WO2004059167A1

WO2004059167A1 - Structure of reed valve for compressor

Info

Publication number: WO2004059167A1
Application number: PCT/JP2003/016639
Authority: WO
Inventors: Katsutaka Une
Original assignee: Zexel Valeo Climate Control Corporation
Priority date: 2002-12-26
Filing date: 2003-12-24
Publication date: 2004-07-15
Also published as: JPWO2004059167A1

Abstract

A reed valve having, without impairing the characteristics of a compressor, reduced pulsation noise caused by delayed opening of the valve and a structure that enables the valve to be produced at low costs. A compressor has a compression chamber, a suction chamber and a discharge chamber that are partitioned from the compression chamber by a valve plate (2), ports (16) provided in the valve plate (2) and respectively communicating between the compression chamber and the suction chamber and between the compression chamber and the discharge chamber, and reed valves (18) for opening and closing the ports (16). Band-like inclined faces (T) are formed along edges of the reed valves (18), on the faces opposite the valve plate (2).

Description

Satsuki Itoda β

Compressor reed valve structure

The present invention relates to a reed valve structure of a compressor mainly used for a vehicle air conditioner. Background art

Reed valves, which are opened by differential pressure, are often used as suction and discharge valves of compressors. Lubricating oil is interposed between the lead valve and the valve seat surface when the valve is closed, and the reed valve is strongly adhered to the valve seat by adhesive force. For this reason, the valve opening is delayed, and the suction and discharge become sharp due to the increased differential pressure, which causes pulsation. The generated pulsation propagates through the pipe and is amplified by the heat exchanger, resulting in noise.

As means for solving this problem, Japanese Patent Application Laid-Open No. 2000-54961 discloses that the contact area between a reed valve and a valve seat is reduced by roughening a lead valve or a valve seat. It is disclosed that.

Further, Japanese Patent Application Laid-Open No. Hei 7-180662 discloses that a contact surface with a reed valve is reduced by providing a concave portion or a convex portion in a valve seat.

Further, as shown in the cross-sectional view of FIG. 9, it is widely practiced to reduce the contact area between the lead valve V and the valve seat by forming a groove G in the valve seat around the port Ρ.

However, when the reed valve or valve seat is roughened, the processing cost for maintaining the roughness standard increases. In addition, the processing cost for maintaining the dimensions is high for the unevenness of the valve seat or the groove around the port.Especially in the case of the suction valve, these unevenness and the groove become the dead volume of the compression chamber and the performance is reduced. There was a problem of inviting.

The present invention has been made in view of such circumstances, and the characteristics of the compressor are as follows. It is an object of the present invention to provide a reed valve having a structure capable of reducing pulsation noise due to a delay in opening of a reed valve without deteriorating performance and capable of producing at low cost. Disclosure of the invention

The invention according to claim 1 of the present application is directed to a compression chamber, a suction chamber and a discharge chamber separated from the compression chamber by a valve plate, and the compression chamber, the suction chamber, and the discharge chamber provided in the valve plate. And a lead valve for opening and closing the port, wherein a band-like shape is formed along the edge of the lead valve on a surface of the lead valve facing the valve plate. This is a compressor lead valve structure characterized by forming a tapered surface.

According to the present invention, since the contact area between the lead valve and the valve seat surface is reduced by forming the tapered surface on the lead valve, the adhesive force by the lubricating oil is also reduced, and Pulsating noise due to delay in opening of the valve can be reduced. In addition, forming a tapered surface on a lead valve is easy to process and low in cost. Also, there is no extra capacity increase (very small) in the compression chamber, so there is no performance degradation.

The invention according to claim 2 of the present application is the invention according to claim 1, wherein the lead valve has a bar wrap portion that wraps around the port in a belt shape in a closed state, A compressor characterized in that the taper surface is provided at least in the overwrap portion, and the width of the taper surface is 50% or more of the width of the overlap portion. This is a reed valve structure.

Usually, the tip of the lead valve has a shape corresponding to the shape of the port, so that the tip of the lead valve overlaps with the periphery of the port in a band shape in the closed state. It has a burlap portion. In this case, if the tip of the reed valve is separated from the valve plate, the base of the reed valve is easily separated from the valve plate by the leverage principle. Therefore, it is sufficient that the taper surface is provided at least in this overlap portion. Then, in order to reduce pulsation noise due to delay in opening of the reed valve, it is desirable that the width of the taper portion is 50% or more of the width of the overlap portion. BRIEF DESCRIPTION OF THE FIGURES

Figure 1

1 is a cross-sectional view of a variable displacement swash plate type compressor according to a specific example of the present invention.

Figure 2

FIG. 3 is a side view showing a suction valve according to a specific example of the present invention.

Fig 3

FIG. 3 is a side view showing a discharge valve according to a specific example of the present invention.

Fig. 4

FIG. 4 is an enlarged view showing a discharge valve according to a specific example of the present invention.

Fig 5

FIG. 3 is an enlarged view showing a suction valve according to a specific example of the present invention.

Fig. 6

FIG. 3 is a cross-sectional view showing a suction valve and a suction port according to a specific example of the present invention.

Fig. 7

FIG. 2 is a sectional view showing a suction valve and a suction port according to a specific example of the present invention.

Fig. 8

FIG. 4 is a cross-sectional view showing a suction valve and a suction port according to a specific example of the present invention.

Fig. 9

FIG. 7 is a cross-sectional view showing a reed valve and a valve seat surface according to a conventional example. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, a specific example in which the present invention is applied to a variable displacement swash plate compressor will be described in detail with reference to the drawings.

FIG. 1 is a sectional view showing a variable displacement swash plate type compressor.

One end of the cylinder block 1 of this variable displacement swash plate compressor has a head 3 via a valve plate 2 and the other end of the cylinder Front heads 4 are fixed respectively.

The cylinder block 1 is provided with a plurality of cylinder bores 6 at predetermined intervals in the circumferential direction around the shaft 5. Each of these cylinder bores 6 is slidably accommodated with a steel 7.

A crank chamber 8 is formed in the front head 4, and a swash plate 10 is accommodated in the crank chamber 8. The swash plate 10 is slidably and tiltably mounted on the shaft 5 via a hinge ball 9.

The swash plate 10 is connected to the stone 7 through a pair of hemispherical shoes 50. The shroud 50 is relatively rotatable with respect to the front sliding surface 10b of the swash plate 10 and the sliding surface 10a of the swash plate 10 by the bridge portion 72 of the biston 7. Supported.

In the head 3, a discharge chamber 12 and a suction chamber 13 located around the discharge chamber 12 are formed.

The discharge chamber 12 and the crank chamber 8 communicate with each other via a gas introduction passage (not shown). A control valve 81 is provided in the middle of the gas introduction passage, and the flow rate of refrigerant from the discharge chamber 12 to the crank chamber 8 is controlled by the control valve 81.

The suction chamber 13 and the crank chamber 8 communicate with each other via a passage 58 provided in the cylinder block 1.

The valve plate 2 has a discharge port 15 for communicating the compression chamber 14 of the cylinder bore 6 with the discharge chamber 12, and a compression chamber of the cylinder bore 6. Suction ports 16 for communicating the suction chambers 14 with the suction chambers 13 are provided at predetermined intervals in the circumferential direction. The discharge port 15 is opened and closed by a discharge valve 17, and the suction port 16 is opened and closed by a suction valve 18.

A thrust flange 40 for transmitting the rotation of the shaft 5 to the swash plate 10 is fixed to the front end of the shaft 5, and the thrust flange 40 is connected to a thrust bearing 33 via a thrust bearing 33. And is rotatably supported on the inner wall of the front head 4.

The thrust flange 40 and the swash plate 10 are connected via a link mechanism 41 so that the top dead center of piston 7 remains constant even if the inclination angle of the swash plate 10 changes. Have been.

The piston 7 is a bridge that connects the cylindrical head portion 71 fitted into the cylinder bore 6 to the head portion 71 and the swash plate 10 via a shoe 50. And a bridge section 72. The bridge section 72 is provided integrally with the head section 71.

A hollow portion 3 for weight reduction is formed in the head portion 71, and a shoe receiving portion 75 for rollingly supporting the shoe 50 is formed in the bridge portion 72. I have.

Next, the operation of the variable displacement type swash plate type compressor will be described.

When the rotational power of the vehicle engine (not shown) is transmitted to the shaft 5, the rotating force of the shaft 5 is transmitted to the swash plate 10 via the thrust flange 40 and the link mechanism 41, and the swash plate 10 rotates. I do.

The rotation of the swash plate 10 causes the shafts 50 and 50 to relatively rotate on the sliding surfaces 10 a and 10 b of the swash plate 10. Converted to a linear reciprocating movement of 7 tons.

The piston 7 reciprocates in the cylinder bore 6, and as a result, the volume of the compression chamber in the cylinder bore 6 changes. This volume change causes the suction, compression and discharge of the refrigerant gas to be performed sequentially, and the swash plate 10 High-pressure refrigerant gas having a capacity corresponding to the inclination angle of the gas is discharged. At the time of suction, the suction valve 18 opens, and low-pressure refrigerant gas is sucked from the suction chamber 13 into the compression chamber 14 in the cylinder bore 6 via the suction port 16, and at the time of discharge, the discharge valve 17 is opened. When opened, high-pressure refrigerant gas is discharged from the compression chamber 14 to the discharge chamber 12 through the discharge port 15.

When the heat load decreases, the control valve 81 increases the cross-sectional area of the gas introduction passage. Therefore, high-pressure refrigerant gas flows from the discharge chamber 12 to the crank chamber 8 via the gas introduction passage, the pressure in the crank chamber 8 increases, and the inclination angle of the swash plate 10 decreases.

On the other hand, when the heat load is increased, the cross-sectional area of the gas introduction passage is reduced by the control valve 81. Therefore, the inflow of high-pressure refrigerant gas from the discharge chamber 12 to the crank chamber 8 is suppressed, the pressure in the crank chamber 8 decreases, and the inclination angle of the swash plate 10 increases. FIG. 2 is a side view showing a suction valve, and FIG. 3 is a side view showing a discharge valve. Each of the suction valve 18 and the discharge valve 17 is a lead valve that opens and closes by a differential pressure, and is formed by stamping a thin plate material by press working. The suction valve 18 is fixed to the cylinder block 1 of the valve plate 2, and the discharge valve 17 is fixed to the valve head 3 of the valve plate 2.

In the suction valve 18, a tongue-shaped lead is formed by punching a U-shaped hole 19, and a hole corresponding to the discharge port 15 is punched.

As shown in FIGS. 4 and 5, the tip of the tongue-shaped lead of the discharge valve 17 and the suction valve 18 is attached to the surface facing the valve plate 2 and, as shown by hatching, to the edge. A tape-shaped tapered surface T is formed along the tapered surface T. The tapered surface T is formed by press working.

The following description is given taking the suction valve 18 as an example, but the same applies to the discharge valve 17.

FIG. 6 is a cross-sectional view showing the suction valve and the suction port in a closed state. The width B of the taper surface is preferably 50% or more of the width A of the overlapped portion, and more preferably 70% or more. In the drawings, for convenience of explanation, Although the tapered surface T is exaggerated, the actual thickness of the suction valve 18 is 0.3 to 0.4 mm, but the distance between the taper surface T and the valve plate 2 C is in the range of 0.03 to 0.05 mm, and the taper angle 0 of the taper surface T is 4 to 6 °.

Most preferably, the width of the tapered surface is equal to the width of the overlap portion as shown in FIG. In this case, the contact area between the suction valve 18 and the valve plate 2 is practically zero ', but as shown in Fig. 8, when the valve is closed, the suction valve 18 radiates due to the differential pressure and the suction port The airtightness is maintained by the taper surface T contacting the edge of the step 16.

In this example, the tapered surface T is provided only on the overlap portion of the suction valve 18 and the discharge valve 17, but a taper surface may be provided on all the shear surfaces of the suction valve and the discharge valve.

The processing of the tapered surface T is not limited to the breath processing, but may be another processing method.

As described above, according to the lead valve structure of the compressor of the present embodiment, the contact area between the lead valve and the valve seat surface is reduced by forming the taper surface on the lead valve. Therefore, the adhesive force due to the lubricating oil is also reduced, and pulsation noise due to the delay in opening of the lead valve can be reduced. In addition, forming a tapered surface on the lead valve is low in cost because of easy processing. Also, there is no extra volume increase (very small) in the compression chamber, so there is no performance degradation. Industrial applicability

INDUSTRIAL APPLICATION This invention can be utilized especially for the compressor used for the air conditioner for vehicles or household appliances.

Claims

Scope of Word

1. a compression chamber, a suction chamber and a discharge chamber separated from the compression chamber by a valve plate, a port provided in the valve plate for communicating the compression chamber with the suction chamber and the discharge chamber, and the port And a lead valve for opening and closing the

A band-shaped taper surface is formed on a surface of the reed valve facing the valve plate along an edge of the reed valve.

2. When the reed valve is in the closed state, the reed valve has an overlapping portion that overlaps in a band shape around the periphery of the port, and the taper surface is provided at least in the overlapping portion, The lead valve structure for a compressor according to claim 1, wherein a width of the taper surface is 50% or more of a width of the overwrap portion.