KR20090118513A - Swash pate type compressor - Google Patents

Abstract

PURPOSE: A swash plate type compressor is provided to prevent a weight center from being farther from the center of a driving axis to reduce rotation balance, thereby reducing vibration and noise. CONSTITUTION: A swash plate type compressor includes a driving axis(140), a lug plate, a swash plate(160), and a piston. Driving power of an engine is transferred to the driving axis. The lug plate is installed in the driving axis. The swash plate is combined with the lug plate. The piston is combined with the swash plate to reciprocate a cylinder bore.

Description

Swash plate type compressor {Swash pate type compressor}

The present invention relates to a swash plate type compressor, and more particularly, to a swash plate type compressor which minimizes a change in the center of gravity of the swash plate even when the inclination angle of the swash plate is varied by moving the rotational center of the swash plate.

In general, a vehicle air conditioner is a device for maintaining a temperature inside a car lower than an external temperature by using a refrigerant, and includes a compressor, a condenser, and an evaporator to configure a circulation cycle of the refrigerant. Here, the compressor is driven by the power of the engine as a device for compressing and pumping the refrigerant.

Such a compressor has a disc-shaped swash plate installed on a drive shaft to which engine power is transmitted so that the inclination angle is variable in response to rotation of the drive shaft, and a shoe is fitted along a circumference of the swash plate by the rotation of the swash plate. The plurality of pistons are configured to suck, compress and discharge the refrigerant gas by linearly reciprocating the inside of the plurality of cylinder bores formed in the cylinder block.

Hereinafter, a coupling structure of a swash plate for a compressor according to the prior art will be described with reference to the drawings.

1 is an exploded perspective view showing a coupling structure of a swash plate for a compressor according to the prior art, Figure 2 is a cross-sectional view of Figure 1, Figure 3 is a schematic diagram showing a change in the center of gravity according to the change in the inclination angle of the swash plate according to the prior art to be.

1 to 2, the coupling structure of the swash plate for the compressor according to the prior art, the drive shaft 10 and the hub 20 is formed with a drive shaft coupling hole 21 corresponding to the drive shaft 10 and It is composed of a swash plate 30 that is coupled to the hub (20).

In addition, the drive shaft 10 has a long hole 11 is formed, the hub 20 is provided with a shaft coupling portion 22 is formed with a pin coupling hole 23 penetrated outward to correspond to the long hole (11). The pin coupling hole 23 and the long hole 11 are sequentially inserted into the coupling pin 27.

On the other hand, the shaft coupling portion 22 is formed to protrude in the direction of the swash plate 30 is inserted into the hollow 31 of the swash plate 30 is fastened.

In addition, an arm 24 is formed in a direction opposite to the swash plate 30 so that the hub 20 is hinged to the lug plate (not shown), and the arm 24 and the lug plate (not shown) are hinged to each other. The hinge pin 25 is provided.

On the other hand, the pin coupling hole 23 and the coupling pin 27 is formed to match the center (C) of the swash plate (30).

In addition, the hub 20 is provided with a counterweight 26 at the opposite end of the arm 24 to prevent the center of gravity from being oriented in one direction by the arm 24.

Accordingly, the swash plate 210 installed on the drive shaft 10 rotates about the pin coupling hole 23 and the coupling pin 25 while sliding in the axial direction of the drive shaft 10 while rotating. Variable.

However, the coupling structure of the swash plate for the compressor according to the prior art, as shown in Figures 2 to 3, the swash plate 30 coupled to the hub 20 based on the rotation center (C) while the drive shaft 10 is rotated ), While the inclination angle is variable, the positions of the upper center of gravity L1 formed on the arm 24 and the lower center of gravity L2 formed on the balance weight 26 change.

That is, as the inclination angle of the swash plate 30 changes, the upper center of gravity L1 and the lower center of gravity L2 move more than the center of gravity before the inclination angle of the swash plate changes, thereby increasing the rotation balance. Vibration and noise of the compressor is a problem that occurs.

The present invention has been made to solve the above problems, the object of the present invention is to move the rotational center of the swash plate to reduce the rotational balance by preventing the center of gravity away from the center of the drive shaft even if the inclination angle of the swash plate is variable vibration And to provide a swash plate compressor to reduce the generation of noise.

The swash plate compressor of the present invention for achieving the above object, the drive shaft to which the driving force of the engine is transmitted, the lug plate is installed on the drive shaft, the swash plate coupled to the lug plate, coupled to the swash plate reciprocating cylinder bore In the swash plate-type compressor including a piston that is coupled to the swash plate, the swash plate has an axial sliding motion and a rotational motion with respect to the drive shaft when the inclination angle is changed, and a center point of the rotational motion is more than a center of the thickness of the swash plate thickness. It is characterized by the deviation in the plate direction.

Here, the swash plate is formed with a guide groove, the sleeve is further provided with a coupling pin is inserted into the guide groove, the coupling pin is preferably a center point of the rotational movement of the swash plate.

In addition, the swash plate is hollow is formed, the hub having a shaft coupling portion corresponding to the hollow is further provided, the hub is formed with a pin coupling hole, the drive shaft is formed with a long hole corresponding to the pin coupling hole, A coupling pin is further provided to be coupled to the pin coupling hole and the long hole, the coupling pin is preferably a center point of the rotational movement of the swash plate.

In addition, a pin coupling hole is formed in the swash plate, and a long hole corresponding to the pin coupling hole is formed in the drive shaft, and a coupling pin coupled to the pin coupling hole and the long hole is further provided. It is preferable that it is the center point of rotational movement.

According to the swash plate type compressor according to the present invention, even if the inclination angle of the swash plate is changed by moving the rotational center of the swash plate to prevent the center of gravity away from the center of the drive shaft to reduce the rotation balance provides an effect of reducing the occurrence of vibration and noise do.

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

4 is a cross-sectional view showing a swash plate compressor according to the present invention.

First, the variable displacement swash plate compressor will be described to help the understanding of the present invention.

As shown in FIG. 3, the variable displacement swash plate type compressor A includes a cylinder block 110 having a plurality of cylinder bores 110a formed in parallel in a longitudinal direction on an inner circumferential surface thereof and constituting an outside of the compressor; The front housing 120 disposed at the front end of the cylinder block 110 to form the swash plate chamber 120a, and the suction chamber 132 and the discharge chamber 133 are formed therein, and the cylinder block 110 It consists of a rear housing 130 disposed at the rear end of the.

Here, the cylinder block 110 and the front housing 120 is provided with a drive shaft 140 that is rotatably supported, the drive shaft 140 is fixed to the lug plate 150 is installed, the lug plate 150 In combination with the swash plate 160 is provided so that the inclination angle can be changed while rotating.

In addition, a spring 170 is provided between the lug plate 150 and the swash plate 160.

In addition, the piston 180 is coupled to the swash plate 160 is provided to allow the reciprocating movement in the cylinder bore (110a), the piston 180 is capable of sliding with the swash plate 160 Reciprocating movement in the cylinder bore 110a is possible by the shoe 181 to be coupled.

In addition, a valve plate 131 is provided between the cylinder block 110 and the rear housing 130, and the inlet port 131a communicates the cylinder bore 110a and the suction chamber 132 to the valve plate 131. And an outlet 131b for communicating the cylinder bore 110a and the discharge chamber 133, respectively.

In addition, the suction port 131a and the discharge port 131b formed in the valve plate 131 may be suctioned to open and close the suction port 131a and the discharge port 131b by a pressure change caused by the reciprocating motion of the piston 180. A valve (not shown) and a discharge valve (not shown) are provided respectively.

Therefore, when the rotational power is transmitted through the engine and the pulley to rotate the drive shaft 140, accordingly, the power transmission lug plate 150 fixed to the drive shaft 140 (pressing, etc.) is rotated and the lug plate is rotated. The swash plate 160 coupled with 150 receives power to make a rotational movement while varying the inclination angle.

In addition, as the piston 180 reciprocates in the cylinder bore 110a due to the rotation of the swash plate 160, the refrigerant gas is sucked from the suction chamber 132 and compressed in the cylinder bore 110a. Discharge from the discharge chamber 133 is performed continuously. At this time, the control of the discharged refrigerant gas is made by a pressure control valve (not shown).

Hereinafter, in describing the coupling structure of the swash plate to minimize the rotation balance of the present invention, the same reference numerals are used for the above-described components and components, and redundant descriptions are omitted.

5 is an exploded perspective view showing a coupling structure of the swash plate for the compressor according to the first embodiment of the present invention, Figure 6 is a cross-sectional view showing a coupling structure of the swash plate for the compressor of FIG.

5 to 6, the coupling structure of the swash plate for the compressor according to the first embodiment of the present invention, the drive shaft 140, the sleeve 190 is coupled to the drive shaft 140, and the sleeve Consists of a swash plate 160 coupled with 190.

Here, the guide plate 161 is formed on both sides of the swash plate 160, and the coupling pin 191 is inserted into the guide groove 161 in the sleeve 190.

In addition, the swash plate 160 is formed with an insertion hole 162 into which the sleeve 190 is inserted, and the coupling hole 192 into which the driving shaft 140 is inserted is formed in the sleeve 190.

In addition, an outer surface of the sleeve 190 adjacent to the insertion hole 162 of the swash plate 160 is formed as a convex curved surface.

In addition, the swash plate 160 is formed with an arm 163 hinged to the lug plate 150, the counterweight 164 is formed at the opposite end of the arm 163.

On the other hand, when the swash plate compressor (A) described above is driven, vibration and noise are generated according to the change of the inclination angle of the swash plate 160.

In order to prevent vibration and noise caused by the change of the inclination angle of the swash plate 160, the amount of change in the rotation balance of the swash plate 160 should be reduced. Therefore, the center of rotation C of which the inclination angle of the swash plate 160 changes is shifted forward than the center of the thickness of the swash plate 160, and the distance at which the center of rotation C is biased is represented by (d).

Here, the center of rotation (C) of the swash plate 160 is a coupling pin 191 formed on both sides of the sleeve 190, to bias the coupling pin 191 forward than the center of the thickness of the swash plate 160 In order to form the guide groove 161 to be deflected forward.

Therefore, as the coupling pin 191 coupled to the guide groove 161 is also biased forward, the rotational center C of the swash plate 160 is also biased forward to change the amount of change in rotational balance of the swash plate 160. Reduces the vibration and noise of the swash plate compressor (A).

Hereinafter, another embodiment of the present invention will be described. For the same reference numerals, the same reference numerals are used for the same reference numerals as those of the first embodiment.

7 is an exploded perspective view showing a coupling structure of the swash plate for the compressor according to the second embodiment of the present invention, Figure 8 is a cross-sectional view showing a coupling structure of the swash plate for the compressor of FIG.

As shown in Figures 7 to 8, the coupling structure of the swash plate for the compressor according to the second embodiment of the present invention, the drive shaft 140 'and the hub 190' coupled to the drive shaft 140 'and And a swash plate 160 'coupled to the hub 190'.

 Here, the hollow 161 'is formed in the swash plate 160', and the shaft 190 'has a shaft coupling portion 192' corresponding to the hollow 161 '.

In addition, a driving shaft coupling hole 193 'is formed through the hub 190' to be coupled to the driving shaft 140 '.

A long hole 141 'is formed in the drive shaft 140', and a pin coupling hole 194 'corresponding to the long hole 141' is formed in the hub 190 ', and the long hole 141' is formed. ) And the pin coupling hole 194 'is sequentially inserted into the coupling pin 191'.

In addition, an arm 195 'hinged to the lug plate 150 is formed at the hub 190', and a counterweight 196 'is formed at an opposite end of the arm 195'.

On the other hand, when the swash plate compressor (A) described above is driven, vibration and noise are generated according to the change in the inclination angle of the swash plate 160 ′.

In order to prevent vibration and noise caused by the change of the inclination angle of the swash plate 160 ', the amount of change in the rotation balance of the swash plate 160' should be reduced. Therefore, the rotational center C 'in which the inclination angle of the swash plate 160' is changed is shifted forward than the center of the thickness of the swash plate 160 ', and the distance at which the rotation center C' is biased is (d '). As shown.

Here, the rotational center C 'of the swash plate 160' is a coupling pin 191 'coupled to the pin coupling hole 194' and the long hole 141 ', and the coupling pin 191' is The pin coupling hole 194 'of the hub 190' is formed on the front outer circumferential surface of the shaft coupling portion 192 'in order to shift forwardly from the center of the swash plate 160'.

Therefore, as the coupling pin 191 'coupled to the pin coupling hole 194' is also biased forward, the center of rotation C 'of the swash plate 160' is biased forward and thus, of the swash plate 160 '. By reducing the amount of change in the rotation balance, it reduces the vibration and noise of the swash plate compressor (A).

9 is an exploded perspective view showing a coupling structure of the swash plate for the compressor according to the third embodiment of the present invention, Figure 10 is a cross-sectional view showing a coupling structure of the swash plate for the compressor of FIG.

9 to 10, the coupling structure of the swash plate for the compressor according to the third embodiment of the present invention, the drive shaft 140 "and the swash plate 160" coupled to the drive shaft 140 " It is composed.

Here, a pin coupling hole 161 "is formed in the swash plate 160", and a long hole 141 "corresponding to the pin coupling hole 161" is formed in the drive shaft 140 ". The coupling pins 191 "are sequentially inserted into the ball 161" and the long hole 141 ".

In addition, an arm 162 ″ hinged to the lug plate 150 is formed at the swash plate 160 ″, and a counterweight 163 ″ is formed at an opposite end of the arm 162 ″.

In addition, a driving shaft coupling hole 164 ″ is formed through the hub 160 ″ to be coupled to the driving shaft 140 ″.

On the other hand, when the above-mentioned swash plate type compressor A is driven, vibration and noise are generated according to the change in the inclination angle of the swash plate 160 ″.

In order to prevent vibration and noise caused by the change of the inclination angle of the swash plate 160 ″, the amount of change in the rotation balance of the swash plate 160 ″ should be reduced. Accordingly, the rotational center C ″ in which the inclination angle of the swash plate 160 ″ is changed is shifted forward than the center of the thickness of the swash plate 160 ″, and the distance at which the rotational center C ″ is biased is (d ″). Shown).

Here, the rotational center C ″ of the swash plate 160 ″ is a coupling pin 191 ″ coupled to the pin coupling hole 161 ″ and the long hole 141 ″, and the coupling pin 191 ″ is connected to the pin. In order to shift forward from the center of the swash plate 160 ″ thickness d, a pin coupling hole 161 ″ of the swash plate 160 ″ is formed on the front outer circumferential surface on which the arm 162 ″ is formed as shown in FIG. 10.

Therefore, as the coupling pin 191 ″ coupled to the pin coupling hole 161 ″ is also biased forward, the center of rotation C ″ of the swash plate 160 ″ is biased forward and thus, By reducing the amount of change in the rotation balance, it reduces the vibration and noise of the swash plate compressor (A).

Figure 11 is a schematic diagram showing the change in the center of gravity according to the change in the inclination angle of the swash plate, Figure 12 is a graph showing the rotation balance according to the change in the inclination angle of the swash plate.

As shown in FIGS. 11 to 12, when the swash plate is rotated, the positions of the upper center of gravity N1 formed on the arm and the lower center of gravity N2 formed on the counterweight change.

At this time, the rotational center of the swash plate to the front shift as described above, so that the upper center of gravity (N1) and the lower center of gravity (N2) to reduce the distance from the center of the drive shaft, the rate of change of the center of gravity compared to the prior art shown in Figure 3 This does not occur much.

That is, even if the inclination angle of the swash plate changes, the upper and lower centers of gravity (N1, N2) is farther away from the center of the drive shaft than in the prior art to reduce the vibration and noise generation of the compressor.

More specifically, the rotational balance of the swash plate adjusts the balance by installing a counterweight when the variable mechanism of the swash plate is determined. However, when the balance is adjusted using the counterweight, the tilt does not change as it moves only up and down as shown in P and P ′ of FIG. 12. In other words, it is difficult to balance the rotation at the minimum and maximum inclination angles, and the difference is large.

Therefore, when the rotational center of the swash plate is biased forward as in the embodiment of the present invention described above, the difference between the minimum and maximum angles at which N1 and N2 are displaced is not large, so the difference in rotation balance is reduced. Expressing this in the graph, the slope is reduced like the P 'line.

Accordingly, the difference in the rotational balance of the swash plate is not large, thereby reducing the overall vibration and noise of the compressor.

As mentioned above, although preferred embodiment of this invention was described in detail, the technical scope of this invention is not limited to the above-mentioned embodiment, It should be interpreted by the claim. At this time, those of ordinary skill in the art should consider that many modifications and variations are possible without departing from the technical scope of the present invention.

1 is an exploded perspective view illustrating a coupling structure of a swash plate for a compressor according to the prior art.

2 is a cross-sectional view of FIG. 1.

Figure 3 is a schematic diagram showing the change in the center of gravity according to the change in the inclination angle of the swash plate according to the prior art.

4 is a cross-sectional view showing a swash plate compressor according to the present invention.

Figure 5 is an exploded view showing the coupling structure of the swash plate for the compressor according to the first embodiment of the present invention.

6 is a cross-sectional view showing a coupling structure of the swash plate for the compressor of FIG.

7 is an exploded perspective view illustrating a coupling structure of a swash plate for a compressor according to a second embodiment of the present invention.

8 is a cross-sectional view showing a coupling structure of the swash plate for the compressor of FIG.

9 is an exploded perspective view illustrating a coupling structure of a swash plate for a compressor according to a third embodiment of the present invention.

10 is a cross-sectional view showing a coupling structure of the swash plate for the compressor of FIG.

Figure 11 is a schematic diagram showing the change in the center of gravity according to the change in the inclination angle of the swash plate according to the present invention.

12 is a graph illustrating a rotation balance according to a change in the inclination angle of the swash plate.

<Explanation of symbols for the main parts of the drawings>

140: drive shaft 150: lug plate

160: swash plate 161: guide groove

162: insertion hole 190: sleeve

191: coupling pin 192: coupling hole

Claims (4)

In a swash plate type compressor comprising a drive shaft to which the driving force of the engine is transmitted, a lug plate installed on the drive shaft, a swash plate coupled to the lug plate, and a piston coupled to the swash plate to reciprocate the cylinder bore. The swash plate is a swash plate-type compressor characterized in that the axial sliding movement and the rotational movement is made with respect to the drive shaft when the inclination angle is changed, the center point of the rotational movement is shifted in the lug plate direction than the center of the swash plate thickness. The method of claim 1, Guide grooves are formed in the swash plate, The sleeve having a coupling pin is inserted into the guide groove is further provided, The coupling pin is a swash plate compressor, characterized in that the center of rotation of the swash plate. The method of claim 1, Hollow is formed in the swash plate, A hub having a shaft coupling portion corresponding to the hollow is further provided, Pin hub is formed in the hub, The drive shaft is formed with a long hole corresponding to the pin coupling hole, Further provided with a coupling pin that is sequentially coupled to the pin coupling hole and the long hole, The coupling pin is a swash plate compressor, characterized in that the center of rotation of the swash plate. The method of claim 1, The swash plate is formed with a pin coupling hole, The drive shaft is formed with a long hole corresponding to the pin coupling hole, Further provided with a coupling pin that is sequentially coupled to the pin coupling hole and the long hole, The coupling pin is a swash plate compressor, characterized in that the center of rotation of the swash plate.

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