KR20110016305A - Swash plate type compressor - Google Patents

Abstract

PURPOSE: A swash plate type compressor capable of improving a performance coefficient is provided to reduce discharging resistance of the refrigerant stuck in a discharge lead and to reduce power consumption. CONSTITUTION: A swash plate type compressor comprises a cylinder block(10), a front housing(20), a rear housing(30), a driving shaft(40), and a valve assembly(60). The cylinder block comprises a plurality of cylinder bores(13). The front housing is united with the cylinder block and forms a crank-case(21).

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 for compressing a refrigerant by linearly reciprocating a plurality of pistons respectively provided on a plurality of cylinder bores of a cylinder block using a swash plate installed on a rotating shaft.

Looking briefly at the air conditioning system of the vehicle, first, the refrigerant of the high temperature low pressure gas state is brought into the high temperature high pressure gas state by the compressor. The refrigerant in the high temperature and high pressure gas state becomes a high temperature high pressure liquid state by the condensation action of the condenser via a condenser, and the refrigerant in the high temperature and high pressure liquid state becomes a low temperature low pressure liquid state by the throttling action of the expansion valve through the expansion valve. do.

 The refrigerant in the low temperature low pressure liquid state is returned to the high temperature low pressure gas state through heat exchange in the evaporator through the evaporator, and the high temperature low pressure gas is compressed by the compressor to become a high temperature high pressure gas state. The air conditioning system of the vehicle is operated by heat exchange in the process of repeatedly performing such a process.

Compressors for compressing a refrigerant include a reciprocating type that actually compresses a working fluid, 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 drive source to the plurality of pistons using a crank, a swash plate type for transmitting using a rotating 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 a discharge port portion of the swash plate compressor according to the prior art. According to this, the cylinder block 102 forms a part of the skeleton of the swash plate type compressor. A plurality of cylinder bores 104 are formed in the cylinder block 102, and a piston (not shown) is installed in the cylinder bore 104 in connection with a drive shaft that is rotated by a driving force of the engine. By the rotation of the drive shaft, the piston reciprocates in the cylinder bore 104 to compress the refrigerant.

One end of the cylinder block 102 is coupled to the rear housing 106 in which the discharge chamber 108 is formed. The discharge chamber 108 is a portion formed in communication with the cylinder block 102 and is a space in which the compressed refrigerant is temporarily stored. The discharge chamber 108 is formed at a position adjacent to an edge of the surface facing the cylinder block 102 in the rear housing 106.

The valve assembly 110 is provided between the cylinder block 102 and the rear housing 106. The valve assembly 110 serves to communicate the cylinder bore 104 with the discharge chamber 108.

The valve plate 111 forming the skeleton of the valve assembly 110 is made in a disc shape, and a plurality of discharge holes 112 are formed. The discharge hole 112 is formed at a position corresponding to the cylinder block 102. The discharge hole 112 is formed to have a predetermined length when referring to Figure 1, which forms a flow path of the refrigerant discharged.

Both sides of the valve assembly 110 are provided with suction leads 114 and discharge leads 116, respectively. The suction lead 114 and the discharge lead 116 are each made of a metal capable of elastic deformation. The suction lead 114 and the discharge lead 116 are elastically deformed according to the refrigerant pressure therein to open and close the suction hole (not shown) and the discharge hole 112.

That is, when the pressure in the cylinder bore 104 is higher than the pressure in the discharge chamber 108, the discharge lead 116 is elastically deformed to open the discharge hole 112 and the cylinder through the discharge hole 112 The refrigerant of the bore 104 is allowed to flow into the discharge chamber 108.

And the regulation gasket 118 is provided in close contact with the discharge lead 116. The regulating gasket 118 serves to regulate a range in which the discharge lead 116 is elastically deformed.

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

The discharge lead 116 is installed to elastically deform by the pressure difference between the cylinder bore 104 and the discharge chamber 108. That is, based on FIG. 1, the discharge lead 116 opens and closes the discharge hole 112 while the upper end is elastically deformed about the lower end.

However, since the discharge hole 112, which is a passage through which the refrigerant flows into the discharge chamber 108, is formed in a straight channel when viewed from the side, the discharge resistance of the refrigerant that pushes the discharge lead 116 increases. . This is because the discharge lead 116 opens the discharge hole 112 while being elastically deformed about one end without being opened while the front surface is moved rearward by the pressure of the refrigerant.

In other words, since the flow cross-sectional area of the refrigerant flowing into the discharge hole 112 is constant, the discharge resistance of the refrigerant is relatively large, thereby increasing the power consumption of the compressor. As the power consumption of the compressor increases, the coefficient of performance (COP) decreases, thereby degrading the efficiency of the compressor.

Accordingly, an object of the present invention is to solve the problems of the prior art as described above, and to provide a swash plate compressor having a structure capable of minimizing the discharge resistance of the refrigerant.

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 object as described above, the present invention includes a cylinder block is formed with a plurality of cylinder bores in which the piston is a linear reciprocating motion in accordance with the rotational movement of the swash plate; A front housing installed at a front end of the cylinder block and coupled to the cylinder block to form a crank chamber therein; A rear housing provided at a rear end of the cylinder block and having a discharge chamber communicating with the cylinder bore, wherein a discharge hole, which is a flow path through which the refrigerant is discharged, is formed between the cylinder bore and the discharge chamber; A drive shaft penetrating the cylinder block and rotatably installed at both ends of the front and rear housings; In the swash plate compressor comprising a valve assembly that controls the flow of the refrigerant between the cylinder block and the rear housing, the discharge lead for opening and closing the discharge hole is provided to be elastically deformable,

The discharge hole is formed with an enlarged portion in which the flow cross-sectional area increases toward the rear, and the enlarged portion is formed at a portion adjacent to the end of the discharge lead.

The extension portion is characterized in that it is formed to have a curved surface or plane toward the rear.

The discharge lead is characterized in that the elastic deformation range is regulated by a regulating gasket provided in the valve assembly.

The drive shaft, characterized in that the flow path is formed inside to transfer the refrigerant delivered to the suction chamber into the cylinder bore.

In the present invention, in the shape of the discharge hole formed between the cylinder bore and the discharge chamber, an enlarged portion is formed in which the flow cross-sectional area increases toward the rear of the discharge hole. In addition, the expansion portion of the discharge hole is formed at a portion adjacent to the end of the discharge lead so that the refrigerant can be concentrated toward the end of the discharge lead. Therefore, since the discharge resistance of the refrigerant applied to the discharge lead is reduced, the power consumption of the compressor is reduced, and as a result, the coefficient of performance (COP) is improved.

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.

2 is a cross-sectional view showing a configuration of a preferred embodiment of the swash plate compressor according to the present invention, Figure 3 is a schematic cross-sectional view showing the main configuration (A) of the swash plate compressor according to a preferred embodiment of the present invention.

As shown in these figures, a portion of the skeleton of the swash plate compressor 1 according to the present invention is formed by the cylinder block 10. A center bore 11 is formed through the center of the cylinder block 10. The center bore 11 is a portion in which the drive shaft 40 to be described below is rotatably installed.

A plurality of cylinder bores 13 penetrate inside the cylinder block 10. The cylinder bore 13 is formed to radially surround the center bore 11. The communication path 14 is formed so that the cylinder bore 13 and the center bore 11 communicate with each other. The communication path 14 becomes a passage for transferring the refrigerant to the cylinder bore 13.

In addition, the piston 15 is installed inside the cylinder bore 13 to enable a straight reciprocating motion. The piston 15 has a cylindrical shape, and the cylinder bore 13 has a cylindrical shape corresponding thereto. One end portion of the piston 15, that is, a portion 17 protruding to the outside of the cylinder bore 13 is formed with a connecting portion 17. The piston 15 compresses the refrigerant in the cylinder bore 13.

Meanwhile, the front housing 20 is installed at the front end of the cylinder block 10. The front housing 20 cooperates with the cylinder block 10 to form a crank chamber 21 therein. The crank chamber 21 is kept airtight with the outside. The front housing 20 is formed through the shaft hole 23 in the front and rear.

The rear housing 30 is installed at the rear end of the cylinder block 10, that is, on the opposite side to which the front housing 20 is installed. The rear housing 30 is formed with a suction chamber 31 in selective communication with the cylinder bore 13. The suction chamber 31 is formed in an area corresponding to the center of the surface facing the cylinder block 10 of the rear housing 30. The suction chamber 31 serves to deliver the refrigerant to be compressed into the cylinder bore 13.

A discharge chamber 33 is formed in the rear housing 30. The discharge chamber 33 is also in selective communication with the cylinder bore 13. The discharge chamber 33 is formed at a position adjacent to an edge of a surface of the rear housing 30 that faces the cylinder block 10. The discharge chamber 33 is a place where the refrigerant compressed in the cylinder bore 13 is discharged and temporarily stays. One side of the rear housing 30 is provided with a control valve 35. The control valve 35 is a configuration for adjusting the angle of the swash plate 48 to be described below.

The bolt 37 is fastened to fasten the cylinder block 10, the front housing 20, and the rear housing 30 to each other. A plurality of bolts 37 are fastened through the edges of the cylinder block 10, the front housing 20 and the rear housing 30 simultaneously.

The drive shaft 40 is rotatably installed through the center bore 11 of the cylinder block 10 and the shaft hole 23 of the front housing 20. The drive shaft 40 is rotated by the driving force transmitted from the engine. The drive shaft 40 is rotatably installed in the cylinder block 10 and the front housing 20. The flow path 41 is formed inside the drive shaft 40. The flow passage 41 is opened to the rear end of the drive shaft 40 to communicate with the suction chamber 31. In addition, the flow passage 41 serves as a passage for transferring the refrigerant delivered to the suction chamber 31 into the cylinder bore 13.

The rotor 44 is installed in the crank chamber 21 so that the drive shaft 40 passes through the center and rotates integrally with the drive shaft 40. The rotor 44 is fixed to the drive shaft 40 in a substantially disk shape and is installed.

The drive shaft 40 is installed so that the swash plate 48 is hinged to the rotor 44 and rotated together. The swash plate 48 is installed at a variable angle to the drive shaft 40 according to the discharge capacity of the compressor. In other words, the driving shaft 40 is orthogonal to the longitudinal direction or inclined at a predetermined angle with respect to the driving shaft 40.

The swash plate 48 has its edge 50 connected to the pistons 15 via a shoe 50. That is, the edge of the swash plate 48 is connected to the connecting portion 17 of the piston 15 via the shoe 50 so that the piston 15 is linearly reciprocated in the cylinder bore 13 by the rotation of the swash plate 48. Try to exercise.

Meanwhile, a valve assembly 60 is provided between the cylinder block 10 and the rear housing 30 to control the flow of the refrigerant between the suction chamber 31 and the discharge chamber 33 and the cylinder bore 13. That is, the valve assembly 60 controls the refrigerant flow from the suction chamber 31 to the cylinder bore 13 and from the cylinder bore 13 to the discharge chamber 33.

The valve assembly 60 is provided with a valve plate 62. The valve plate 62 is substantially disk-shaped, the gasket 63 is coupled to the front surface. The gasket 63 is coupled to the valve plate 62 for sealing, and serves to prevent the refrigerant from leaking out.

Both sides of the valve plate 62 are provided with suction leads 64 and discharge leads 66, respectively. The suction lead 64 and the discharge lead 66 are made of a metal that is elastically deformable, and elastically deformed according to the pressure of the refrigerant in the cylinder bore 13 so that the discharge hole 70 and the suction hole will be described below. It serves to open and close 71.

3 shows an enlarged view of the configuration between the cylinder bore 13 and the discharge chamber 33. Referring to this, when the discharge lead 66 is based on the drawings, the lower end is fixed to the rear housing 30, the elastic deformation occurs around the upper end. That is, when the pressure inside the cylinder bore 13 is higher than the discharge chamber 33, the discharge lead 66 opens the discharge hole 70 while the upper end is elastically deformed by the pressure of the refrigerant, so that the refrigerant discharges the discharge chamber 33. To be discharged. Meanwhile, a regulating gasket 68 is provided to closely contact the discharge lead 66. The regulating gasket 68 serves to regulate a range in which the discharge lead 66 is elastically deformed.

The discharge hole 70 is formed between the cylinder bore 13 and the discharge chamber 33 and is formed through the valve plate 62. A plurality of discharge holes 70 are formed, respectively, and are formed at positions corresponding to the cylinder bores 13. In the present embodiment, the discharge hole 70 is enlarged toward the rear to reduce the discharge resistance. In other words, the front end portion of the discharge hole 70 has a constant diameter so that the flow cross-sectional area of the refrigerant is constant, and the expansion portion 72 is formed at the rear end portion so that the diameter of the discharge hole 70 increases toward the rear side.

Meanwhile, a suction hole 71 is formed between the cylinder bore 13 and the suction chamber 31. The suction holes 71 are formed through the valve plate 62, and a plurality of suction holes 71 may be formed at positions corresponding to the cylinder bores 13.

At this time, the diameter of the extension portion 72 is formed to increase only in the portion adjacent to the end of the discharge lead (66). That is, when viewed from the side, the flow path formed by the discharge hole 70 is formed to increase the flow cross-sectional area at the rear end, in particular, the flow cross-sectional area is increased around the portion adjacent to the end of the discharge lead (66). As such, the expansion portion 72 is formed in the discharge hole 70 to reduce the discharge resistance of the refrigerant.

Specifically, since the discharge lead 66 is most elastically deformed at the end, a flow path is formed so that refrigerant is concentrated in this portion so that the discharge lead 66 can be opened more easily, and the discharge lead ( 66) It is to reduce the discharge pressure received by the whole. In this embodiment, the extension portion 72 is formed to have a curved surface to allow the refrigerant to flow smoothly along the extension portion 72.

Meanwhile, FIG. 4 is a cross-sectional view schematically showing a main configuration A of the swash plate compressor according to another embodiment of the present invention. Referring to this, it can be seen that the shape of the extension portion 82 'is different from the above-described embodiment. In this embodiment, the extension portion 82 'is formed to have a flat surface. As a result, extension portions 82 and 82 'having a flow cross-sectional area increasing toward the rear of the discharge hole 70 may be formed, which is not necessarily limited to the shape of the above-described embodiment.

Hereinafter, the operation of the swash plate compressor according to the present invention having the configuration as described above in detail.

Referring to the process of the refrigerant is discharged in the swash plate compressor according to the present invention, the swash plate 48 is rotated together with the rotary shaft 40 as the rotary shaft 40 is rotated by a driving force transmitted from the outside. Rotation of the swash plate 48 allows the piston 15 to make a linear reciprocating motion inside the cylinder bore 13.

At this time, as the rotating shaft 40 rotates, the refrigerant in the suction chamber 31 is sequentially sucked into each cylinder bore (13). As such, when the refrigerant is delivered to the cylinder bore 13, the piston 15 of the corresponding cylinder bore 13 moves in the direction of the valve assembly 60, and compression of the refrigerant occurs.

As such, when the refrigerant is compressed in the cylinder bore 13, the pressure inside the cylinder bore 13 is relatively higher than the discharge chamber 33 and the refrigerant is discharged to the discharge chamber 33.

Referring to FIG. 2, the discharge hole 70 is formed such that the flow cross-sectional area is not constant over the entire discharge hole 70 and expands toward the rear end as in the related art. In particular, since the expansion portions 72 and 72 'are formed so that the portion adjacent the end of the discharge lead 66 is enlarged, the refrigerant is concentrated toward the expansion portions 72 and 72' as shown by the arrow. When the refrigerant is concentrated at the end of the discharge lead 66, the discharge lead 66 is elastically deformed around the other end by the discharge pressure, and the discharge lead 66 is bent in the dotted line direction. At this time, the elastic deformation range of the discharge lead 66 is regulated by the regulation gasket (68).

In this way, since the extension portions 72 and 72 'are formed at the end of the discharge lead 66, the discharge resistance applied to the discharge lead 66 is reduced, thereby reducing the power consumption of the compressor 1.

When the inclination angle of the swash plate 48 is changed by the control valve 35, the amount of refrigerant compressed in the cylinder bore 13 is variable, so that the discharge amount of the refrigerant may be varied.

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 a discharge port portion of the swash plate compressor according to the prior art.

Figure 2 is a cross-sectional view showing the configuration of a preferred embodiment of a swash plate compressor according to the present invention.

Figure 3 is a schematic cross-sectional view showing the main portion (A) of the swash plate compressor according to a preferred embodiment of the present invention.

Figure 4 is a schematic cross-sectional view showing the main portion (A) of the swash plate compressor according to another embodiment of the present invention.

Explanation of symbols on the main parts of the drawings

10: cylinder block 11: center bore

13: cylinder bore 14: communication path

15: piston 17: connection

20: front housing 21: crankcase

23: shaft hole 30: rear housing

31: suction chamber 33: discharge chamber

35 control valve 37 bolt

40: drive shaft 41: flow path

44: rotor 48: swash plate

50: shoe 60: valve assembly

62: valve plate 63: gasket

64: suction lead 66: discharge lead

68: regulated gasket 70: discharge hole

71: suction hole 72,72 ': extension part

Claims (4)

A cylinder block 10 in which a plurality of cylinder bores 13 on which the piston 15 linearly reciprocates along the rotational motion of the swash plate 48 are formed; A front housing (20) installed at the front end of the cylinder block (10) and coupled to the cylinder block (10) to form a crank chamber (21) therein; A discharge chamber 33 is formed at the rear end of the cylinder block 10 and communicates with the cylinder bore 13, and a flow path through which the refrigerant is discharged between the cylinder bore 13 and the discharge chamber 33. A rear housing 30 in which a phosphorus discharge hole 70 is formed; A drive shaft 40 penetrating the cylinder block 10 and rotatably installed at both ends of the front and rear housings 20 and 30; It includes a valve assembly 60 that controls the flow of the refrigerant between the cylinder block 10 and the rear housing 30, the discharge lead 66 for opening and closing the discharge hole 70 is elastically deformable In the swash plate type compressor, An expansion portion 72 is formed in the discharge hole 70 to increase the flow cross-sectional area toward the rear, and the expansion portion 72 is formed at a portion adjacent to the end of the discharge lead 66. compressor. The method of claim 1, The expansion unit 72 is a swash plate compressor characterized in that it is formed to have a curved surface or plane toward the rear. The method according to claim 1 or 2, The discharge lead (66) is a swash plate compressor, characterized in that the elastic deformation range is regulated by a regulating gasket (68) provided in the valve assembly (60). The method of claim 1, The drive shaft (40), the swash plate-type compressor, characterized in that the flow path (41) formed therein to transfer the refrigerant delivered to the suction chamber (31) into the interior of the cylinder bore (13).

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