valve seat concave surface 8c similar to the valve seat concave surface 13c is provided around the discharge port 8b. When the head end surface 5a side of the piston 5 moves from the suction stroke to the discharge stroke, the discharge valve 15a closes the discharge port 13b as shown in FIGS. At this time, the discharge valve 15a is curved and deformed along the concave direction of the valve seat concave surface 13c, and is joined to the valve seat concave surface 13c. Since the discharge valve 15a bends only in a specific direction, which is the recessed direction of the valve seat concave surface 13c, this elastic deformation is easily performed. Therefore, if the concave shape of the valve seat concave surface 13c is properly set, the discharge valve 15a is joined to the valve seat concave surface 13c exactly and the discharge port 13b is closed well.

When the head end surface 5a side of the piston 5 moves from the discharge stroke to the suction stroke, the discharge valve 15a is separated from the valve seat concave surface 13c. The discharge valve 15a and the valve seat concave surface 13c are tightly joined to each other, and the adhesive force of the lubricating oil is large. The discharge valve 15a is elastically deformed and comes into close contact with the valve seat concave surface 13c, and this elastic deformation force opposes the adhesion force due to the lubricating oil. Therefore, the discharge valve 15a is smoothly separated from the valve seat concave surface 13c, and the inside of the cylinder bore 2a is not overcompressed. Therefore, power loss and noise due to overcompression are suppressed.

Similar high sealing performance and smooth separation are achieved between the other discharge valve 10a and the valve seat concave surface 8c. The discharge valves 10a and 15a are housed in the valve seat concave surfaces 8c and 13c. However, if the discharge valves 10a and 15a are within the recess width W, even if the tip ends of the discharge valves 10a and 15a protrude from the valve seat concave surfaces 8c and 13c. There is no hindrance.

Of course, the present invention is not limited to the above-described embodiment. For example, as shown in FIG. 6, a valve seat concave surface 13d is provided around the intake port 13a, and the intake valve 14a is elastically deformed to form a valve seat concave surface. You may make it join to 13d. Also in this case, the valve seat concave surface 13d is recessed only in a specific direction, which is the extending direction of the intake valve 14a.

Further, in the present invention, even if the elastically deformable valve such as the discharge valve or the intake valve is not elastically deformed, it may have a curved shape close to the concave shape of the concave surface of the valve seat. In this case, the curvature of the elastic deformation valve when it is not elastically deformed is smaller than that of the concave surface of the valve seat, and the elastic return action of the elastic deformation valve facilitates the separation between the concave surface of the valve seat and the elastic deformation valve. There is a need.

Further, in the present invention, the elastically deformable valve may be bent and deformed in a direction orthogonal to the extending direction of the elastically deformable valve when the elastically deformable valve is joined to the concave surface of the valve seat.

[0020]

[Effect of device]

 As described above in detail, according to the present invention, the concave direction of the valve seat concave surface is specified as one direction, and the elastic deformation valve is accommodated within this concave width, so that the elastic deformation valve has a concave direction within the width of the valve seat concave surface. In addition to being easily curved and joined to the concave surface of the valve seat, the elastic deformation valve and the concave surface of the valve seat can be easily separated, which can improve the sealing performance when the port is closed and prevent overcompression that causes power loss and noise. It has an excellent effect that it can be avoided.

[Brief description of drawings]

FIG. 1 is a side sectional view of an entire compressor.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is an enlarged cross-sectional view taken along line BB of FIG.

FIG. 4 is an enlarged cross-sectional view taken along line CC of FIG.

FIG. 5 is an enlarged side sectional view of an essential part showing a state in which the concave surface of the valve seat and the discharge valve are joined.

FIG. 6 is an enlarged side sectional view of an essential part showing another example.

[Explanation of symbols]

8, 13 ... Valve plate, 8a, 13a ... Suction port, 8b, 13b ... Discharge port, 8c, 13c ... Valve seat concave surface, 9a, 14a ... Suction valve, 10a, 15a ... Discharge valve.

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Creator Tomohiko Yokono 2-chome, Toyota-cho, Kariya city, Aichi stock company Toyota Industries Corp.

Claims (1)

[Scope of utility model registration request] 1. A compressor in which a cylinder bore in a cylinder block for accommodating a piston is defined by a valve plate, and a port on the valve plate for entering and exiting a refrigerant gas to and from the cylinder bore is opened and closed by a butterfly-type elastic deformation valve. A valve seat concave surface is provided in the area around the port on the plate facing the elastic deformation valve, and the concave direction of the valve seat concave surface is specified as one direction, and the valve in a compressor in which the elastic deformation valve is housed within this concave width Construction.