KR20110072317A

KR20110072317A - Variable displacement swash plate type compressor

Info

Publication number: KR20110072317A
Application number: KR1020090129194A
Authority: KR
Inventors: 송세영; 윤영섭
Original assignee: 한라공조주식회사
Priority date: 2009-12-22
Filing date: 2009-12-22
Publication date: 2011-06-29

Abstract

PURPOSE: A capacity-variable swash-plate compressor is provided to minimize the leakage of refrigerant using an oil groove formed on the outer surface of the valve unit of a driving shaft. CONSTITUTION: A capacity-variable swash-plate compressor comprises a cylinder block, a piston, a front housing, a rear housing, a driving shaft(140) and a swash plate. The cylinder block comprises a plurality of cylinder bores. The piston compresses working fluid. The front housing is coupled to the front of the cylinder block and forms a crank chamber. The rear housing is coupled to the rear of the cylinder block and forms a suction chamber and a discharge chamber. The driving shaft is rotatably supported on the front housing and the cylinder block. A fluid path(141') communicating with the suction chamber is formed in one end of the driving shaft. A fluid outlet(142) is formed on the side of one end of the driving shaft.

Description

Variable displacement swash plate type compressor

The present invention relates to a variable displacement swash plate type compressor, and more particularly, to a variable displacement swash plate type compressor having improved sealing at a valve portion of a drive shaft and improved wear on the outer circumferential surface of the valve portion.

As a compressor used in a vehicle air conditioner or the like, there is a variable displacement swash plate type compressor (hereinafter referred to as a compressor) capable of variably controlling the discharge capacity.

1 is a cross-sectional view of a variable displacement swash plate compressor according to the prior art.

The variable displacement swash plate type compressor includes a cylinder block 10 in which a plurality of cylinder bores 11 are disposed radially, and a front housing 30 coupled to the front of the cylinder block 10 to form a crank chamber C. And, it is coupled to the rear of the cylinder block 10 includes a rear housing 50 to form a suction chamber (S) and the discharge chamber (D). In fact, a plurality of bolts B are fastened through the front housing 30, the cylinder block 10, and the rear housing 50 to complete the assembly of the compressor.

The cylinder block 10 has a plurality of cylinder bores 11 are formed at regular intervals around the edge of the cylinder block 10, in fact the cylinder bore 11 is to pass through the cylinder block 10 have. The pistons 15 are respectively accommodated in the cylinder bores 11 to linearly reciprocate, thereby compressing the working fluid introduced into the cylinder bores 11.

The crank chamber C is made between the front housing 30 and the cylinder block 10 as the rear of the front housing 30 is concave. Inside the crank chamber (C) is provided with components for reciprocating the piston (15).

First, the drive shaft 40 is rotatably installed in the center bore 12 formed in the center of the cylinder block 10 through the shaft hole 32 of the front housing 30. The drive shaft 40 is rotated by a driving force transmitted from an engine of a vehicle, a drive motor for a vehicle, or a drive motor for a compressor separately provided.

And inside the crank chamber (C), a rotor (43) through which the drive shaft (40) passes through the center and rotates together with the drive shaft (40) is provided. The rotor 43 is formed in a substantially disk shape, and one side of the rotor 43 is formed to protrude.

In addition, the drive shaft 40 is provided with a swash plate 45 for reciprocating the piston (15). The swash plate 45 may change an inclination angle with respect to the drive shaft 40 according to the discharge capacity of the compressor. Here, the inclination angle of the swash plate 45 means an angle formed by a surface orthogonal to the drive shaft 40 and a surface of the swash plate 45. That is, the swash plate 45 is changed to a state inclined at a predetermined range with respect to the drive shaft 40.

On one side of the swash plate 45, a connecting arm 46 which is connected to the hinge arm 44 of the rotor 43 is formed to protrude. The connecting arm 46 and the hinge arm 44 are connected by the hinge pin 47 so as to accommodate an angle change of the swash plate 45.

The edge portion of the swash plate 45, that is, the outer circumferential portion, is coupled between the shoes 18 of the connecting portion 17 protruding in front of the piston 15. When the swash plate 45 is rotated in an inclined state, as the outer peripheral portion passes between the shoes 18, the piston 15 performs a linear reciprocating motion to compress the working fluid.

A radial yarn spring 48 having a predetermined elastic force is installed on the drive shaft 40 between the swash plate 45 and the rotor 43. The radial yarn spring 48 presses the swash plate 45 such that the inclination angle of the swash plate 45 increases, that is, the inclination of the swash plate 45 increases.

On the other hand, between the cylinder block 10 and the rear housing 50 is provided with a valve assembly 60 for controlling the flow of the refrigerant between the discharge chamber (D) and the cylinder bore (11).

The flow of the refrigerant in the embodiment of the present invention will be briefly described with reference to FIG. 1. First, a valve portion 41 is formed at one end of the drive shaft 40. The valve portion 41 is a portion supported by the center bore 12. Inside the valve portion 41, a flow passage 41 'is formed in communication with the suction chamber (S). In addition, a flow path outlet 42 for communicating the flow passage 41 ′ with the outside is formed at one side surface of the valve portion 41. The flow path outlet 42 is connected to the communication path 14 for communicating the cylinder bore 11 and the center bore 12 as the drive shaft 40 is rotated.

By such a configuration, the refrigerant in the suction chamber S flows into the flow passage 41 ′ in the drive shaft 40 through the rear end of the drive shaft 40, and the flow passage outlet 42 and the cylinder block of the drive shaft 40 are inclined. The refrigerant inside the drive shaft 40 is delivered to the cylinder bore 11 at the moment when the communication paths 14 formed in the 10 communicate with each other. The refrigerant delivered to the cylinder bore 11 is compressed by the piston 15, and the compressed refrigerant is discharged to the discharge chamber D under the control of the valve assembly 60.

However, in the structure in which the refrigerant in the suction chamber S is transferred to the cylinder bore 11 through the flow passage 41 'formed inside the drive shaft 40, the valve portion 41 having the flow passage 41' is formed. The leakage of the refrigerant occurs through the gap formed between the outer surface of the center block and the center bore 12 of the cylinder block 10. Such leakage of the refrigerant has a problem of lowering the compression efficiency.

An object of the present invention is to solve the problems of the prior art as described above, to minimize the refrigerant leakage between the outer surface of the drive shaft and the center bore of the cylinder block.

According to a feature of the present invention for achieving the above object, the present invention is a cylinder block having a plurality of cylinder bores radially, a piston installed in the cylinder bore to compress the working fluid by linear reciprocating movement, and A front housing coupled to the front of the cylinder block to form a crank chamber therein; a rear housing coupled to the rear of the cylinder block to form a suction chamber and a discharge chamber therein; and rotatably supported by the front housing and the cylinder block. A flow passage communicating with the suction chamber is formed in one end portion, and a driving shaft having a flow passage outlet through which the flow passage communicates with the outside at one end portion thereof, and coupled to the drive shaft in the crank chamber to rotate together with the piston And including a swash plate to transmit power thereto; The outer surface of the valve portion rotatably supported by the cylinder block in the drive shaft is characterized in that the oil groove for retaining the oil or refrigerant containing oil is formed concave.

Here, the oil groove may be formed in a circular shape.

According to the present invention, an oil groove for retaining oil is formed in the valve outer surface of the drive shaft so that an oil film is formed on the valve outer surface when the drive shaft rotates. Since the oil film thus formed prevents a gap between the outer surface of the valve portion and the center bore, leakage of the refrigerant through the gap is minimized. Therefore, the compression performance of the compressor is improved.

In addition, wear of the outer surface of the valve portion is prevented by the oil film. Therefore, the durability of a valve part also improves.

Hereinafter, the present invention will be described in more detail with reference to the embodiments shown in the drawings.

The practical structure of the variable displacement compressor is the same as that shown in FIG. Since the structure of the variable displacement compressor has been described above, a detailed description thereof will be omitted, and reference numerals of FIG. 1 are referred to for the same configuration except for the driving shaft.

2 is a partial perspective view of a preferred embodiment of a drive shaft constituting the present invention.

The drive shaft 140 shown in FIG. 2 is a component rotatably installed through the center bore 12 of the cylinder block 10 and the shaft hole 32 of the front housing 30. The drive shaft 140 is rotated by the driving force transmitted from the engine.

One end of the drive shaft 140 is formed with a valve portion 141 rotatably supported inside the center bore 12. The flow path 141 ′ communicating with the suction chamber S is formed in the valve part 141. The flow path 141 ′ is formed to be opened to one end of the valve part 141. In addition, a flow path outlet 142 for communicating the flow path 141 ′ and the communication path 14 is formed at a side surface of the valve unit 141.

In addition, a plurality of oil grooves 190 are formed concave on the outer surface of the valve unit 141. The plurality of oil grooves 190 are formed at regular intervals from each other. The oil groove 190 is formed through forging or rolling. In the embodiment shown in Figure 2 the oil groove 190 is formed in a circular shape. However, the shape of the oil groove 190 is not necessarily limited to the circle.

The oil groove 190 includes oil for cooling and lubricating while circulating inside the compressor so that an oil film is formed on the outer surface of the valve unit 141. That is, the oil does not flow along the outer surface of the valve unit 141 but stays in the oil groove 190, and as a result, an oil film is formed on the outer surface of the valve unit 141. In particular, when the drive shaft 140 rotates during the operation of the compressor, the oil film is more surely made.

Of course, not only the oil but also the refrigerant may be seated in the oil groove 190. Similarly, an oil film may be formed on the outer surface of the valve unit 141 by the refrigerant seated in the oil groove 190.

Since the gap between the outer surface of the valve portion 141 and the center bore 12 is reduced by the oil film formed on the outer surface of the valve portion 141, leakage of the refrigerant through the gap is minimized. In addition, wear of the outer surface of the valve unit 141 is prevented by the oil film.

Hereinafter, a process of compressing a refrigerant by the variable displacement swash plate compressor according to the embodiment of the present invention will be described with reference to FIGS. 1 and 2.

When the drive shaft 140 is rotated by the driving force of the engine, the rotor 43 rotates together, and the swash plate 45 rotates by the rotor 43. The rotation of the swash plate 45 is transmitted to the piston 15 through the shoe 18 to be converted into a linear reciprocating motion of the piston 15.

The piston 15 compresses the refrigerant in the cylinder bore 11 as the linear reciprocating motion. At this time, the stroke distance of the piston 15 is determined according to the angle of the swash plate 45. The angle of the swash plate 45 may be adjusted by the pressure of the refrigerant delivered into the crank chamber (C).

On the other hand, it will be described that the refrigerant is delivered into the cylinder bore (11). The refrigerant delivered from the outside to the suction chamber S is transferred to the flow path 141 ′ provided in the valve unit 141 of the drive shaft 140. As the refrigerant delivered to the flow path 141 ', the flow path outlet 142 is connected to each cylinder bore 11 and each communication path 14 according to the rotation of arrow B direction (see FIG. 2) of the drive shaft 140. It is transmitted to each cylinder bore 11 by being sequentially communicated through.

At this time, in the process of the refrigerant is delivered into the cylinder bore 11 through the flow path outlet 142 and the communication path 14, some of the refrigerant may be counted to the outer surface of the valve portion 141.

However, in the present embodiment, as the driving shaft 140 rotates while the oil groove 190 formed on the outer surface of the driving shaft 140 contains oil or a refrigerant including oil, as shown in FIG. An oil film is formed on the outer surface. Since the clearance between the outer surface of the valve portion 141 and the inner surface of the center bore 12 is reduced by the oil film, leakage of the refrigerant through the clearance is minimized.

In addition, in the present embodiment, the wear phenomenon generated on the outer surface of the valve portion 141 and the inner surface of the center bore 12 is minimized by the oil film formed on the outer surface of the valve portion 141. This improves the durability of the compressor.

Meanwhile, the refrigerant delivered to the cylinder bore 11 and compressed by the piston 15 is delivered to the discharge chamber D by the valve assembly 60 and to the outside of the compressor.

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 variable displacement swash plate compressor according to the prior art.

Figure 2 is a partial perspective view showing a preferred embodiment of the drive shaft constituting the present invention.

Explanation of symbols on the main parts of the drawings

10: cylinder block 12: center bore

14: communication path 30: front housing

50: rear housing 140: drive shaft

141: valve portion 141 ': flow path

142: Euro exit 190: Oil groove

C: crank chamber S: suction chamber

Claims

A cylinder block 10 having a plurality of cylinder bores 11 radially;

A piston (15) installed in the cylinder bore (11) to compress the working fluid by linear reciprocating motion;

A front housing 30 coupled to the front of the cylinder block 10 to form a crank chamber C therein;

A rear housing 50 coupled to the rear of the cylinder block 10 to form a suction chamber S and a discharge chamber D therein;

A flow path 141 ′ rotatably supported by the front housing 30 and the cylinder block 10 and communicating with the suction chamber S is formed at one end thereof, and at one end side thereof, the flow path 141 ′. A drive shaft 140 in which a flow path outlet 142 communicating with outside is formed, and

A swash plate (45) coupled to the drive shaft (140) in the crank chamber (C) to rotate together and transmit power to the piston (15);

Variable capacity, characterized in that the oil groove 190 for retaining the oil or the refrigerant containing oil is formed in the outer surface of the valve unit 141 rotatably supported by the cylinder block 10 in the drive shaft 140 Type swash plate compressor.

The variable displacement swash plate compressor of claim 1, wherein the oil groove (190) is circular.