KR100917020B1 - Compressor - Google Patents

Abstract

According to the invention, a compressor is disclosed. In the disclosed compressor, the swash plate rotating in the swash plate chamber formed inside the cylinder block is integrally coupled to the drive shaft, and the pistons respectively accommodated in the plurality of cylinder bores annularly arranged around the drive shaft reciprocate in conjunction with the rotation of the swash plate. And each cylinder bore through a plurality of suction passages formed in the cylinder block such that the refrigerant sucked into the main refrigerant suction passage formed inside the drive shaft from the swash plate chamber sequentially communicates the main refrigerant suction passage with each cylinder bore according to the rotation of the drive shaft. As the suction, the opening angle of the outlet of the main refrigerant suction flow path formed inside the drive shaft is characterized in that the 118 ° to 135 °.

According to the compressor having such a structure, the suction passage formed in the cylinder block is opened when the suction stroke of the piston is started and the pressure in the cylinder bore is equal to the suction pressure, so that the suction efficiency of the refrigerant can be improved.

Compressor, air conditioning, RSV, swash plate, suction, compression

Description

Compressor

1 is a cross-sectional view showing an example of a conventional compressor,

FIG. 2 is a sectional view taken along line II-II of FIG. 1 and illustrating a time point when the NO.3 piston reaches a top dead center and starts compression; FIG.

3 is a conceptual diagram illustrating a state of FIG. 2;

Figure 4 is a graph showing the pressure and volume of the cylinder bore when the compressor is the optimum suction efficiency,

5 is a graph showing the pressure and volume of the cylinder bore when the opening angle of the outlet of the main refrigerant suction flow path is too small;

6 is a graph showing the pressure and volume of the cylinder bore when the opening angle of the outlet of the main refrigerant suction flow path is too large;

7 is a cross-sectional view showing a compressor according to an embodiment of the present invention;

8 is a conceptual diagram illustrating a state in which the NO.3 piston of the compressor according to an embodiment of the present invention reaches a top dead center to start compression;

Figure 9 is a graph showing the results of measuring the pressure and volume of the cylinder bore by operating the compressor of the present invention.

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

Compressor 110, 120 Front and rear housing

130,131 Cylinder block 132

130a ... cylinder bore 135 ... suction passage

140 Drive shaft 141 Main refrigerant suction flow path

142 Main refrigerant suction flow inlet 143 Main refrigerant suction flow outlet

150 swash plate 151 refrigerant path

160 ... piston 170,180 ... valve unit

190 Refrigerant Storage Room 191 Auxiliary Refrigerant Suction Channel

The present invention relates to a compressor, and more particularly, a fixed-capacity swash plate type in which a piston reciprocates in conjunction with rotation of a swash plate integrally coupled to a drive shaft. Accordingly, the present invention relates to a compressor employing a rotary suction valve structure that sequentially sucks each cylinder bore.

In general, an air conditioner compressor sucks refrigerant gas discharged from an evaporator and is discharged into a condenser by converting the refrigerant gas into a high temperature and high pressure state which is easily liquefied. There are various kinds of such compressors, such as a swash plate type compressor in which a piston reciprocates with the rotation of an inclined swash plate, a scroll compressor compressed by a rotational motion of two scrolls, and a vane rotary compressor compressed by a rotary vane. .

The reciprocating compressor that compresses the refrigerant according to the reciprocating motion of the piston includes crank and wobble plate type, in addition to the swash plate compressor, and the swash plate compressor includes a fixed capacity swash plate compressor and a variable capacity swash plate compressor. have.

1 shows a conventional compressor employing a rotary suction valve structure as a type of fixed displacement swash plate compressor.

As shown, the conventional compressor 1 is coupled to the inside of the front and rear housings 10 and 11 and the front and rear housings 10 and 11, and the swash plate chamber 22 is formed therein. Cylinder block 20, 21 having a plurality of cylinder bores 23, the drive shaft 30 is integrally coupled to the swash plate 31 to rotate in the swash plate chamber 22 inclined, and the swash plate 31 is rotated A plurality of pistons 40 reciprocating in the cylinder bore 23 in conjunction with the movement, and the valve unit interposed between the front and rear housings 10, 11 and the cylinder block 20, 21, respectively 50 and 51 are provided.

In addition, a main refrigerant suction flow path 32 is formed inside the drive shaft 30 to allow the refrigerant sucked from the swash plate chamber 22 to move to the cylinder bore 23, and the cylinder blocks 20 and 21. A plurality of suction passages 25 and 26 are formed in the main refrigerant suction passage 32 to communicate the cylinder bores 23 with each other.

In the fixed displacement swash plate type compressor employing the conventional rotary suction valve structure having the above structure, the circulation process of the refrigerant will be described in more detail as follows.

First, the refrigerant is supplied from the outside into the swash plate chamber 22, and the refrigerant supplied to the swash plate chamber 22 is formed on the inside of the drive shaft 30 when the drive shaft 30 rotates. The suction passages 25 and 26 of the blocks 20 and 21 are sequentially supplied to the respective cylinder bores 23.

Inlet 33 of the main refrigerant suction flow path 32 of the drive shaft 30, one side of the drive shaft 30 is in direct communication with the swash plate chamber 22, the main refrigerant suction behind the cylinder block 21 The suction chamber 50 which communicates with the flow path 32 is formed. However, the inlet 33 of the main refrigerant suction passage 32 may be formed through the hub 31a of the swash plate 31 and one side of the drive shaft 30.

2 is a cross-sectional view showing a time point when the NO.3 piston 40 reaches the top dead center and starts compression, according to line II-II of FIG. 1, and FIG. 3 shows the state of FIG. 2. The conceptual diagram shown is shown.

Here, A1 is the opening angle of the main refrigerant suction passage 32, outlet 34, and W1 represents the width of the suction passages 25, 26 formed in the cylinder block 21.

As shown, the suction passage 26 and the main refrigerant suction passage 32 of the cylinder block 21 are blocked when the NO.3 piston 40 reaches the top dead center and starts compression.

At this time, one side of the main refrigerant suction flow path 32, the outlet 34 is positioned at 180 degrees at the time when the NO.3 piston 40 starts to compress as shown. Accordingly, the opening angle of the main refrigerant suction flow path 32 and the outlet 34 represents the angle opened clockwise with respect to 180 ° at the time of compression of the NO.3 piston 40.

In addition, the NO.4 piston 40 in the suction stroke is directed to the top dead center, and at this time, the suction passage 26 of the cylinder block 21 and the outlet 34 of the main refrigerant suction passage 32 are in communication with each other. .

As such, the suction passage 26 and the main refrigerant suction passage 32 of the cylinder block 21 are blocked during the compression stroke, and the suction passage 26 and the main refrigerant of the cylinder block 21 are blocked during the suction stroke. The suction passage 32 and the outlet 34 communicate with each other.

Here, the opening angle A1 of the main refrigerant suction channel 32 outlet 34 and the width W1 of the suction passage 26 of the cylinder block 21 correspond to the suction passage 26 and the main passage of the cylinder block 21. It can be seen that the element determines the communication point of the refrigerant intake passage 32, the outlet 34.

However, when the suction stroke of the piston 40 is started as described above and the main refrigerant suction flow path 32 and the outlet 34 and the suction passage 26 of the cylinder block 21 communicate with each other, the suction of the compressor 1 is performed. The disadvantage is that the efficiency is lowered.

This is because the pressure inside the cylinder bore 23 is still higher than the suction pressure even when the suction stroke of the piston 40 starts. Therefore, in this case, when the outlet of the main refrigerant suction passage 32 and the suction passage 26 of the cylinder block 21 communicate with each other, the adverse effect of discharging the refrigerant through the suction passage 26 occurs.

In addition, when the suction stroke of the piston 40 is started and the pressure in the cylinder bore 23 is excessively low, the main refrigerant suction flow path 32 and the outlet 34 and the suction passage 26 of the cylinder block 21 are opened. Even in communication, the suction efficiency of the compressor 1 is lowered.

At this time, since the piston 40 lowers the pressure inside the cylinder bore 23 to a state lower than the actual suction pressure, the unnecessary work is performed and the efficiency of the compressor 1 is lowered.

Such details will be described once again with reference to FIGS. 4 to 6.

4 is a graph showing the pressure and volume of the cylinder bore when the suction passage is opened at the same point as the pressure inside the cylinder bore, Figure 5 is a suction passage at the point where the pressure inside the cylinder bore higher than the suction pressure Figure 6 is a graph showing the pressure and volume of the cylinder bore when opened, Figure 6 is a graph showing the pressure and volume of the cylinder bore when the suction passage is opened at a point lower than the suction pressure inside the cylinder bore. (Here, the area inside the graph represents the work of the compressor 1).

As shown in Fig. 4, the NO.3 piston starts the compression stroke, the NO.5 piston starts the suction stroke, and the suction is carried out at the current position where the pressure inside the cylinder bore 23 drops to the suction pressure. It can be seen that the passage 26 is opened to operate at the optimum suction efficiency.

However, as shown in FIG. 5, when the opening angle A1 of the outlet 34 of the main refrigerant suction passage 32 is too large, the suction passage at the point P1 before the pressure inside the cylinder bore 23 reaches the suction pressure. 26 is opened.

At this time, it can be seen that the refrigerant in the cylinder bore 23 is discharged through the suction passage 26 so that the pressure in the cylinder bore 23 instantly drops to the suction pressure. That is, it can be seen that unnecessary work is caused by the result of discharging the refrigerant during the suction stroke.

6, when the opening angle A1 of the outlet 34 of the main refrigerant suction passage 32 is too small, the suction passage at the point P2 where the pressure inside the cylinder bore 23 is lower than the suction pressure. 26 is opened.

In this case, it can be seen that the compressor 1 performs unnecessary work that excessively drops the pressure inside the cylinder bore 23.

That is, as shown in FIG. 4, the compressor 1 should be operated at the optimum efficiency without unnecessary work. As shown in FIGS. 5 and 6, the conventional compressor 1 simply does not consider the suction pressure and simply the piston ( Since the suction passage 26 is opened in accordance with the suction stroke of 40, unnecessary work is performed, and thus the suction efficiency of the refrigerant is low.

The present invention has been made to solve the above problems, the structure is to improve the suction efficiency of the refrigerant by opening the suction passage at the time when the pressure in the cylinder bore and the suction pressure of the compressor in the same general operating conditions. The object is to provide an improved compressor.

Compressor of the present invention for achieving the above object is a swash plate rotating in the swash plate chamber formed in the cylinder block is integrally coupled to the drive shaft, the pistons are respectively accommodated in a plurality of cylinder bores arranged annularly around the drive shaft; The reciprocating motion in conjunction with the rotation of the swash plate, and the refrigerant sucked from the swash plate chamber into the main refrigerant suction flow path formed inside the drive shaft to sequentially communicate the main refrigerant suction flow path with each cylinder bore in accordance with the rotation of the drive shaft. It is sucked into each cylinder bore through a plurality of suction passages formed in the cylinder block, the opening angle of the outlet of the main refrigerant suction flow path formed inside the drive shaft is characterized in that 118 ° to 135 °.

In addition, the width of the suction passage formed in the cylinder block is preferably 2.5mm to 3.5mm.

In addition, the piston is a double-headed piston, the cylinder bore is formed on both sides of the swash plate chamber, the main refrigerant suction flow path outlet of the drive shaft at least one front and rear respectively to correspond to the cylinder bore of the front and rear And a refrigerant communication passage communicating the inlet of the main refrigerant suction flow path of the swash plate chamber and the drive shaft may be formed in the swash plate.

Hereinafter, with reference to the accompanying drawings to help understand the present invention will be described a preferred embodiment. However, the following examples are merely to illustrate the present invention is not limited to the scope of the present invention.

Therefore, the embodiments described in the specification and the drawings shown in the drawings are only preferred embodiments of the present invention and do not represent all of the technical idea of the present invention, various equivalents that may be substituted for them at the time of the present application It should be understood that there may be variations and variations.

7 is a cross-sectional view of a compressor according to an embodiment of the present invention.

As shown, the compressor 100 according to an embodiment of the present invention, the drive shaft 140 is integrally coupled to the swash plate 150 to rotate in the swash plate chamber 132, the drive shaft 140 is rotatable Front and rear cylinder blocks 130 and 131 to be installed, and is mounted via the shoe 144 on the outer periphery of the swash plate 150 and in conjunction with the rotational movement of the swash plate 150 front and rear cylinder block 130 A plurality of pistons 160 reciprocating the inside of the cylinder bore 130a formed on both sides of the swash plate chamber 132 of 131, and coupled to both sides of the front and rear cylinder blocks (130, 131) Between the front and rear housings 110 and 120, and the front and rear cylinder blocks 130 and 131 and the front and rear housings 110 and 120, respectively, in which discharge chambers 111 and 121 are formed, respectively. Each valve unit 170 and 180 is provided.

The swash plate 150 rotating in the swash plate chamber 132 is inclined to the drive shaft 140, and the refrigerant sucked into the swash plate chamber 132 passes through the swash plate 150 to move to the cylinder bore 130a. The main refrigerant suction passage 141 is formed to interlock the swash plate chamber 132 and the cylinder bore 130a.

That is, the inlet 142 of the main refrigerant suction passage 141 is formed to communicate with the swash plate chamber 132, the outlet 143 is the respective suction passage 135 of the front and rear cylinder blocks 130, 131 It is formed to communicate with.

The inlet 142 of the main refrigerant suction passage 141 communicates with the swash plate chamber through the refrigerant inlet 151 formed through the hub 150a of the swash plate 150 and one side of the driving shaft 140. Here, only one inlet 142 of the main refrigerant suction passage 141 may be formed at one side of the driving shaft 140, or two may be formed in opposite directions as shown in the drawing.

The outlet 143 of the main refrigerant suction passage 141 is formed on both sides of the main refrigerant suction passage 141 in opposite directions, and each cylinder formed on both sides of the swash plate chamber 132 when the driving shaft 140 rotates. It is possible to allow the refrigerant to be sucked into the bore 130a at the same time.

In detail, since the swash plate 150 is inclined, the pistons 160 disposed in opposite directions among the pistons 160 coupled to the outer circumference of the swash plate 150 perform the same suction or compression stroke, so that the main refrigerant suction is performed. Both outlets 143 of the flow path 141 must be formed in opposite directions so that the refrigerant can be sucked into the cylinder bores 130a formed on both sides of the swash plate chamber 132 at the same time. Of course, the direction of each outlet 143 of the main refrigerant suction passage 141 formed in the drive shaft 140 may vary depending on the design purpose, such as the number of the piston (160).

The refrigerant in the swash plate chamber 132 is supplied into the cylinder bore 130a through the main refrigerant suction passage 141 formed in the drive shaft 140. In this case, in order to supply a sufficient flow rate of the coolant even when the drive shaft 140 rotates at a high speed, a coolant storage chamber 190 is further formed at the rear of the cylinder block, and the swash plate chamber is formed at the cylinder block 131. Auxiliary refrigerant suction passage 191 for communicating the coolant storage chamber 132 with the 132 may be further formed. Accordingly, the refrigerant in the swash plate chamber 132 at the high speed rotation of the drive shaft 140 is supplied into the cylinder bore 130a through the auxiliary refrigerant suction flow path 191 as well as the main refrigerant suction flow path 141. The flow rate of is supplied to improve the performance.

In the compressor of the present invention configured as described above, a preferred embodiment of the present invention will be described with reference to FIGS.

Fig. 8 is a conceptual diagram showing a state at which the NO.3 piston reaches compression top and starts compression.

Referring to FIG. 8, the NO.5 piston has a compression stroke and a suction stroke is started, and a suction passage 135 is opened at a time when the pressure in the cylinder bore 130a is equal to the suction pressure. It begins.

Here, the compressor 100 of the present invention preferably forms the opening angle A2 of the main refrigerant suction flow path 141 and the outlet 143 at 118 ° to 135 ° under general operating conditions (idle, medium speed and high speed). .

One side of the main refrigerant suction passage 141, the outlet 143 is located at the point C1 (180 °) at the time when the NO.3 piston starts to compress, so that the main refrigerant suction passage 141 of the outlet 143 The opening angle A2 represents the opening angle with respect to the point C1.

FIG. 9 is a graph showing the results of operating the compressor 100 of the present invention at idle, medium and high speeds, which are general operating speeds, and measuring the pressure and volume in the cylinder bore 130a. . At this time, the width W2 of the suction passage 135 formed in the cylinder block 130 was 2.5 mm to 3.5 mm.

On the other hand, ◆, ▲, ＊, ■ marks on the axis of the graph indicate that the opening angles A2 of the outlet of the main refrigerant suction passage 141 are 118 °, 121 °, 130 °, and 135 °, respectively. It means a time point when the suction passage 135 is opened.

9, in the idle state, the suction pressure is about 4.5 MPa, and in order to open the suction passage 135 in a state where the pressure of the cylinder bore 130a is dropped to about 4.5 MPa, the main refrigerant suction flow path 141 exits ( It can be seen that the opening angle A2 of 143 should be formed at 118 °.

In addition, when operating at a high speed, the suction pressure is about 2 MPa, and in order to open the suction passage 135 in a state where the pressure of the cylinder bore 130a is dropped to about 2 MPa, the opening angle of the outlet of the main refrigerant suction passage 141 ( It can be seen that A2) should be formed at 135 °.

In the embodiment of the present invention described above, the piston is a double-headed piston, the cylinder bore is formed on both sides of the swash plate chamber, the main refrigerant suction flow path of the drive shaft to the front and rear to correspond to each cylinder bore of the front and rear At least one compressor formed at the rear has been described, but this is merely illustrative, and features of the present invention can be implemented in a fixed displacement swash plate type compressor having a migrating piston and employing a rotary suction valve structure.

In addition, the exemplary embodiment of the present invention illustrates a case in which the inlets 142 and 242 of the main refrigerant suction passages 141 and 241 formed inside the drive shaft are formed through the hub 150a of the swash plate 150 and one side of the drive shaft 140. 1, the inlet 33 of the main refrigerant suction flow path 32 is formed by one side of the drive shaft 30 directly communicating with the swash plate chamber 22, and the cylinder block 21. The features of the present invention mentioned in the embodiment may be equally applied to a compressor in which a suction chamber 50 communicating with the main refrigerant suction passage 32 is formed at the rear side.

As described above, according to the compressor of the present invention, since the suction passage formed in the cylinder block is opened at the time when the suction stroke of the piston starts and the pressure in the cylinder bore is equal to the suction pressure, the suction efficiency of the refrigerant can be improved. .

Although the present invention has been described with reference to the embodiments illustrated in the accompanying drawings, it is merely an example, and those skilled in the art may realize various modifications and equivalent other embodiments therefrom. I will understand. Therefore, the true scope of protection of the present invention should be defined by the technical spirit of the appended claims.

Claims (3)

The swash plate 150 which rotates in the swash plate chamber 132 formed in the cylinder blocks 130 and 131 is integrally coupled to the drive shaft 140, and a plurality of cylinder bores 130a, which are annularly arranged around the drive shaft 140. Pistons 160 respectively accommodated in 131a reciprocate in conjunction with rotation of the swash plate 150 and are sucked into the main refrigerant suction flow path 141 formed inside the drive shaft 140 from the swash plate chamber 132. The refrigerant flows through the plurality of suction passages 135 and 235 formed in the cylinder blocks 130 and 131 so that the refrigerant communicates with the main refrigerant suction passage 141 and the respective cylinder bores 130a sequentially as the drive shaft 140 rotates. In the compressor (100) sucked into the cylinder bore (130a), The opening angles of the main refrigerant suction flow passage 141 and the outlet 143 formed inside the drive shaft 140 are 118 ° to 135 °, The piston 160 is a double head piston, the cylinder bore (130a) is formed in both sides of the swash plate chamber 132, At least one main refrigerant suction flow path 141 of the drive shaft 140 is formed at the front and rear to correspond to the cylinder bores 130a at the front and rear, respectively. And a refrigerant communication passage (151) communicating with the swash plate chamber (132) and the main refrigerant suction passage (141) of the drive shaft (140) and the inlet (142) is formed in the swash plate (150). The method of claim 1, Compressor, characterized in that the width of the suction passage 135 formed in the cylinder block (130,131) is 2.5mm to 3.5mm. delete

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