KR20080029032A - Oil separation structure of compressor - Google Patents

Abstract

An oil separation structure of a compressor is provided to form an oil groove and a bead in a gasket for restoring oil remaining in a head discharge part to a crank chamber and to restore the oil moved along the bead to the crank chamber via a bolt hole. An oil separation structure of a compressor includes a valve unit, a head gasket, and a suction gasket(185) having through-holes(210) respectively for moving oil remaining in a head discharge part of refrigerant, oil grooves(220) extended from the through-holes at a lower part of the suction gasket to a circular bead(230), the bead connected to the oil grooves and formed along an outer peripheral part of the suction gasket, and connection grooves(240) formed at an upper part of the suction gasket and extended from the bead to bolt coupling holes(123G).

Description

Oil Separation Structure of Compressor {OIL SEPARATION STRUCTURE OF COMPRESSOR}

1 is a cross-sectional view of a fixed displacement swash plate type compressor as an example of a general compressor.

2 is a cross-sectional view of a compressor oil separator according to the prior art.

3 is a cross-sectional view of an RSV compressor as an example of a compressor to which the present invention may be applied.

Figure 4 is a perspective view showing a valve unit of the front housing side of the conventional compressor.

5 is a plan view showing a suction gasket of the compressor according to the present invention.

Figure 6 is a partially cutaway perspective view showing a state in which the valve unit is coupled to the front housing of the compressor according to the present invention.

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

100: compressor 110: front housing

111,121: discharge chamber 112,122: fixing hole

113,123: Bolted hole 120: Rear housing

130: front cylinder block 131,141: cylinder bore

132,142: suction passage 133,143: shaft support hole

134,144: discharge passage 135,145: muffler

136: swash chamber 140: rear cylinder block

147: discharge port

150: drive shaft 151: flow path

152: entrance 153: exit

160: Saphan 161: Hub

165: shoe 170: piston

180: valve unit 181: valve plate

181a: refrigerant discharge hole 181b: communication path

182: discharge lead valve 183: fixed pin

190: bolts

185: suction gasket 186: head gasket

123G: Bolt tightening hole 131H: Cylinder bore hole

133G: Shaft Supporters

210: through hole 220: oil groove

230: Bead 240: Connection groove

The present invention relates to an oil separation structure of a compressor, and more particularly, oil separation of a swash plate type compressor which recovers oil mixed in refrigerant gas discharged to the head discharge part of an automobile compressor and supplies it to the friction part of the compressor of the compressor. It's about structure.

In general, a compressor for automobiles sucks refrigerant gas discharged after evaporation is completed from an evaporator, converts the refrigerant gas into a refrigerant gas in a high temperature and high pressure state that is easily liquefied, and discharges the refrigerant gas.

There are various types of such compressors, such as a swash plate compressor in which a piston reciprocates by the rotation of an inclined swash plate, a scroll compressor compressing by a rotational movement of two scrolls, and a vane rotary compressor compressing by a rotary vane. .

Among these, reciprocating compressors compressing refrigerant according to the reciprocating motion of pistons include crank compressors and wobble plate compressors as well as swash plate compressors. Capacitive swash plate compressor;

1 is a view showing a conventional fixed displacement swash plate type compressor, briefly described with reference to the following.

As shown, the swash plate compressor (1) is coupled to the front housing 10, the front cylinder block 20, the front housing 10, the rear housing (20a) is built in the rear housing ( 10a).

Inside the front and rear housings 10 and 10a, the discharge chamber 12 and the suction chamber are respectively located inside and outside the partition 13 in correspondence with the refrigerant discharge hole and the refrigerant suction hole of the valve plate 61 to be described below. (11) is formed.

On the other hand, a plurality of bolted fastening holes 16 are formed in the circumferential direction of the suction chamber 11. Through the bolt fastening hole 16, the front and rear housings 10 and 10a are fastened / fixed with the bolt 80 in a state where a plurality of components are assembled therein.

In addition, the front and rear cylinder blocks 20 and 20a have a plurality of cylinder bores 21 formed therein, and the cylinder bores 21 of the front and rear cylinder blocks 20 and 20a corresponding to each other have a piston ( The pistons 50 are coupled in a straight line with the pistons to linearly reciprocate therein, and the pistons 50 are coupled to the outer circumference of the swash plate 40 inclinedly coupled to the drive shaft 30 via the shoe 45.

Accordingly, the pistons 50 reciprocate inside the cylinder bore 21 of the front and rear cylinder blocks 20 and 20a in conjunction with the swash plate 40 rotating together with the drive shaft 30.

The valve unit 60 is installed between the front and rear housings 10 and 10a and the front and rear cylinder blocks 20 and 20a.

Here, the valve unit 60 is composed of a valve plate 181 having a refrigerant suction hole and a refrigerant discharge hole, and a suction gasket 63 and a head gasket 62 installed at both sides thereof.

The valve unit 60 is assembled between the front and rear housings 10 and 10a and the front and rear cylinder blocks 20 and 20a, respectively, in which fixing pins 65 are formed on both sides of the valve plate 61. ) Is assembled in a fixed position while being inserted into the fixing holes 15 formed on the opposite surfaces of the front and rear housings 10 and 10a and the front and rear cylinder blocks 20 and 20a.

When the power of the engine is transmitted to the drive shaft of the compressor configured as described above, the pistons move forward and backward by the swash plate rotating in an inclined state together with the drive shaft. During the piston's forward and backward movement, the refrigerant is sucked into the cylinder bore through the valve unit, and during the piston stroke, the refrigerant is compressed and discharged through the valve unit.

In order to facilitate the operation of such a compressor, the refrigerant contains oil to lubricate the surfaces where the mechanical friction occurs, such as the gap between the piston and the cylinder bore, as the oil circulates with the refrigerant to each part of the system during system operation.

However, when the oil is introduced into a heat exchanger or expansion device such as a condenser, pipes and hoses, the oil is coated on the inner wall of the oil flow path such as a heat exchanger, or occupies a predetermined space of the heat exchanger of the refrigerant, thereby reducing the refrigerant fluidity. In addition to lowering the heat exchange efficiency of the machine, the pressure drop increases, and thus, the system is adversely affected by increasing the amount of power required for driving. In addition, when the oil circulates through the entire system, the amount of oil supplied to the compressor is fluctuated so that the lubrication of the compressor is not stable and smooth, and the durability of the compressor is reduced. On the other hand, when a large amount of oil is used to prevent this, the oil loses its inherent function of the refrigerant, which further affects the system.

In order to solve the above problems, the air conditioner is usually used to separate the oil from the refrigerant compressed and discharged from the compressor discharged to return to the compressor.

2 is an example of a conventional oil separator equipped with a compressor, and shows a compressor oil integrated separator proposed in Japanese Patent Laid-Open No. 5-240158.

As shown, the compressor-integrated oil separator separates and stores oil from the refrigerant discharged from the cylinder bore, and is parallel to the oil storage chamber 92 so as to maintain a pressure difference in the oil storage chamber 92. The oil supply chamber 94 for introducing and storing the oil flowing out through the pipeline 93 and the crank chamber 98 formed by the oil supply chamber 94 and the housing 91 are connected to each other. An oil supply passage 96 for guiding oil to the crank chamber 98, and a flow control valve 95 installed at an inlet of the oil supply passage 96 of the oil supply chamber 94 to control the amount of oil; It is made to include.

However, since the oil separator chamber 92 and the oil supply chamber 94 must be parallel to each other in the housing 91 of the compressor, the oil separator chamber of the compressor has a limitation in enlarging the size of the oil reservoir chamber 92. There is a problem in that the oil can not be stored, and when the oil storage chamber is enlarged to secure an oil storage amount, the size of the compressor 90 becomes large so that it is difficult to mount the compressor 90 in a vehicle.

In addition, as can be seen in Figure 2, when the vehicle body is tilted and the compressor 90 is inclined, the water level of the oil 97 stored in the oil storage chamber 92 is changed from A to B while the pipeline 93 There is a problem that the compressor (90) is damaged because the inlet (99) is opened and the refrigerant gas (not the oil) is introduced through the inlet (99) and supplied to the crank chamber (98).

The present invention has been made in order to solve the above problems, in order to return the residual oil of the head discharge portion of the swash plate compressor to the crank chamber to form an oil groove and a bead in the gasket and the oil flowing through the bead through the bolt hole It is an object of the present invention to provide an oil separation structure of a swash plate compressor capable of returning to a crank chamber.

According to the oil separation structure of the compressor according to the present invention devised to achieve the above object, the front and rear housings each formed with a discharge chamber therein; A front and rear cylinder block having a cylinder bore and coupled between the front and rear housings; A drive shaft installed and rotated to penetrate the center of the front and rear housings and the front and rear cylinder blocks; A swash plate fixed to an outer circumferential surface of the drive shaft and rotatably installed in the swash plate chamber of the compressor; A piston interposed on the swash plate and movably installed in the cylinder bore according to rotation thereof to compress the refrigerant; Valve units installed on both side surfaces of the front and rear cylinder blocks; A head gasket installed at the front housing side of the valve unit; In the swash plate compressor comprising a suction gasket provided on the cylinder bore side of the valve unit,

A through hole through which the head discharge portion of the refrigerant gas formed under the valve unit, the head gasket, and the suction gasket moves; An oil groove formed from a through hole in the lower portion of the suction gasket to a circular bead; A bead communicating with the oil groove and formed along an outer circumference of the suction gasket; And a connection groove formed on the suction gasket from the bead to the bolt fastening hole.

In addition, it is preferable that at least two through-holes are formed to communicate with the cylinder bores located below the front and rear cylinder blocks of the cylinder bores.

Preferably, the beads form a circular flow path, and the circular flow path is recessed from the housing side to the cylinder block side to form a semicircular cross section.

In addition, it is preferable that the diameter of the said semicircular cross section exists in the range of 0.5-1.5 mm.

According to another embodiment of the present invention, the drive shaft has a flow path formed therein so that the refrigerant sucked into the swash plate chamber can move through the swash plate to the cylinder bore, and the flow path communicates with the swash plate chamber. At least one or more inlets are formed, respectively, and a pair of outlets are spaced apart from the inlet and formed in opposite directions, and the front and rear cylinder blocks are configured to sequentially cool the refrigerant sucked into the flow path of the drive shaft when the drive shaft rotates. And a suction passage communicating the shaft support hole and each cylinder bore so as to be sucked into each cylinder bore, and the valve unit is a plurality of refrigerants to communicate the discharge chambers of the cylinder bore and the front and rear housings. A valve plate having a discharge hole formed therein, and a soil plate installed at one side of the valve plate to open and close the refrigerant discharge hole. Characterized by consisting of a reed valve.

The features and advantages of the present invention will become more apparent from the following detailed description based on the accompanying drawings. Prior to this, the terms or words used in the present specification and claims are based on the principle that the inventor can appropriately define the concept of terms in order to explain the invention in the best way. It should be interpreted as meanings and concepts corresponding to

3 is a cross-sectional view of an RSV compressor as an example of a compressor to which the present invention can be applied, and FIG. 4 is a perspective view showing a front housing side valve unit of the compressor according to the prior art, and FIG. 5 is a suction gasket of the compressor according to the present invention. 6 is a partially cutaway perspective view illustrating a state in which a valve unit is coupled to a front housing of a compressor according to the present invention.

As shown in FIG. 3, the swash plate compressor 100 of the rotary suction valve type according to an embodiment of the present invention is a swash plate rotating in the swash plate chamber 136 inside the compressor 100. Drive shaft 150 is inclined coupled to 160, the front and rear cylinder blocks (130, 140) rotatably installed in the shaft support holes (133, 143) and the outer circumference of the swash plate 160 It is mounted via the shoe 165 to the reciprocating inside the cylinder bore (131, 141) formed on both sides of the swash plate chamber 136 of the front and rear cylinder block (130, 140) in conjunction with the rotational movement of the swash plate 160 The front and rear housings 110 and 120 are coupled to both of the plurality of pistons 170 and the front and rear cylinder blocks 130 and 140 and the discharge chambers 111 and 121 are formed therein, respectively. The valve unit 180 is interposed between the front and rear cylinder blocks 130 and 140 and the front and rear housings 110 and 120, respectively.

First, both sides of the drive shaft 150 are rotatably installed in the shaft support holes 133 and 143 of the front and rear cylinder blocks 130 and 140, and one end thereof extends through the front housing 110. It is combined with an electronic clutch (not shown).

The swash plate 160 rotating in the swash plate chamber 136 is inclined to the drive shaft 150, and is sucked into the swash plate chamber 136 through the suction port 146 of the rear cylinder block 140. A flow path 151 is formed in communication with the swash plate chamber 136 and the cylinder bores 131, 141 so that the suction refrigerant can move through the swash plate 160 to the cylinder bores 131, 141.

The inlet 152 of the flow path 151 is formed to communicate with the swash plate chamber 136, the outlet 153 is the respective suction passages 132, of the front and rear cylinder blocks 130, 140 to be described below 142).

Here, the inlet 152 of the flow path 151 is formed penetrating through one side of the hub 161 and the drive shaft 150 of the swash plate 160.

Meanwhile, only one inlet 152 of the flow path 151 may be formed on one side of the driving shaft 150, or two may be formed in opposite directions.

In addition, the outlet 153 of the flow path 151 is formed on both sides of the flow path 151 in opposite directions to each cylinder bore 131 provided on both sides of the swash plate chamber 136 when the drive shaft 150 rotates. 141, at the same time the refrigerant can be sucked.

That is, since the swash plate 160 is formed to be inclined, the piston 170 disposed in opposite directions among the piston 170 coupled to the outer circumference of the swash plate 160 performs the same suction or compression stroke, so that the flow path ( Both outlets 153 of the 151 must be formed in opposite directions so that the refrigerant can be sucked into the cylinder bores 131 and 141 provided on both sides of the swash plate chamber 136 at the same time.

Of course, the direction of each outlet 153 of the flow path 151 formed in the drive shaft 150 may vary depending on the design purpose such as the number of the piston 170.

In addition, the front and rear cylinder blocks 130 and 140 are provided with a plurality of cylinder bores 131 and 141, respectively, on both sides of the swash plate chamber 136, and rotatably support the drive shaft 150 at the center thereof. Axial support holes (133, 143) are formed to be.

In addition, the front and rear cylinder blocks (130, 140), the refrigerant sucked into the flow path 151 of the drive shaft 150 in the swash plate chamber 136, each cylinder bore 131 sequentially during the rotation of the drive shaft 150 Suction passages 132 and 142 communicating with the shaft support holes 133 and 143 and the respective cylinder bores 131 and 141 are formed to be sucked into the 141.

In addition, a suction port (not shown) in communication with the swash plate chamber 136 to supply an external refrigerant to the swash plate chamber 136 on the outer surface of one of the front and rear cylinder blocks (130, 140), Discharge ports 147 communicating with the discharge chambers 111 and 121 are formed to discharge the refrigerant in the discharge chambers 111 and 121 of the front and rear housings 110 and 120 to the outside.

Accordingly, the front and rear cylinder blocks 130 and 140 have discharge passages 134 and 144 connecting the discharge chambers 111 and 121 of the front and rear housings 110 and 120 to the discharge port 147. At this time, the outer surface of the cylinder block (130, 140) is formed with a muffler (135, 145) extending the discharge passage (134, 144) to reduce the pulsation pressure of the discharge refrigerant to reduce the noise .

In addition, the valve unit 180 has a plurality of refrigerant discharge holes 181a formed to communicate the cylinder bores 131 and 141 with the discharge chambers 111 and 121 of the front and rear housings 110 and 120. A valve plate 181 and a discharge lead valve 182 installed at one side of the valve plate 181 to open and close the refrigerant discharge hole 181a.

That is, the discharge lead valve 182 is installed in the discharge chambers 111 and 121 of the front and rear housings 110 and 120 based on the valve plate 181 to discharge the refrigerant during the compression stroke of the piston 170. The valve plate is elastically deformed to open the ball 181a and to close the refrigerant discharge hole 181a when the suction stroke is performed.

In addition, the valve plate 181 has refrigerant in the discharge chambers 111 and 121 of the front and rear housings 110 and 120 passing through the discharge passages 134 and 144 of the front and rear cylinder blocks 130 and 140. A communication path 181b for communicating the discharge chambers 111 and 121 and the discharge passages 134 and 144 so as to be discharged to the discharge port 147 is formed.

In addition, the valve unit 180 is a surface in which the fixing pins 183 provided on both sides of the valve plate 181 face the front and rear housings 110 and 120 and the front and rear cylinder blocks 130 and 140. It is coupled to / fixed while being inserted into the fixing holes (112, 122) formed in.

Meanwhile, the front and rear housings 110 and 120 have a plurality of bolt fastening holes 113 and 123 formed at edges thereof, and the front and rear housings 110 through the bolt fastening holes 113 and 123. , 120 is fastened / fixed to the mutual bolt 190 in a state where the above components are assembled.

As shown in FIG. 4, the valve unit 180 includes the valve plate 181 and the discharge lead valve 182 mounted at one side thereof, and the head gasket 186 is disposed at the left and right sides of the valve unit 180. And a suction gasket 185, which is coupled to the front housing of the compressor (110 in FIG. 6). It will be appreciated that the rear housing 120 of the compressor is also coupled in the order of the suction gasket 185, the valve plate 181, the discharge lead valve 182 and the head gasket 186.

As shown in FIG. 6, the refrigerant gas is discharged in the front housing 110 coupled to the valve unit 180, and the oil contained therein accumulates in the lower space formed in the front housing by the difference in specific gravity. Since the pressure in the front housing 110 through which the refrigerant gas is discharged in accordance with the operation of the compressor is higher than the pressure of the compressor operating part such as the cylinder bores 131 and 141, through the oil separation structure according to the present invention by such a pressure difference between the two. Residual oil in the front housing is transferred to the crank chamber of the compressor.

The conventional suction gasket 185 as shown in FIG. 4 has a shaft support ball 133G at the center thereof, and five cylinder bore holes 131H are formed around the cylinder suction hole 131H. Five bolt fastening holes 123G are formed in the grooves. Unlike the conventional suction gasket 185, the suction gasket 185 according to the present invention shown in FIG. 5 further includes a through hole 210, an oil groove 220, a bead 230, and a connection groove 240. Formed.

As shown in FIG. 5, at least two through-holes 210 through which the residual oil in the front housing may move are disposed at left and right sides of the bolt fastening hole 123G under the suction gasket 185 constituting the valve unit 180. It is formed in two places. As shown in FIG. 6, the through hole 210 is formed not only in the suction gasket 185 but also in the valve plate 181 and the head gasket 186 constituting the valve unit 180, so that the inside of the front housing is provided. Residual oil moves through the through hole 210 to the suction gasket 185. The through hole 210 is a hole penetrating the suction gasket 185, but the cylinder bores 131 and 141 of the suction gasket 185 are blocked by the piston 170, and thus move through the through hole 210. One oil cannot enter the cylinder bores 131 and 141 directly.

As shown in FIG. 5, a bead 230 concentric with the outer circumference of the suction gasket 185 and slightly smaller in diameter is formed concave to the rear (cylinder bore side) near the outer circumference of the suction gasket 185. In addition, an oil groove 220 is formed to allow oil to flow from the through hole 210 to the bead 230.

In addition, the two bolt fastening holes 123G formed at the upper portion among the five bolt fastening holes 123G formed in the suction gasket 185 may include a connection groove 240 through which oil may move from the bead 230. It is. As shown in FIG. 3, the front and rear housings 110 and 120 are bolts 190 inserted into and fastened through the bolt fastening holes 123G, and bolt fastening holes 123G of the suction gasket 185. ) And a bolt 190 is formed a constant gap. Therefore, the oil moved from the bead 230 to the bolt fastening hole 123G along the connection groove 240 is moved to the crank chamber of the compressor along this gap.

The through hole 210 is formed in the lower portion of the suction gasket 185 and the bolt fastening hole 123G through which the oil moves is formed in the upper portion of the suction gasket 185. Nevertheless, the oil moved through the through hole 210 and the oil groove 220 is moved in the reverse direction to gravity through the connection groove 240 along the bead 230 to the upper bolt fastening hole 123G This is because the pressure in the crankcase, which is the operating part of the compressor, is lower than the pressure in the front housing 110, and the only passage through which the oil can move is the above-described oil movement path.

In the oil movement path of the present invention, the connection groove 240 connecting the beads 230 to the bolt fastening holes 123G is formed at two bolt fastening holes 123G on the upper side of the suction gasket 185. If the connection groove 240 is formed in the bolt fastening hole 123G in the lower portion of the suction gasket 185, the oil flow path is short and the pressure difference between the head discharge portion and the crank chamber cannot be maintained. Therefore, the bead 230 is formed over the entire circumference of the suction gasket 185, but the oil flow path is formed long so that the oil moves through the two bolt fastening holes (123G) at the top. In this case, since the pressure drops sufficiently while the oil moves along the long flow path of the suction gasket 185, the pressure difference between the head discharge portion and the crank chamber can be maintained. In addition, the dimensions of the bead 230 or the like constituting the oil flow path should be formed so as not to be too large for maintaining this pressure difference, 0.5 to 1.5 mm range is preferred.

In the above embodiment, the oil separation structure according to the present invention is formed in the valve unit 180 on the front housing 110 side, but in the case of a compressor in which a double head piston as shown in FIG. It will be appreciated that the same oil separation function can be performed by forming the oil separation structure according to the present invention in the valve unit 180 on the housing 120 side.

In addition, the scope of the present invention is not limited to these specific embodiments, and those skilled in the art will be able to appropriately change within the scope described in the claims of the present invention.

As described above, according to the oil separation structure of the compressor according to the present invention, there is an effect that oil can be separated by forming an oil separation structure in the valve unit of the compressor without having a separate oil separator.

In addition, in order to return the residual oil of the head discharge part of the swash plate compressor to the crank chamber, an oil groove and a bead may be formed in the gasket, and the oil flowing through the bead may be returned to the crank chamber through the bolt hole.

In addition, it is possible to improve the durability of the compressor and the performance of the air conditioning apparatus by smoothly supplying the oil to the operation portion of the compressor requiring oil.

Claims (5)

Front and rear housings each having a discharge chamber formed therein; A front and rear cylinder block having a cylinder bore and coupled between the front and rear housings; A drive shaft installed and rotated to penetrate the center of the front and rear housings and the front and rear cylinder blocks; A swash plate fixed to an outer circumferential surface of the drive shaft and rotatably installed in the swash plate chamber of the compressor; A piston interposed on the swash plate and movably installed in the cylinder bore according to rotation thereof to compress the refrigerant; Valve units installed on both side surfaces of the front and rear cylinder blocks; A head gasket installed at the front housing side of the valve unit; In the swash plate compressor comprising a suction gasket provided on the cylinder bore side of the valve unit, A through hole 210 through which the head discharge portion residual oil of the refrigerant gas formed under the valve unit, the head gasket, and the suction gasket moves; An oil groove 220 formed from a through hole in the lower portion of the suction gasket to a circular bead; A bead 230 in communication with the oil groove and formed along an outer circumference of the suction gasket; And The oil separation structure of the compressor, characterized in that it comprises a connecting groove 240 formed from the bead to the bolt fastening hole on the upper portion of the suction gasket. The method of claim 1, The through-hole 210, at least two of the cylinder bore, the oil separation structure of the compressor, characterized in that formed in communication with the cylinder bore located in the lower portion of the lower cylinder block. The method of claim 1, The bead 230 forms a circular flow path, wherein the circular flow path is recessed from the housing side to the cylinder block side to form a semicircular cross section, characterized in that the compressor oil separation structure. The method of claim 3, The bead 230, the oil separation structure of the compressor, characterized in that the diameter of the semi-circular cross section is in the range of 0.5 ~ 1.5mm. The method of claim 1, The drive shaft has a flow path 151 formed therein so that the refrigerant sucked into the swash plate chamber can move through the swash plate to the cylinder bore, and the flow path 151 has at least one inlet communicating with the swash plate chamber ( 152 is formed respectively, and a pair of outlets 153 are spaced apart from the inlet 152 in the opposite direction, The front and rear cylinder blocks may have suction passages 132 and 142 communicating with the shaft support hole and each cylinder bore such that the refrigerant sucked into the flow path 151 of the drive shaft may be sequentially sucked into each cylinder bore when the drive shaft rotates. ) Is formed, The valve unit may include a valve plate 181 having a plurality of refrigerant discharge holes formed therein so as to communicate the cylinder bores with the discharge chambers of the front and rear housings, and one side of the valve plate 181 to provide the refrigerant discharge holes. Oil separation structure of the compressor, characterized in that consisting of the discharge lead valve 182 to open and close.

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