KR101152025B1 - Swash plate type compressor - Google Patents

Abstract

The present invention relates to a swash plate compressor. In the present invention, the cylinder bore 4a is formed therein, and the front and rear cylinder blocks 4 and 4 'are provided in which a plurality of communication holes 8 are formed in a portion adjacent to the cylinder bore 4a. The valve assembly 14 is coupled to one surface of the front and rear cylinder blocks 4 and 4 ′ to flow the refrigerant flowed into or discharged from the front and rear cylinder blocks 4 and 4 ′. To control. The drive shaft 24 is rotatably installed to penetrate the front and rear cylinder blocks 4 and 4 'to receive power required for the compression of the refrigerant from the driving source. Meanwhile, the front and rear cylinder blocks 4 and 4 'are formed with guide holes 10 for guiding the engagement positions with the valve assembly 14, and the front and rear cylinder blocks 4 and 4' and the valve assembly 14 are formed. In order to equalize the pressure of the surface is coupled to) is formed around the guide hole (10) 112 is formed.

According to the present invention, since the pressure applied to the front and rear cylinder block (4, 4 ') and the valve assembly 14 is coupled to the entire surface by forming the recessed surface 112, the front and rear cylinder block (4, 4 ') and the leak occurring between the valve assembly 14 is minimized.

Compressor, swash plate, valve

Description

Swash plate type compressor {Swash plate type compressor}

The present invention relates to a compressor, and more particularly, to a swash plate compressor having a structure that can prevent the refrigerant from leaking between the front and rear cylinder block and the valve assembly.

The compressor used in the automotive air conditioning system sucks the evaporated refrigerant from the evaporator, makes the refrigerant at high temperature and high pressure, which is easy to liquefy, and delivers it to the condenser.

In such a compressor, there is a configuration in which the refrigerant is actually compressed, and a reciprocating type that performs compression while reciprocating and a rotary type that performs compression while rotating. The reciprocating type includes a crank type for transmitting the driving force of the driving source to a plurality of pistons using a crank, a swash plate type for transmitting a swash plate to a drive shaft provided with a swash plate, and a wobble plate type using a wobble plate. Rotary type includes vane rotary type using rotary rotary shaft and vane, and scroll type using rotary scroll and fixed scroll.

1 is a cross-sectional view showing the configuration of a general swash plate compressor, Figure 2 is a perspective view showing a part of the cylinder block of the general swash plate compressor, Figure 3 is a photograph showing the pressure distribution of the cylinder block of FIG.

As shown in these figures, the swash plate type compressor 1 according to the present invention has a front and rear cylinder block 4, 4 'and a front and rear cylinder block 4, 4' having a cylinder bore 4a formed therein. And a front head 2 and a rear head 27 which are coupled to the front and the rear, respectively, to form the discharge chambers 2a and 27a and the suction chambers 2b and 27b. The front head 2, front and rear cylinder blocks 4, 4 'and the rear head 27 are joined by bolts B.

The front head 2 has a substantially cylindrical shape, and the discharge chamber 2a and the suction chamber 2b are formed therein. The discharge chamber 2a and the suction chamber 2b communicate with the front cylinder block 4, respectively. The discharge chamber 2a and the suction chamber 2b are formed to be selectively connected to each cylinder bore 4a of the front cylinder block 4 through the valve assembly 14.

Meanwhile, referring to FIG. 2, the front cylinder block 4 and the rear cylinder block 4 ′ are provided with a plurality of cylinder bores 4a formed in a direction parallel to the drive shaft 24. The cylinder bore 4a has a substantially cylindrical shape, and the piston bore 4a is provided with a linear reciprocating motion.

In the center of the front and rear cylinder block (4, 4 ') is formed a shaft hole (6) for installing the drive shaft (24). A communication hole 8 is formed between the cylinder bore 4a and the shaft hole 6. A plurality of communication holes 8 may be formed in the longitudinal direction of the front and rear cylinder blocks 4 and 4 '.

In addition, an oil groove 9 is formed in communication with the shaft hole 6 and the communication hole 8. The oil groove 9 is a portion formed to allow oil to be injected into the drive shaft 24.

A plurality of guide holes 10 are formed in the front and rear cylinder blocks 4 and 4 ′. The guide hole 10 is a portion formed to guide the engagement position with the valve assembly 14 coupled to the front and rear cylinder blocks 4, 4 '. That is, a guide pin (not shown) is inserted into the guide hole 10 to determine a coupling position between the front and rear cylinder blocks 4 and 4 'and the valve assembly 14, and in this state, the front and rear cylinder blocks ( 4, 4 ') and the valve assembly 14 are combined.

Referring back to FIG. 1, a valve assembly that controls the flow of refrigerant between the suction chamber 2b and the discharge chamber 2a and the cylinder bore 4a between the front head 2 and the front cylinder block 4. 14 is provided. That is, the valve assembly 14 controls the refrigerant flow from the suction chamber 2b to the cylinder bore 4a and the refrigerant flow from the cylinder bore 4a to the discharge chamber 2a, respectively.

The valve assembly 14 includes a valve plate 15 coupled to the front cylinder block 4, and suction leads 16 and discharge leads 17 provided on both sides of the valve plate 15, respectively. .

The valve plate 15 is generally formed of a metal material of steel. The valve plate 15 is provided with discharge holes 15a and suction holes 15b at positions corresponding to the respective cylinder bores 4a. Zinc (Zn) is plated on the valve plate 15. This is to prevent corrosion of the valve plate 15 and is plated on the entire surface of the valve plate 15.

Meanwhile, the suction lead 16 and the discharge lead 17 are elastically deformable materials and are elastically deformed according to the internal pressure of the cylinder bore 4a to open and close the suction hole 15b and the discharge hole 15a. Do it.

A head gasket 18 is provided on one surface of the valve plate 15 facing the front head 2. The head gasket 18 has a substantially disc shape, and serves to prevent the refrigerant from leaking between the front head 2 and the valve plate 15.

The head gasket 18 is formed with a retainer 19 integrally with the head gasket 18. The retainer 19 is a portion for preventing the discharge lead 17 from being excessively elastically deformed toward the inside of the discharge chamber 2a by the discharge pressure of the refrigerant. The retainer 19 extends radially toward the outer circumferential surface of the head gasket 18 of the head gasket 18. The retainer 19 is formed bent toward the discharge chamber 2a by a predetermined angle.

In addition, a suction gasket 20 is provided on one surface of the valve plate 15 facing the front cylinder block 4. The suction gasket 20 has a substantially disc shape, and serves to prevent the refrigerant from leaking between the front head 2 and the front cylinder block 4.

On the other hand, the swash plate chamber 23 is formed inside the front cylinder block 4 and the rear cylinder block 4 '. In the swash plate chamber 23, a swash plate 25 provided on the drive shaft 24 is rotatably positioned.

The drive shaft 24 is installed through the center of the front head 2, the front cylinder block 4 and the rear cylinder block 4 '. An approximately disk-shaped swash plate 25 is inclined with respect to the extending direction of the drive shaft 24 on the drive shaft 24.

A shoe 26 is provided between the swash plate 25 and the piston 30. The shoe 26 is provided between the swash plate 25 and the piston 30 so that the rotational movement of the swash plate 25 is transmitted to the piston 30.

On the other hand, the piston 30 is installed inside the cylinder bore 4a to enable a straight reciprocating motion. The piston 30 has a substantially cylindrical shape corresponding to the inside of the cylinder bore 4a, and both ends thereof are located in the cylinder bore 4a of the front cylinder block 4 and the rear cylinder block 4 ', respectively.

That is, both ends of the piston 30 serve to compress the refrigerant in the cylinder bore 4a. The piston 30 is the middle portion thereof is coupled to the shoe 26, the linear reciprocating motion according to the rotation of the swash plate 25.

The rear head 27 is mounted on one surface of the rear cylinder block 4 '. The rear head 27 is provided with a discharge chamber 27a and a suction chamber 27b. The discharge chamber 27a and the suction chamber 27b are in communication with the rear cylinder block 4 ', respectively. The discharge chamber 27a and the suction chamber 27b are selectively connected to the cylinder bores 4a formed in the rear cylinder block 4 'through the valve plate 15.

The valve assembly 14 is also provided between the rear head 27 and the rear cylinder block 4 '. The valve assembly 14 controls the refrigerant flow from the suction chamber 27b to the cylinder bore 4a and the refrigerant flow from the cylinder bore 4a to the discharge chamber 27a, respectively.

A head gasket 18 is also provided on one surface of the valve plate 15 facing the rear head 27. The head gasket 18 has a substantially disc shape, and serves to prevent the refrigerant from leaking between the rear head 27 and the valve plate 15.

In addition, the suction gasket 20 is provided on one surface of the valve plate 15 facing the rear cylinder block 4 '. The suction gasket 20 serves to prevent the refrigerant from leaking between the rear head 27 and the rear cylinder block 4 '.

The operation of the compressor having such a configuration will be described. As the drive shaft 24 is rotated by a driving force transmitted from the outside, the swash plate 25 is rotated together with the drive shaft 24. Rotation of the swash plate 25 allows the piston 30 to make a linear reciprocating motion inside the cylinder bore 4a.

At this time, as the drive shaft 24 rotates, the refrigerant in the suction chambers 2b and 27b is sucked into the cylinder bore 4a, respectively. For reference, the refrigerant is sucked into the cylinder bore 4a when the piston 30 moves from the corresponding cylinder bore 4a to the bottom dead center.

As such, when the refrigerant is delivered to the cylinder bore 4a, the piston 30 of the corresponding cylinder bore 4a moves in the direction of the valve plate 15, and the refrigerant is compressed.

When the refrigerant is compressed in the cylinder bore 4a, the pressure inside the cylinder bore 4a becomes relatively high and the refrigerant is discharged to the discharge chambers 2a and 27a. The refrigerant discharged into the discharge chambers 2a and 27a is transferred to the condenser (not shown) through the refrigerant discharge port.

However, the above-described conventional techniques have the following problems.

3 shows the pressure received at the front and rear cylinder blocks 4, 4 'and the valve assembly 14 in engagement. For reference, in this picture, the pressure increases toward the red side and the pressure decreases toward the blue side. Referring to this, it can be seen that the pressure at the portion where the communication hole 8 is formed (hereinafter referred to as A portion) and the portion where the guide hole 10 is formed (hereinafter referred to as B portion) are different from each other. That is, the portion where the communication hole 8 and the guide hole 10 are connected in the portion B shows a lower pressure distribution than the portion A, so that the portion B decreases the pressure locally.

As such, if the surface pressure of the front and rear cylinder blocks 4 and 4 'is not uniform, there is a problem in that the inner leak is weak when the compressor 1 is operated. In other words, since the pressure received by the valve plate 15 coupled to the front and rear cylinder blocks 4 and 4 'is uneven, a problem arises in which the refrigerant leaks from the high A portion to the B portion.

Accordingly, an object of the present invention is to solve the problems of the prior art as described above, so that the pressure at the surface in which the front and rear cylinder blocks and the valve assembly are coupled is evenly distributed throughout.

Technical problems to be achieved by the present invention are not limited to the above-mentioned technical problems, and other technical problems not mentioned above will be clearly understood by those skilled in the art from the following description. Could be.

According to a feature of the present invention for achieving the above object, the present invention is a cylinder bore is formed inside, the front and rear cylinder block is formed with a plurality of communication holes in the portion adjacent to the cylinder bore; A valve assembly coupled to one surface of the front and rear cylinder blocks to control the flow of the refrigerant sucked into or discharged from the front and rear cylinder blocks; A drive shaft rotatably installed to penetrate the front and rear cylinder blocks, and receives power required to compress the refrigerant from a drive source; And a piston for linearly reciprocating movement in the cylinder bore according to the rotation of the swash plate installed on the drive shaft, wherein the front and rear cylinder blocks are formed with guide holes for guiding the engagement position with the valve assembly. The block is characterized in that the surface pressure uniform means for uniformizing the pressure of the surface meeting the valve assembly.

The surface pressure uniform means is characterized in that the recessed surface formed around the guide hole.

The recessed surface is formed to have a size corresponding to the cross section of the communication hole.

The wall portion of the front and rear cylinder block formed between the cylinder bore and the recessed surface and the wall portion of the front and rear cylinder block formed between the cylinder bore and the communication hole have the same thickness.

In the present invention, the recessed surface is formed around the guide hole formed in the front and rear cylinder block and the valve assembly is coupled. In this way, since the pressure applied to the surface where the front and rear cylinder blocks and the valve assembly are coupled to each other is formed evenly, the leakage occurring between the front and rear cylinder blocks and the valve assembly is minimized. As a result, if the occurrence of leakage is minimized, the performance of the compressor can be improved.

Hereinafter, a preferred embodiment of the compressor according to the present invention will be described in detail with reference to the accompanying drawings.

Figure 4 is a perspective view showing the configuration of the cylinder block of the swash plate compressor according to the present invention, Figure 5 is a photograph showing the pressure distribution of the cylinder block of FIG. Hereinafter, the same reference numerals are used to refer to the same components as the prior art, and the illustrated configuration illustrated in FIG. 4 will be described in more detail below.

The swash plate compressor 1 according to the present invention includes front and rear cylinder blocks 4 and 4 'in which a cylinder bore 4a is formed. In the front and rear cylinder blocks 4 and 4 ', two cylinder blocks are coupled to each other to form the cylinder bore 4a therein. In this embodiment, a total of five cylinder bores 4a are formed, which may vary depending on the number of pistons 30 installed in the cylinder bores 4a. The cylinder bore 4a has a substantially cylindrical shape, and the piston 30 is installed in the cylinder bore 4a to enable a linear reciprocating motion.

In the center of the front and rear cylinder block (4, 4 ') is formed a shaft hole (6) for installing the drive shaft (24). The shaft hole 6 is formed by penetrating the front and rear cylinder blocks 4, 4 'in front and rear.

In addition, a plurality of communication holes 8 are formed at a portion corresponding to the cylinder bore 4a and the shaft hole 6. The communication hole 8 is a portion formed for communicating with the swash plate chamber 23 and the shaft hole 6 and at the same time lose weight.

Meanwhile, an oil groove 9 is formed in communication with the communication hole 8 and the shaft hole 6. The oil groove 9 is a portion formed to allow oil to be injected into the drive shaft 24. That is, the drive shaft 24 is a groove is formed so that the oil can be effectively introduced because the friction is generated by the rotation.

Communication holes 8 are preferably formed in all portions except the cylinder bore 4a and the shaft hole 6, but a plurality of guide holes 10 are formed in a part of the front and rear cylinder blocks 4 and 4 '. do. The guide hole 10 has a relatively smaller size than the communication hole 8, as shown in FIG. 4, and is formed in two portions, respectively. The guide hole 10 is a portion formed to guide the position where the front and rear cylinder blocks 4, 4 'and the valve assembly 14 are coupled. A guide pin (not shown) is inserted into the guide hole 10 to guide a coupling position of the front and rear cylinder blocks 4 and 4 'and the valve assembly 14.

And the recessed surface 112 is formed on one surface of the front and rear cylinder blocks (4, 4 ') around the guide hole (10). The recessed surface 112 is a portion formed to prevent the pressure from being lowered in the portion (B portion) corresponding to the periphery of the guide hole 10. That is, the pressure in the periphery of the guide hole 10 in Figure 3 is because the communication hole 8 is not formed in this portion is made of a plane.

Therefore, in order to prevent this by placing the indentation surface 112 around the guide hole 10 so that the pressure is similar to the peripheral portion (part A) formed with the communication hole (8). Substantially referring to Figure 5, by placing the concave inlet surface 112, the pressure of the peripheral portion (part B) of the guide hole 10 is measured to be similar to the pressure of the peripheral portion (part A) of the communication hole (8) You can see that. For reference, in this picture, the pressure increases toward the red side and the pressure decreases toward the blue side. As such, the pressure on one surface of the front and rear cylinder blocks 4 and 4 ′ is generally maintained to be similar, so that leakage occurs between the valve assembly 14 coupled to one surface of the front and rear cylinder blocks 4 and 4 ′. You can minimize it. In addition, since the guide hole 10 is left as it is, only the concave inlet surface 112 is formed, the guide hole 10 may perform an original function.

In this embodiment, the concave surface 112 is preferably formed to have a size corresponding to the cross section of the communication hole (8). This is to uniformize the pressure at the surface where the front and rear cylinder blocks 4 and 4 'and the valve assembly 14 are coupled. As described above, in the present embodiment, the leakage occurring between the front and rear cylinder blocks 4 and 4 'and the valve assembly 14 can be easily solved through the configuration of the recessed surface 112.

On the other hand, the front and rear cylinder block formed between the wall portion of the front and rear cylinder blocks 4 and 4 'formed between the cylinder bore 4a and the concave inlet surface 112 and the cylinder bore 4a and the communication hole 8. The wall portion of (4, 4 ') preferably has the same thickness T. This is illustrated well in FIG. As such, the thicknesses of the respective wall portions are equal, so that the pressure at the surface at which the front and rear cylinder blocks 4 and 4 'and the valve assembly 14 are coupled may be uniformly formed.

Hereinafter will be described in detail the operation of the compressor according to the present invention having the configuration as described above.

First, as the drive shaft 24 rotates by the driving force transmitted from the engine, the swash plate 25 is rotated together with the drive shaft 24. Rotation of the swash plate 25 allows the piston 30 to make a linear reciprocating motion inside the cylinder bore 4a.

At this time, as the drive shaft 24 rotates, the refrigerant in the suction chambers 2b and 27b is sucked into the cylinder bore 4a, respectively. For reference, the refrigerant is sucked into the cylinder bore 4a when the piston 30 moves from the corresponding cylinder bore 4a to the bottom dead center.

As such, when the refrigerant is delivered to the cylinder bore 4a, the piston 30 of the corresponding cylinder bore 4a moves in the direction of the valve assembly 14, and compression of the refrigerant occurs.

The pressure applied to the valve assembly 14 by the piston 30 may be represented evenly throughout the configuration of the recessed surface 112 as shown in FIG. 5. Therefore, the occurrence of the leakage in the surface in which the front and rear cylinder block (4, 4 ') and the valve assembly 14 is coupled can be minimized.

When the refrigerant is compressed in the cylinder bore 4a, the pressure inside the cylinder bore 4a becomes relatively high and the refrigerant is discharged to the discharge chambers 2a and 27a. The refrigerant discharged into the discharge chambers 2a and 27a is transferred to the condenser (not shown) through the refrigerant discharge port.

The scope of the present invention is not limited to the embodiments described above, but is defined by the claims, and various changes and modifications can be made by those skilled in the art within the scope of the claims. It is self evident.

1 is a cross-sectional view showing the configuration of a typical swash plate compressor.

Figure 2 is a perspective view showing the configuration of a cylinder block of a typical swash plate type compressor.

Figure 3 is a photograph showing the pressure distribution of the cylinder block of Figure 2;

Figure 4 is a perspective view showing the configuration of the cylinder block of the swash plate compressor according to the present invention.

5 is a photograph showing the pressure distribution of the cylinder block of FIG.

Explanation of symbols on the main parts of the drawings

1: compressor 2: front head

4: Front cylinder block 4 ': Rear cylinder block

4a: cylinder bore 6: shaft hole

8: communication hole 9: oil groove

10: guide hole 14: valve assembly

15: valve plate 16: suction lead

17: discharge lead 18: head gasket

19: Retainer 20: Suction Gasket

23: swash chamber 24: drive shaft

25: swash plate 26: shoe

27: rear head 30: cylinder

112: recessed surface

Claims (4)

A front and rear cylinder block (4,4 ') having a cylinder bore (4a) formed therein and a plurality of communication holes (8) formed in a portion adjacent to the cylinder bore (4a); A valve assembly 14 coupled to one surface of the front and rear cylinder blocks 4 and 4 'to control the flow of the refrigerant sucked into or discharged from the front and rear cylinder blocks 4 and 4'. )Wow; A drive shaft (24) rotatably installed to penetrate the front and rear cylinder blocks (4, 4 '), and receives power required to compress the refrigerant from a drive source; And In the compressor comprising a piston 30 linearly reciprocating in the cylinder bore (4a) in accordance with the rotation of the swash plate 25 installed on the drive shaft 24, The front and rear cylinder blocks 4 and 4 'are provided with guide holes 10 for guiding the engagement positions with the valve assembly 14, and the front and rear cylinder blocks 4 and 4' are provided with the valve assembly 14. Compressor, characterized in that the surface pressure uniform means for equalizing the pressure of the surface meets. The method of claim 1, The surface pressure uniform means is a compressor, characterized in that the concave inlet surface 112 formed around the guide hole (10). The method of claim 2, The concave inlet surface 112 is formed to have a size corresponding to the cross section of the communication hole (8). The method of claim 2, Front and rear cylinder blocks 4 and 4 formed between the wall portion of the front and rear cylinder blocks 4 and 4 'formed between the cylinder bore 4a and the concave inlet surface 112 and the cylinder bore 4a and the communication hole 8; A wall of 4 ') having the same thickness.

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