KR101262488B1 - Swash plate type compressor - Google Patents

Abstract

The present invention relates to a swash plate compressor. The compressor of the present invention is coupled to the front and rear cylinder blocks (10a, 10b) having a cylinder bore 12 of the working fluid therein, and to the front and rear of the front and rear cylinder blocks (10a, 10b) and discharged. And a front housing 30 and a rear housing 40 forming the seals 32, 42. And the swash plate 24 rotated by the rotation shaft 50 reciprocates the piston 20 in the cylinder bore 12 to compress the refrigerant. The compressed refrigerant is transferred to the muffler 60 through the discharge chamber connecting portion 74. A penetration depth L of the through hole 70 for guiding the compressed refrigerant into the muffler 60 is 8 to 11 mm. According to the present invention having such a configuration, by limiting the penetration depth (L) of the through hole 70 for guiding the refrigerant, there is an advantage that the pulsation of the fluid can be minimized.

Description

Swash plate type compressor {Swash plate type compressor}

The present invention relates to a swash plate compressor, and more particularly, to a swash plate compressor configured to reduce the pulsation of the refrigerant discharged at a high pressure.

1 shows a configuration of a general swash plate compressor in cross section. As illustrated, the swash plate type compressor includes a cylinder block 10 having a plurality of cylinder bores 12 therein, a front housing 30 coupled to the front of the cylinder block 10, and the cylinder block. It includes a rear housing 40 coupled to the rear of the (10).

The cylinder block 10 is formed by combining the front cylinder block 10a and the rear cylinder block 10b which are formed symmetrically with each other. In addition, a plurality of cylinder bores 12 are arranged in a circle along the edges on the front and rear sides of the front and rear cylinder blocks 10a and 10b. The cylinder bore 12 is formed in a cylindrical shape as a space for compressing the refrigerant.

And the front housing 30 is coupled to the front of the front cylinder block (10a). The rear surface of the front housing 30 is formed concave, and the concave portion is combined with the front housing 30 to form the discharge chamber (32). In addition, the rear housing 40 is coupled to the rear of the rear housing 10b. The front surface of the rear housing 40 is formed concave, the discharge chamber 42 is formed at the edge portion. The front and rear cylinder blocks 10a and 10b, the front housing 30, and the rear housing 40 are fastened by the fastening bolts 70.

And the rotating shaft 50 for transmitting the rotational force of the engine, is rotatably installed in a state passing through the front housing 30 and the cylinder block 10. That is, the rotation shaft 50 is installed in a state passing through the shaft hole 36 formed in the center portion of the front housing 30 and the shaft support hole 14 formed in the center portion of the cylinder block 10.

A swash plate 24 having a predetermined inclination angle with respect to the rotating shaft 50 is installed in the center of the rotating shaft 50, the swash plate 24 is coupled to rotate together with the rotation of the rotating shaft 50. The swash plate 24 is assembled so as to be located in the swash plate chamber 22 formed inside the central portion where the front and rear cylinder blocks 10a and 10b are coupled to each other. The swash plate 24 is for linear reciprocating movement of the piston 20 compressing the refrigerant in the cylinder bore 12. That is, the swash plate 24 converts the rotational movement of the rotary shaft 50 into a linear reciprocating motion of the piston 20, thereby receiving the refrigerant introduced into the cylinder bore 12 by the piston 20. It is compressed and sent to the discharge chambers (32, 42).

In addition, a seating part 23 for connecting the swash plate 24 is formed at the central portion of the piston 20 performing the linear reciprocating motion. A pair of hemispherical shoes 26 are provided in the seating part 23 which is partially open toward the rotation shaft 50.

The edge portion of the swash plate 24 is coupled between the shoe 26 of the seating portion (23). Therefore, when the swash plate 24 having a predetermined inclination rotates and its edge portion passes the shoe 26, the piston 20 having the shoe 26 is inclined by the inclination of the swash plate 24. The refrigerant is compressed while linearly reciprocating in the bore 12. That is, both ends of one piston 20 serve to compress the refrigerant in the cylinder bore 12.

In addition, the rotation shaft 50 is installed to interlock while penetrating through the hub 28 formed in the central portion of the swash plate 24. A bearing B is interposed between the front and rear surfaces of the hub 28 and the inner and front surfaces of the rear cylinder blocks 10a and 10b forming the swash plate chamber 22, so that the rotation shaft 50 rotates. Will be supported.

The flow path 52 through which the refrigerant flows along the length direction is formed in the rotation shaft 50. The flow passage 52 has an inlet 54 communicating with the outside so that the refrigerant can flow therein, and an outlet 56 communicating with the outside so that the refrigerant can be supplied to the cylinder bore 12. The inlet 54 is connected to an inflow path 28a formed in the hub 28 so as to communicate with the swash plate chamber 22. The outlet 56 communicates with the suction passages 29 formed in the front and rear cylinder blocks 10a and 10b so as to communicate with the cylinder bores 12 formed in the front and rear cylinder blocks 10a and 10b, respectively. It is formed to be possible.

The discharge chambers 32 and 43 are connected to the discharge passages 39 and 49 through communication holes 35 and 45 formed outside the valve assemblies 34 and 44. The discharge passages 39 and 49 are connected to the muffler 60 formed on the outer surface of the cylinder block 10. The muffler 60 is �²� that serves to reduce pulsation and noise of the refrigerant. In addition, a discharge port 61 is formed at the outlet side of the muffler 60 to deliver the compressed refrigerant to a condenser (not shown).

The operation of the compressor having such a structure will be described. As the rotary shaft 50 rotates by a driving force transmitted from the outside, the swash plate 24 is rotated together with the rotary shaft 50. Rotation of the swash plate 24 causes the piston 20 to linearly reciprocate in the cylinder bore 12.

At this time, the refrigerant supplied to the swash plate chamber 22 enters into the flow path 52 through the inlet 54 of the rotating shaft 50 through the inflow path 28a of the hub 28. And it moves along the flow path 52 inside the rotating shaft 50, and moves to the exit 56. The refrigerant is supplied into the cylinder bore 12 through the suction passage 29 of the cylinder block 10.

The refrigerant supplied into the cylinder bore 12 is compressed to high pressure by the movement of the piston 20, and then the valve assemblies 34 and 44 are opened and discharged to the discharge chambers 32 and 42. The refrigerant discharged into the discharge chambers 32 and 42 flows back into the muffler 60 through the discharge passages 39 and 49 through the communication holes 35 and 45 of the valve assemblies 34 and 44. . And the refrigerant inside the muffler 60 is discharged through the discharge port 61, the compressed refrigerant is transferred to the condenser side in the swash plate type compressor.

The swash plate type compressor having such a configuration has a basic function of compressing a refrigerant at a high pressure and transferring the refrigerant to a condenser, and it is required to reduce pulsation generated in the process of introducing the refrigerant discharged at a high pressure into the muffler.

The present invention is to solve the above problems, to minimize the pulsation generated in the process of the refrigerant discharged at a high pressure flow into the muffler.

According to a feature of the present invention for achieving the above object, the present invention comprises a front and rear cylinder block having a compression space of the refrigerant therein; Front and rear housings coupled to the front and rear of the front and rear cylinder blocks to form a discharge chamber; Compression means for compressing a refrigerant in a compression space of the front and rear cylinder blocks to discharge the discharge chamber; A muffler formed on outer surfaces of the front and rear cylinder blocks to discharge compressed refrigerant to the outside; And a swash plate type compressor including a discharge chamber connecting portion for transferring the high pressure refrigerant of the discharge chamber to the muffler; The penetration length of the through hole for guiding the compressed refrigerant into the muffler is between 8 and 11 mm.

The through hole is preferably formed in the inner wall of the muffler and the bottom of the muffler which are distinguished from the inside of the front and rear cylinder blocks.

It is preferable that a rotating shaft is rotatably installed through the front housing and the front and rear cylinder blocks, and a flow passage for transferring the refrigerant to the compression space of the front and rear cylinder blocks is formed in the rotating shaft.

According to the present invention, when the refrigerant compressed in the cylinder bore is introduced into the muffler, by limiting the penetration depth of the through hole for guiding the refrigerant, the pulsation of the fluid can be minimized. In addition, due to the reduction in the flow path resistance, smooth fluid flow and noise reduction can be expected.

1 is a cross-sectional view showing a typical swash plate compressor.
Figure 2 is an exemplary perspective view of the front cylinder block of the swash plate compressor to which the present invention can be applied.
3 is a partial cross-sectional view showing the main portion of the embodiment of the present invention.
4 is a pulsation graph according to the penetration depth of the through hole.

Hereinafter, a preferred embodiment of the swash plate compressor according to the present invention will be described in detail with reference to the accompanying drawings. In the following description of the present invention, the basic structure of the swash plate compressor is substantially the same as the conventional one shown in Figure 1 will be described with reference to Figure 1 together. 2 is a diagram illustrating an example of a front cylinder block of a swash plate compressor to which the present invention can be applied, and will be described with reference to the same reference numerals as shown in FIG.

As shown in FIG. 2, a plurality of cylinder bores 12 are formed at one side of the front cylinder block 10a to compress the refrigerant. The cylinder bores 12 are arranged in a circle along the edge. A shaft support hole 14 for rotatably supporting the drive shaft 50 is formed in the front cylinder block 10a corresponding to the center portion of the cylinder bore 12.

A portion of the outer side of the front housing 10a is provided with a muffler 60 (see FIG. 3) passing through the cylinder bore 12 before the refrigerant compressed by the piston 20 is supplied to the outside. The muffler 60 serves to reduce pulsation and noise of the refrigerant. The muffler 60 is formed on the outer surface of the front housing 10a, and is substantially formed at a position corresponding to the rear housing 10b. Therefore, the muffler 60 is coupled to the front and rear cylinder blocks (10a, 10b), it is formed as a space for reducing the pulsation and noise of the refrigerant. The same applies to the configurations of the cylinder bore and the shaft support hole.

Looking at the configuration of the muffler 60 on the basis of the front housing 10a, the muffler 60, the outer wall 62 forming the outer surface of the front cylinder block 10a, the muffler 60 and the swash plate It can be seen that a predetermined space is formed between the inner walls 64 partitioning the seal 22. The outer wall 62 substantially forms part of the overall outline of the compressor. The inner wall 64 may be substantially a wall partitioning the swash plate chamber 22 and the muffler 60 to which the refrigerant to be compressed is supplied.

The refrigerant compressed in the front and rear cylinder blocks 10a and 10b is introduced into the muffler 60 via the respective discharge chambers 32 and 42. Refrigerant flows into the muffler 60 from the discharge chambers 32 and 42 through the discharge passages 39 and 49, through which a through hole is formed in the muffler 60. The refrigerant flows into the muffler 60.

2 and 3, the through hole 70 for guiding the coolant is formed to allow communication between the muffler 60 and the discharge chamber connecting portion 74. That is, by drilling the high-pressure refrigerant from the discharge chamber (32, 42) toward the interior of the muffler (60), it is formed to penetrate to the bottom surface 66 of the muffler (60). Here, the discharge chamber connecting portion 74 collectively refers to a passage connected to the discharge chambers 32 and 42 through which the refrigerant compressed in the cylinder bore 12 is discharged, which is described as the discharge passages 39 and 49 in FIG. 1. It is to include. That is, the discharge chamber connecting portion 74 is used as a generic term for a connecting portion into which the refrigerant discharged by being compressed at a high pressure in the compressor can be introduced into the muffler 60.

In the cylinder block 10a formed by die casting, it can be seen that the through hole 70 is formed by drilling the refrigerant to flow into the muffler 60. In this case, the portion where the through hole 70 is formed is a portion corresponding to the inner bottom surface 66 of the muffler 60 adjacent to the inner wall 64, which can be seen in FIG. 3.

The coolant supplied to the through hole 70 must pass through the discharge passages 39 and 49 in the discharge chambers 32 and 42, and the structure around the through hole 70, that is, the discharge chambers 32 and 42. ), The through hole 70 is drilled in a state spanning the inner wall 64 by the structure of the cylinder block 10a itself including the discharge passages 39 and 49 and the cylinder bore 12. Is formed.

And, in order to form the through hole 70, when drilling into the interior of the muffler in the discharge chamber connecting portion 74, from the bottom 66 of the muffler 60 to the rear (right side in the drawing) to a constant depth Drilling must be performed. As shown in FIG. 3, the depth drilled in the bottom surface 66 of the muffler 60, that is, the distance from the inlet of the through hole 70 to the inlet of the muffler 60 is referred to as “L”. have.

Since the flow path resistance and pulsation generated during the operation of the compressor are closely related to the efficiency of the compressor, it is very important to solve the problems related to the improvement of the driving efficiency and noise of the compressor. The present inventors have recognized that the condition of the depth L of the through hole 70 associated with the bottom face 66 of the muffler 60 is closely related to the flow path resistance and pulsation. And through experiments, etc., it was found that the most preferable for reducing the pulsating pressure in a specific condition of the depth (L).

For example, the relationship between the pulsating pressures was tested while varying the penetration depth L of the bottom surface 66 of the muffler 60 within the range of 6 to 13 mm. At this time, it is assumed that the area of the through hole 70 is the same regardless of the penetration depth (L).

The experiment was performed while varying the penetration depth (L) and the revolutions per minute (rpm) of the compressor, and the results are shown in FIG. Referring to the pulsation test results in connection with FIG. 4, when the revolution per minute (rpm) of the compressor is 900 rpm, that is, at a relatively low speed, the pulsation is most severe when the penetration depth L of the through hole 70 is 13 mm. At 9.5mm, it is noticeably reduced. And when the rpm (rpm) of the compressor is 2200rpm, that is, relatively high speed, it can be seen that the pulsation is the most severe when the penetration depth (L) of the through hole 70 is 6.0mm and significantly reduced when it is 9.5. . That is, it can be seen that the discharge-side pulsation has a considerable change with respect to the change in the penetration depth L.

To summarize the above experimental results, when forming the through-holes, the pulsation pressure is high within the range of most rotations when the penetration depth L of the through-hole 70 is short (less than 6 mm). It can be seen that. Further, even when the penetration depth L of the through hole 70 is long (more than 13 mm), it can be seen that it is not preferable because the pulsation pressure is high within most rotation speed ranges.

Therefore, the present inventors can confirm that a preferable result in terms of pulsation can be obtained when the value of the penetration depth L of the through hole 70 is between 8 mm and 11 mm by the experiment under the above conditions. In addition, in the above-described experimental example, it is not advantageous in terms of pulsation and flow path resistance by substantially increasing the value of the depth L unconditionally, and there is an effect of reducing pulsation and flow path resistance only within a predetermined range. Referring to these experimental results, it can be seen that it is most preferable to set the value of the penetration depth L of the through hole 70 related to the muffler in the above-described condition, that is, in the range of 8 mm to 11 mm.

As described above, the present invention can be seen that the basic technical idea is to configure the through-hole of the muffler in a predetermined range to minimize the pulsation pressure and reduce the flow resistance. Within the scope of the basic technical spirit of the present invention, it will be apparent to those skilled in the art that various modifications are possible, and that the present invention should be interpreted based on the appended claims.

10a, 10b: front and rear cylinder blocks 12: cylinder bore
20: piston 24: swash plate
30: front housing 40: rear housing
32, 42: discharge chamber 50: rotating shaft
60: muffler 62: outer wall
64: inner wall 70: through hole
74: discharge chamber connection

Claims (3)

Front and rear cylinder blocks (10a, 10b) having a compression space of the refrigerant therein;
A front housing 30 and a rear housing 40 coupled to the front and rear of the front and rear cylinder blocks 10a and 10b to form discharge chambers 32 and 42;
Compression means for compressing the refrigerant in the compression spaces of the front and rear cylinder blocks 10a and 10b and discharging the refrigerant into the discharge chambers 32 and 42;
A muffler (60) formed on the outer surfaces of the front and rear cylinder blocks (10a, 10b) for discharging the compressed refrigerant to the outside; And
In the swash plate type compressor comprising a discharge chamber connecting portion (74) for transferring the high pressure refrigerant in the discharge chamber (32, 42) to the muffler (60);
The swash plate compressor, characterized in that the through length L of the through hole 70 for guiding the compressed refrigerant into the muffler 60 is between 8 and 11 mm. The inner wall 64 of the muffler 60 and the bottom surface 66 of the muffler 60 are separated from the inside of the front and rear cylinder blocks 10a and 10b. Swash plate compressor, characterized in that formed on. The method of claim 2,
A rotating shaft 50 is rotatably installed through the front housing 30 and the front and rear cylinder blocks 10a and 10b, and the front and rear cylinder blocks 10a and 10b are compressed on the rotating shaft 50. A swash plate compressor, characterized in that a flow path (52) for delivering a refrigerant to the space is formed.

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