KR101086100B1 - Valve apparatus of reciprocating compressor - Google Patents

Abstract

The present invention relates to the valve device of the reciprocating compressor,

A cylinder block having a housing, a plurality of cylinder bores, a piston accommodated reciprocally in the cylinder bore, a piston drive means for driving the piston, and a suction valve installed opposite the bottom of the piston; A valve device including a discharge valve, and a reciprocating compressor configured to include a suction chamber and a discharge chamber formed in the housing via the valve device, the plurality of suction ports facing the bottom surface of the piston and along the circumferential direction A valve plate having a discharge port formed therein; A domed shell valve detachably installed at a discharge port on the discharge chamber side; And a retainer disposed to face the valve plate with the domed shell valve interposed therebetween. Thus, the dome-shaped shell valve is moved between the valve plate and the retainer to open and close the discharge port of the valve plate. The dead volume due to space can be minimized and the efficiency of the compressor can be maximized.

Description

VALVE APPARATUS OF RECIPROCATING COMPRESSOR}

The present invention relates to a valve device of a reciprocating compressor, and more particularly, to a valve device of a reciprocating compressor having a simplified structure by minimizing the dead volume of a cylinder bore and forming oil and refrigerant supply passages together.

A reciprocating compressor is a compressor comprising a piston, a piston drive device, and a cylinder block having a cylinder bore in which the piston reciprocates. A suction / discharge valve for controlling the entry and exit of the medium between the bottom of the cylinder bore and the bottom of the piston. The device is installed.

1A to 1C show the structure of a capacity variable swash plate compressor as a representative example of a reciprocating compressor.

As shown, the conventional variable displacement swash plate compressor 10, the cylinder block 11 having a plurality of cylinder bores (11a) formed in parallel in the longitudinal direction on the inner peripheral surface, and the front of the cylinder block 11 It consists of a front housing 12 is hermetically coupled to the rear housing 13 is hermetically coupled via a valve plate 13a at the rear of the cylinder block 11.

A swash plate chamber 14 is formed inside the front housing 12, and one end of the drive shaft 15 is rotatably supported at the center of the front housing 12, while the other end of the drive shaft 15 is It passes through the swash plate chamber 14 and is supported by the bearing 11c to the central shaft hole 11b of the cylinder block 11 via a bearing 11c.

In addition, the drive shaft (15) is provided with a lug plate (16) spaced apart by a predetermined distance and a swash plate (17) provided through the drive shaft (15) so that the inclination angle is variable, and the lug plate (16) is provided. A spring 27 for elastically supporting the swash plate 17 with respect to the lug plate 16 is interposed between the swash plates 17.

In the lug plate 16, a pair of power transmission protrusions 16a, each of which has a hinge hole 16b linearly perforated, is formed to protrude integrally at one end of the surface to rotate together with the drive shaft 15, and the swash plate 17 is a hinge pin (18) fixed to one surface of the lug plate (16) formed in the hinge hole (16b) of the power transmission projection (16a) is fixed to one side while being inclined at a predetermined angle to the drive shaft (15). It is inserted so as to rotate together with the lug plate 16, and its inclination angle is variable.

In addition, the outer circumferential surface of the swash plate 17 is slidably fitted to the piston 19 provided in each cylinder bore 11a via the shoe 20.

Accordingly, as the swash plate 17 rotates in an inclined state, the pistons 19 fitted through the shoe 20 on the outer circumferential surface thereof reciprocate in each cylinder bore 11a of the cylinder block 11. .

In the rear housing 13, the suction chamber 21 and the discharge chamber 22 are respectively formed, and each cylinder is provided in the valve plate 13a interposed between the rear housing 13 and the cylinder block 11. The suction port 23 and the discharge port 24 are respectively formed in the position corresponding to the bore 11a.

Suction valves for opening and closing the inlet port 23 and the outlet port 24 in each of the inlet port 23 and the outlet port 24 formed in the valve plate 13a by the pressure change according to the reciprocating motion of the piston 19. 25 and a discharge valve 26 are provided.

In addition, the rear housing 13 has suction with the swash plate chamber 14 so as to adjust the inclination angle of the swash plate 17 by varying the pressure difference between the refrigerant suction pressure in the cylinder bore 11a and the pressure in the swash plate chamber 14. A control valve (not shown) for operatively communicating the seal 21 is provided.

In the conventional displacement variable swash plate type compressor 10 configured as described above, the inclination angle of the swash plate 17 is adjusted in response to the pressure difference between the pressure in the swash plate chamber 14 and the suction pressure in the cylinder bore 11a. The stroke distance of the piston 19 connected to the swash plate 17 is changed by the change of the inclination angle of the), and the discharge capacity of the compressor is varied.

On the other hand, as shown in Figure 1b and Figure 1c, the suction valve 25 constituting the conventional valve device was configured in a large plate shape to cover all the cylinder bores (11a). Reference numeral 25b denotes a lid of the suction valve.

Further, a gasket 13g is disposed between the cylinder block 11 and the valve plate 13a along the circumference, and a suction valve 25 is disposed between the gasket 13g and the valve plate 13a. That is, the gasket 13g and the suction valve 25 overlap each other.

Thus, in the conventional compressor, since the lid of the flat discharge valve 26 opens and closes the discharge port 24 present in the valve plate 13a, the thickness of the valve plate 13a and the discharge port 24 are reduced. The space formed by the area becomes dead volume, which adversely affects the efficiency of the compressor.

Technical Challenge

The present invention has been made to solve the above problems, an object of the present invention to provide a valve device of the reciprocating compressor that can maximize the efficiency by minimizing the dead volume in the cylinder bore.

It is also an object of the present invention to provide a valve device of a reciprocating compressor that can minimize damage to the retainer during operation.

It is also an object of the present invention to provide a valve device of a reciprocating compressor having a simplified structure by having an oil and refrigerant circulation passage itself.

Technical solution

In order to achieve the above object, the valve device of the reciprocating compressor according to the present invention,

A cylinder block having a housing, a plurality of cylinder bores, a piston accommodated reciprocally in the cylinder bore, a piston drive means for driving the piston, and a suction valve installed opposite the bottom of the piston; It is provided in the valve device including a discharge valve, and a reciprocating compressor comprising a suction chamber and a discharge chamber formed in the housing via the valve device,

A valve plate facing the bottom surface of the piston and having a plurality of inlets and outlets formed along a circumferential direction;

A domed shell valve detachably installed at a discharge port on the discharge chamber side;

And a retainer disposed to face the valve plate with the domed shell valve interposed therebetween.

Here, it is preferable to form a valve seat tapered in the axial direction at the discharge port facing the dome shell valve.

The domed shell valve preferably has a flat portion bent outwardly around the convex portion.

In addition, the flat portion edge of the domed shell valve is preferably inclined toward the convex portion.

In addition, the domed shell valve is preferably formed by connecting two surfaces having a curvature.

The angle between the line connecting the boundary points of the two curvature surfaces and the tangent at the bottom point of the domed shell valve is the line connecting the boundary points of the two curvature surfaces and the end points of the curvature surfaces and the bottom point. It is preferable that it is 0.5 to 3 times the angle between the tangent lines.

Further, it is preferable that the distance between the center of the first radius of curvature including the bottom point and the center of the second radius of curvature is in the range of 0 to 20% of the second radius of curvature.

In addition, it is preferable that an oil circulating groove is formed on the piston side facing surface of the valve plate.

In addition, it is preferable that a refrigerant circulation groove is formed on the piston side facing surface of the valve plate.

1A is a longitudinal sectional view showing an example of a conventional reciprocating compressor.

Figure 1b is a detailed cross-sectional view showing a coupling structure of the valve device in Figure 1a.

1C is a front view of FIG. 1B.

2 is a longitudinal sectional view showing an example of a reciprocating compressor equipped with a valve device according to the present invention.

3 is a perspective view showing a coupling structure of the valve device and the cylinder convex in FIG.

4 is an exploded perspective view of FIG. 3.

FIG. 5 is a perspective view illustrating a coupling state of a valve plate and a dome shell valve in FIG. 3.

FIG. 6A is a longitudinal sectional view showing a closed state of the valve device shown in FIG. 3. FIG.

FIG. 6B is a longitudinal sectional view showing an open state of the valve device shown in FIG. 3. FIG.

FIG. 7 is a perspective view illustrating a rear structure of the valve plate in FIG. 4. FIG.

FIG. 8 is a longitudinal cross-sectional view illustrating a structure of a dome shell valve in FIG. 4.

9 is a longitudinal sectional view showing another example of a reciprocating compressor equipped with a valve device according to the present invention.

Best Mode for Carrying Out the Invention

Hereinafter, with reference to the accompanying Figures 2 to 8 will be described in detail a preferred embodiment of the present invention. In the figure, a swash plate compressor is adopted as an example of the reciprocating compressor.

As shown, the reciprocating swash plate compressor 1000 according to the present embodiment includes a housing 100, a cylinder block 110 having a plurality of cylinder bores 110a, and a cylinder block 110. The cylinder bore by the sliding shaft and the drive shaft 140, the swash plate 150 is connected to the drive shaft 140 is installed to be able to change the inclination angle while rotating, and the sliding plate and the swash plate 150 A piston 200 that is reciprocally accommodated in the 110a, a suction / discharge valve device 300 provided to face the bottom of the piston 200, and the suction / discharge valve device 300 are interposed therebetween. It comprises a suction chamber 131 and the discharge chamber 132 formed in the housing 100.

The housing 100 is composed of a front housing 120 and a rear housing 130 with the cylinder block 110 interposed therebetween.

In addition, the cylinder block 110 is formed with eight cylinder bores (110a), the refrigerant introduced from the suction chamber 131 by the piston 200 reciprocating through the cylinder bore (110a) is continuous Is compressed.

The drive shaft 140 is rotatably supported by the front housing 120 and the cylinder block 110 via a bearing 400.

In addition, the swash plate 150 is slidably coupled to the piston 200 via the shoe 201.

Furthermore, connecting projections 155 are formed before and after the swash plate 150, respectively, and a connecting link 600 is interposed between the connecting projection 155 and the driving shaft 140, and the hinge pins 610 are connected to each other. Are connected by Therefore, the connection link 600 and the connection protrusion 155, the connection link 600 and the drive shaft 140 can be hinged with respect to each other.

Meanwhile, the suction chamber 131 and the discharge chamber 132 are formed in the rear housing 130, respectively.

The valve device 300 is provided with a suction valve 340 and a discharge valve 350, respectively, with a valve plate 330 interposed therebetween. The retainer 360 is disposed on the discharge chamber side of the discharge valve 350.

Specifically, first, the valve plate 330 includes an inlet 331 for communicating the cylinder bore 110a and the suction chamber 131, and an outlet 332 for communicating the cylinder bore 110a and the discharge chamber 132. Each is formed.

The discharge port 332 is freely attached to and detached from the dome type shell valve, which is the discharge valve 350. In this case, the outlet 332 facing the domed shell valve is formed with a valve seat 332a tapered in the axial direction so that the bottom of the domed shell valve is easily coupled to the outlet 332. Therefore, the seating property of the domed shell valve at the time of closing is excellent.

In addition, when the domed shell valve is used as described above, when the dome shell valve is closed by the pressure of the discharged refrigerant, the dome shell valve is closed at a higher speed than the conventional flat valve.

In addition, when the dome type shell valve is used, since the streamlined discharge flow path is formed at the time of opening, the discharge speed from the cylinder bore is faster and smoother than the conventional discharge valve having a flat structure, thereby avoiding the pressure drop.

In this case, it is important to reduce the dead volume by bringing the bottom of the domed shell valve 350 close to the inlet of the discharge port 332 and contacting the inner surface of the discharge port 332 as much as possible. In other words, it is necessary to almost fill the tapered discharge port 332 with the domed shell valve 350.

To this end, as shown in FIG. 7, the convex portion 357 of the domed shell valve 350 may be configured by connecting two curvature surfaces R1 and R2. In particular, the angle α1 between the line connecting the boundary point A2 of the two curvature surfaces from the bottom point A1 of the domed shell valve 350 and the tangent at the bottom point A1 is the two curvatures. The inner space of the discharge port 332 can be reduced as much as 0.5 to 3 times the angle α2 between the line connecting the boundary point A2 of the surface and the end point A3 of the curvature surface and the tangent at the bottom point A1. It becomes possible. In this case, however, it is necessary to make the distance between the center O _R1 of the first radius of curvature and the center O _R2 of the second radius of curvature be between 0 to 20% of the radius of O _R2 .

When the convex portion of the dome shell valve 350 is configured as a double curved surface as described above, the dead volume in the cylinder bore can be reduced, and the contact with the inner surface of the discharge port 332 can be optimized to completely prevent leakage during refrigerant intake.

As a result, the domed shell valve 350 moves to close the discharge port 332 when the refrigerant is sucked, while moving in the opposite direction when discharged, and is blocked by the retainer 360 (see FIG. 6). That is, the domed shell valve 350 controls the flow of the refrigerant while reciprocating between the discharge port 332 and the retainer 360.

The retainer 360 is preferably made of a rubber material to ensure sealing.

The retainer 360 has sealing protrusion lines 361 and 362 formed along the circumferential direction of the surface to completely separate the suction refrigerant from the suction chamber 131 and the discharge refrigerant from the discharge chamber 132. have.

In particular, the hole formed in the portion of the retainer 360 that faces the discharge port 332 of the valve plate 330 is composed of a central pressure margin hole 363 and a discharge communication hole 364 formed around the center hole.

Of course, a suction communication hole 365 is formed at a portion of the retainer 360 that faces the suction port 331 of the valve plate 330.

The domed shell valve 350 has a flat portion 358 that is bent outwardly around the convex portion 357. Accordingly, it does not damage the retainer 360 at the time of contact, it is possible to minimize the fluctuation of the self due to the discharge pressure of the refrigerant.

Furthermore, the edge of the flat portion 358 of the domed shell valve 350 is formed to be inclined 359 toward the convex portion 357, so that the damage of the retainer 360 by the fine burr during frequent contact is also increased. It can prevent.

On the other hand, an oil circulation groove 380 is formed on the opposite surface of the piston 200 side of the valve plate 330, a passage for raising oil accumulated at the bottom through the control valve 800 by the oil pump 910. Can be

In addition, a refrigerant circulation groove 390 is formed on the opposite surface of the piston 200 side of the valve plate 330 so that the refrigerant in the swash plate chamber serves as a flow passage when the refrigerant flows out through the passage in the drive shaft 140. can do.

The valve device and the domed shell valve according to the present invention can be applied to other swash plate compressors (the conventional compressors of FIG. 1) as shown in FIG. 9, and can be widely used in general reciprocating compressors in addition to the swash plate compressors.

According to the present invention having the above-described configuration, since the dome-shaped shell valve is moved between the valve plate and the retainer to open and close the discharge port of the valve plate, it is possible to minimize the dead volume caused by the space in the discharge port.

In addition, according to the present invention, when closed by the pressure of the discharged refrigerant, the response speed is faster than the conventional reed valve.

In addition, according to the present invention, since the streamlined discharge passage is formed when the discharge port is opened, the discharge speed from the cylinder bore is faster and smoother than the conventional discharge valve having a flat structure, thereby avoiding the pressure drop.

Further, according to the present invention, the discharge port of the valve plate has a valve seat tapered in the axial direction to facilitate the coupling of the dome type shell valve and excellent sealing property.

In addition, according to the present invention, a flat portion bent outwardly is formed around the convex portion of the domed shell valve, so that it does not damage the retainer upon contact and minimizes the fluctuation caused by the discharge pressure of the refrigerant.

In addition, according to the present invention, the flat edge of the domed shell valve is inclined toward the convex portion to prevent the retainer damage by the fine burr.

In addition, according to the present invention, the inner space of the discharge port is minimized and the sealing property is improved because it is formed by connecting two curvature of the domed shell valve.

In addition, according to the present invention, since the oil circulating groove or the refrigerant circulating groove is formed on the piston side facing surface of the valve plate, a separate passage is omitted, thereby simplifying the structure.

Claims (9)

A cylinder block having a housing, a plurality of cylinder bores, a piston accommodated reciprocally in the cylinder bore, a piston drive means for driving the piston, and a suction valve installed opposite the bottom of the piston; In the valve device of the reciprocating compressor comprising a valve device including a discharge valve, and a suction chamber and a discharge chamber formed in the housing via the valve device, A valve plate facing the bottom surface of the piston and having a plurality of inlets and outlets formed along a circumferential direction; A domed shell valve detachably installed at a discharge port on the discharge chamber side; And a retainer disposed to face the valve plate with the domed shell valve interposed therebetween. The method of claim 1, And a valve seat tapered in the axial direction at a discharge port facing the dome shell valve. 3. The method of claim 2, The domed shell valve, the valve device of the reciprocating compressor, characterized in that the flat portion is bent outwardly around the convex portion. The method of claim 3, The valve unit of the reciprocating compressor, characterized in that the flat edge of the domed shell valve is inclined toward the convex portion. 3. The method of claim 2, The domed shell valve is the valve device of the reciprocating compressor, characterized in that formed by connecting two surfaces having a curvature. The method of claim 5, The angle between the line connecting the boundary points of the two curvature surfaces and the tangent at the bottom point of the domed shell valve is the line connecting the boundary points of the two curvature surfaces and the end points of the curvature surfaces and the bottom point. The valve device of the reciprocating compressor, characterized in that 0.5 to 3 times the angle between the tangential line. The method of claim 6, Wherein said distance between the center of the first radius of curvature including the bottom point and the center of the second radius of curvature is in the range of 0 to 20% of the second radius of curvature. The method according to any one of claims 1 to 7, The valve device of the reciprocating compressor, characterized in that the oil circulation groove is formed on the piston side facing surface of the valve plate. The method according to any one of claims 1 to 7, The valve device of the reciprocating compressor, characterized in that a refrigerant circulation groove is formed on the piston side facing surface of the valve plate.

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