KR20050096238A - Variable capacity swash plate type compressor - Google Patents

Abstract

The present invention relates to a variable displacement swash plate compressor, and more particularly, to improve the performance of the compressor by maintaining the top clearance of the piston at the minimum and maximum inclination angle of the swash plate in coupling the swash plate to the drive shaft. The present invention also relates to a variable capacity swash plate type compressor having improved productivity by easily processing and assembling swash plate.

Accordingly, the present invention is connected to one side of the rotor 160 mounted on the drive shaft 150 and the swash plate 170 is installed to change the inclination angle corresponding to the pressure change of the crank chamber 121, the swash plate 170 of the The hub pin 172 is coupled to the through hole 171 to be orthogonal to the driving shaft 150 to support the swash plate 170 so that the inclination angle can be adjusted with respect to the driving shaft 150. In the variable displacement swash plate type compressor comprising a plurality of pistons 140 reciprocating in the cylinder bore 111 in conjunction with rotation in the suction, compression and discharge of the refrigerant, the hub coupled to the through hole 171 The position of the pin 172 is to maintain the top clearance of the piston 140 at the minimum inclination angle (αmin) and maximum inclination angle (αmax) of the swash plate 170, the following equation , It is characterized in that determined by.

Description

Variable capacity swash plate type compressor

The present invention relates to a variable displacement swash plate compressor, and more particularly, to improve the performance of the compressor by maintaining the top clearance of the piston at the minimum and maximum inclination angle of the swash plate in coupling the swash plate to the drive shaft. The present invention also relates to a variable capacity swash plate type compressor having improved productivity by easily processing and assembling swash plate.

Compressor constituting the automotive air conditioner is a device that selectively receives the power from the power source by the intermittent action of the electromagnetic clutch to suck the refrigerant gas from the evaporator to the inside to compress by the linear reciprocating motion of the piston to discharge to the condenser. These compressors are divided into various types according to the compression method and structure, and among these compressors, variable capacity compressors that can change the compression volume are also widely used.

Hereinafter, a conventional general variable displacement swash plate compressor will be described with reference to FIG. 1.

The variable displacement swash plate compressor 1 is provided with a cylinder block 10 having a plurality of cylinder bores 11 formed in an axial direction along a concentric circle, and a crank chamber 21 installed inside the cylinder block 10 in front of the cylinder block 10. A front housing 20 forming a rear housing, a rear housing 30 installed at a rear side of the cylinder block 10 to form a refrigerant suction chamber 31 and a refrigerant discharge chamber 32 therein, and the cylinder block. A plurality of pistons 40 are reciprocally inserted into the respective cylinder bores 11 of FIG. 10, and a bridge 41 is formed at the rear end thereof, and one end thereof rotatably penetrates the front housing 20, and the rear end portion thereof. A drive shaft 50 inserted into the center of the cylinder block 10 to be rotatably supported, and a rotor 60 coupled to the drive shaft 50 inside the crank chamber 21 to rotate together with the drive shaft 50. And a bush or hub pin 72 around the drive shaft 50 to enable flow. And an edge thereof is rotatably coupled to the insertion space of the piston 40 bridge 41 via the shoe 42, and the center of the front upper end is hinged 73 to the rotor 60 so as to be connected to the rotor 60. It is installed between the swash plate 70 and the cylinder block 10 and the rear housing 30 to be tilted with respect to the drive shaft 50 while rotating together, from the refrigerant suction chamber 31 to the cylinder bore 11. And a valve unit 80 for sucking the refrigerant and discharging the compressed refrigerant from the cylinder bore 11 to the refrigerant discharge chamber 32.

In addition, the inclination angle of the swash plate 70 with respect to the drive shaft 50 is adjusted according to the pressure change in the crank chamber 21 by the control valve 90 installed in the rear housing 30.

On the other hand, the spring 51 interposed in the drive shaft 50 between the rotor 60 and the swash plate 70 to support the swash plate 70 with respect to the rotor 60 to return the swash plate 70 to its initial position. It works.

As described above, the variable displacement swash plate compressor (1), the plurality of pistons (40) arranged along the concentric circle of the cylinder block 10 by the rotation of the swash plate 70 sequentially performs the front and rear reciprocating motion Done. At the time of the suction stroke of the piston 40 from the cylinder bore 11, the suction valve (not shown) of the valve unit 80 is opened by the pressure drop inside the cylinder bore 11 to open the cylinder bore 11. ) And the refrigerant suction chamber 31 communicate with each other so that the refrigerant flows into the cylinder bore 11 from the refrigerant suction chamber 31.

In the compression stroke from the cylinder bore 11, the refrigerant is compressed by an increase in the pressure inside the cylinder bore 11, and a discharge valve (not shown) of the valve unit 80 is opened to open the cylinder bore 11. ) And the refrigerant discharge chamber 32 communicate with each other, so that the compressed refrigerant is discharged from the cylinder bore 11 to the refrigerant discharge chamber 32. In addition, since the inclination angle of the swash plate 70 is adjusted in response to the pressure difference between the pressure in the crank chamber 21 and the suction pressure in the cylinder bore 11, the discharge capacity of the compressor 1 is variable.

Meanwhile, a through hole 71 having a diameter larger than the diameter of the drive shaft 50 is formed at the center of the swash plate 70 and the direction perpendicular to the drive shaft 50 is formed in the through hole 71. As the hub pins 72 are coupled to each other, the outer circumferential surface of the hub pins 72 is in contact with the outer circumferential surface of the drive shaft 50 and is configured to minimize swinging when the swash plate 70 rotates.

However, in determining the position of the hub pin 72 coupled to the through-hole 71 of the swash plate 70 when the position of the hub pin 72 is determined according to the maximum inclination angle of the swash plate 70, that is, If the position of the outer circumferential surface of the hub pin 72 is in contact with the outer circumferential surface of the drive shaft 50 at the maximum inclination angle of the swash plate 70, the swash plate 70 is minimized when the rotation is rotated at the maximum inclination angle, swash plate When the 70 is gradually changed to the minimum inclination angle, the gap between the hub pin 72 and the drive shaft 50 increases, causing oscillation during rotation of the swash plate 70 at the minimum inclination angle.

On the contrary, if the position of the hub pin 72 is determined at the minimum inclination angle of the swash plate 70, a problem also occurs when the swash plate 70 is changed to the maximum inclination angle.

When the swash plate 70 oscillates, the stroke distance of the piston 40 becomes irregular and at the same time, the top clearance of the piston 40 increases, and at the minimum inclination angle of the swash plate 70, the piston ( If the top clearance of 40) is increased, there is a problem in that the refrigerant is not compressed during initial operation of the compressor (1), so that sufficient refrigerant compression cannot be exerted, and the top clearance of the piston (40) may increase at the maximum inclination angle. In this case, when the idle of the vehicle (idle) can not exhibit sufficient compressor (1) performance, there is a problem that power loss occurs and at the same time can not obtain sufficient air conditioning performance.

In addition, since the two through-holes must be formed in the through-hole 71 of the swash plate 70 to couple the two hub pins 72 to the upper and lower ends of the drive shaft 50, processing of the swash plate 70 is cumbersome. In addition, there was a disadvantage that a high frequency heat treatment should be added to the through hole.

An object of the present invention for solving the above-mentioned problems is to determine the position of the hub pin to maintain the top clearance of the piston at a constant minimum and maximum inclination angle of the swash plate in coupling the swash plate to the drive shaft It is to provide a variable capacity swash plate type compressor which improves productivity by minimizing fluctuations in the rotation of the swash plate, improving the performance of the compressor, and easily processing and assembling the swash plate.

The present invention for achieving the above object is connected to one side of the rotor mounted on the drive shaft and is provided with a swash plate to change the inclination angle in response to the pressure change of the crank chamber, coupled to the orthogonal to the drive shaft in the through hole of the swash plate The hub pin is installed to support the swash plate to be able to adjust the inclination angle with respect to the drive shaft, and comprises a plurality of pistons reciprocating in the cylinder bore in conjunction with the rotation of the swash plate variable to suck, compress and discharge the refrigerant In the capacitive swash plate type compressor, the position of the hub pin coupled to the through hole is such that the top clearance of the piston can be kept to a minimum at the minimum and maximum inclination angles of the swash plate. , It is characterized in that determined by.

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

Repeated description of the same construction and operation as in the prior art will be omitted.

Figure 2 is a cross-sectional view showing a variable displacement swash plate compressor according to the present invention, Figure 3 is a perspective view showing a state in which the rotor and the swash plate coupled to the drive shaft in the variable displacement swash plate compressor according to the present invention, Figure 4 5 is a cross-sectional view for designing the position of the hub pin in the variable displacement swash plate compressor according to the present invention.

As shown, the variable displacement swash plate compressor 100 according to the present invention is provided with a cylinder block 110 formed with a plurality of cylinder bores 111 in the axial direction along the concentric circle, the front of the cylinder block 110 A front housing 120 is formed at the side to form a crank chamber 121, and a rear housing is formed at the rear side of the cylinder block 110 to form a refrigerant suction chamber 131 and a refrigerant discharge chamber 132 therein. 130) is installed.

Each of the cylinder bores 111 of the cylinder block 110 is reciprocally inserted and a plurality of pistons 140 having a bridge 141 formed at the rear end thereof are installed.

Then, one end is rotatably penetrating the front housing 120, the rear end is inserted into the center of the cylinder block 110 is installed a drive shaft 150 is rotatably supported.

In addition, a rotor 160 coupled to the drive shaft 150 in the crank chamber 121 and rotating together with the drive shaft 150 is installed, and the drive shaft 150 is disposed inside the crank chamber 121. A through hole 171 through which the drive shaft 150 passes in the center is formed to be movable along the edge thereof, and an edge thereof is rotatably coupled via the shoe 142 to the insertion space of the bridge 140 and the piston 140. A swash plate 170 is installed, the center of which is hinged to the rotor 160 and rotates with the rotor 160 to adjust the inclination angle with respect to the drive shaft 150.

Then, it is installed between the cylinder block 110 and the rear housing 130 to suck the refrigerant from the refrigerant suction chamber 131 to the cylinder bore 111 and to compress the refrigerant from the cylinder bore 111 to the refrigerant discharge chamber 132. A valve unit 180 for discharging the gas is installed.

In addition, the rear housing 130 is provided with a control valve 190 to operate the refrigerant discharge chamber 132 and the crank chamber 121 to communicate with the refrigerant suction pressure and the crank chamber (11) in the cylinder bore (111). The inclination angle of the swash plate 170 is adjusted by varying the pressure difference with the gas pressure in 121.

On the other hand, the spring 155 interposed in the drive shaft 150 between the rotor 160 and the swash plate 170 to support the swash plate 170 with respect to the rotor 160 to return the swash plate 170 to the initial position It works.

In the variable displacement swash plate type compressor, the through-hole 171 of the swash plate 170 is located at the lower end of the drive shaft 150 and the hub pin 172 orthogonal to the drive shaft 150 is coupled.

The hub pin 172 is configured to change the inclination angle of the swash plate 170 while the outer circumferential surface is in contact with the outer circumferential surface of the drive shaft 150 and minimizes the fluctuation during rotation of the swash plate 170.

Here, the hub pin 172 may omit a separate high frequency heat treatment process using a roller of the needle roller bearing.

On the other hand, the compressor 100 should be designed so that the swash plate 170 coupled to the drive shaft 150 is minimized at the minimum and maximum inclination angle to uniform the stroke distance of the piston 140 and at the same time the swash plate 170 The top clearance of the piston 140 can be kept to a minimum under the minimum inclination angle and the maximum inclination angle condition. This will soon improve the compression efficiency of the refrigerant to improve the performance of the compressor (100).

Therefore, the present invention constantly minimizes the top clearance of the piston 140 at the minimum inclination angle and the maximum inclination angle of the swash plate 170 to the position of the hub pin 172 coupled to the through hole 171 of the swash plate 170. In order to keep it as follows, it is determined by the following equation.

As shown in FIG. 5, the axial distance from the center of rotation of the swash plate 170 to the center of the hub pin 172 is referred to as Px, and from the center of rotation of the swash plate 170 to the center of the hub pin 172. The axially perpendicular distance is Py, the diameter of the drive shaft 150 is D, the diameter of the hub pin 172 is d, the minimum inclination angle of the swash plate 170 is αmin, the maximum inclination angle of the swash plate 170 is αmax, and the hub is at the minimum inclination angle. If the angle to the center of the pin 172 is β, the distance from the center of rotation of the swash plate 170 to the center of the hub pin 172 is L,

When the L value is the shortest, the clearance between the driving shaft 150 and the hub pin 172 is the smallest and the shaking of the swash plate 170 can be minimized. In addition, the top clearance of the piston 140 at the minimum inclination angle αmin and the maximum inclination angle αmax of the swash plate 170 should be the smallest difference between the L value at the minimum inclination angle αmin and the L value at the maximum inclination angle αmax. It can be kept constant to a minimum, which can be seen that the optimal value is located in the center angle between the hub pin 172 is the minimum inclination angle (αmin) and the maximum inclination angle (αmax).

Therefore, in the present invention, the position of the center of the hub pin 172 with respect to the rotation center of the swash plate 170 is derived from the following relationship.

First, the angle β formed from the minimum inclination angle αmin of the swash plate 170 to the center of the hub pin 172 is expressed by Equation 1 below.

That is, it can be seen that the angle β is the central angle between the minimum inclination angle αmin and the maximum inclination angle αmax.

Subsequently, when the β value is obtained in Equation 1, the distance L from the rotation center of the swash plate 170 to the center of the hub pin 172 may be obtained through Equation 2 below.

Thus, when β and L values are obtained through Equations 1 and 2, the axial distance Px from the rotation center of the swash plate 170 to the center of the hub pin 172, and the axial perpendicular distance Py Can be obtained through the following equations (3) and (4).

Subsequently, when Equation 2 is substituted for Equation 3 and Equation 4, the following equation (5) is obtained.

On the other hand, in the state in which the swash plate 170 is vertically fixed to the drive shaft 150 inclined to rotate the drive shaft 150 on the basis of the line connecting the rotation center of the swash plate 170 and the center of the hub pin 172. When the minimum inclination angle and the maximum inclination angle of) are drawn by lines 150a and 150b, respectively, the outer circumferential surface of the hub pin 172 is in contact with the minimum and maximum inclination angle lines 150a and 150b of the driving shaft 150. It is preferable.

As described above, when the equation 5 is satisfied, fluctuation is minimized at the minimum inclination angle αmin and the maximum inclination angle αmax of the swash plate 170 when the swash plate 170 rotates, so that the top clearance of the piston 140 is minimized. Can be kept constant to a minimum.

This is because the hub pin 172 coupled to the swash plate 170 is coupled to a position that satisfies both of the minimum inclination angle αmin or the maximum inclination angle αmax of the swash plate 170, thereby initially driving the compressor 100. Both of the above conditions when the vehicle (idle) and the vehicle (idle) exhibits a sufficient refrigerant compression action to improve the performance of the compressor 100 and at the same time can achieve sufficient air conditioning performance.

In the present invention, by combining the hub pin 172 to the lower end of the drive shaft 150 to the through hole 171 of the swash plate 170 to support the rotation of the swash plate 170 by processing and Easy to assemble

In addition, a hub pin (not shown) may also be coupled to the through hole 171 of the swash plate 170 to the upper side of the driving shaft 150 to reduce the gap between the driving shaft 150 and the hub pin 172. have.

According to the present invention, in coupling the swash plate to the drive shaft by determining the position of the hub pin to maintain the top clearance of the piston at a constant minimum minimum and maximum inclination angle of the swash plate to the minimum inclination angle during rotation of the swash plate In addition, the fluctuation is minimized at the maximum inclination angle, so that the stroke length of the piston is uniform, and the top clearance of the piston is kept at a constant minimum, so that the compressor performance is improved and the performance of the air conditioner is improved by sufficient refrigerant compression.

In addition, the swash plate can be easily processed and assembled to improve productivity.

1 is a cross-sectional view showing a conventional variable displacement swash plate compressor;

2 is a cross-sectional view showing a variable displacement swash plate compressor according to the present invention;

3 is a perspective view illustrating a state in which a rotor and a swash plate are coupled to a drive shaft in a variable displacement swash plate compressor according to the present invention;

4 is a cross-sectional view of FIG.

5 is a view for the position design of the hub pin in the variable displacement swash plate compressor according to the present invention.

<Description of Signs of Major Parts of Drawings>

100: compressor 110: cylinder block

111: cylinder bore 120: front housing

121: crankcase 130: rear housing

131: refrigerant suction chamber 132: refrigerant discharge chamber

140: piston 141: bridge

142: shoe 150: drive shaft

150a: minimum inclination line of the drive shaft

150b: Maximum inclination line of the drive shaft

155: spring 160: rotor

170: swash plate 171: through hole

172: hub pin 173: hinge

180: valve unit 190: control valve

Claims (2)

The swash plate 170 is connected to one side of the rotor 160 mounted on the drive shaft 150 and the inclination angle is changed in response to the pressure change of the crank chamber 121, and the through hole 171 of the swash plate 170 is provided. Is coupled to the drive shaft 150 orthogonal to the hub pin 172 is installed to support the swash plate 170 to adjust the inclination angle with respect to the drive shaft 150, in conjunction with the rotation of the swash plate 170 In the variable capacity swash plate compressor comprising a plurality of pistons 140 reciprocating in the cylinder bore 111 to suck, compress and discharge the refrigerant, The position of the hub pin 172 coupled to the through hole 171 may maintain the top clearance of the piston 140 at the minimum inclination angle αmin and the maximum inclination angle αmax of the swash plate 170, Variable displacement swash plate compressor characterized by the following equation. Where Px is the axial distance from the center of rotation of the swash plate to the center of the hub pin, Py is the axial perpendicular distance from the center of rotation of the swash plate to the center of the hub pin, D is the diameter of the drive shaft, d is the diameter of the hub pin, β is the angle from the minimum inclination angle to the center of the hub pin, αmin is the minimum inclination angle of the swash plate. The method of claim 1, The hub pin 172 is a variable capacity swash plate compressor, characterized in that made of a roller of the needle roller bearing.