KR20110064663A - Scoroll compressor and refrigerator having the same - Google Patents

Abstract

PURPOSE: A scroll compressor and a freezing device applying the same are provided to more stably support a pivot scroll by increasing the sealing force of a back pressure chamber. CONSTITUTION: A scroll compressor comprises a frame, a fixed scroll(50), and a pivot scroll(60). The frame is installed in the internal space of a casing. The fixed scroll is installed on the frame. The pivot scroll is installed between the frame and the fixed scroll, reciprocates in a state of engaging with the fixed scroll and forms a compression chamber. A boss part is formed on one side of the pivot scroll and is coupled to a crank shaft. An oil path(150) passes through the pivot scroll belonging to the inside of the boss part of the pivot scroll. The oil path passes through the bearing surface between the pivot scroll and the fixed scroll. A groove(131) communicated with the outlet of the oil path is formed on the fixed scroll or the pivot scroll.

Description

SCROLL COMPRESSOR AND REFRIGERATOR HAVING THE SAME}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor and a refrigerating machine employing the same, and more particularly, to a scroll compressor for lubricating between both scrolls using oil drawn up while supporting the rear surface of the turning scroll using discharge pressure, and a refrigerating machine using the same. .

A scroll compressor is a compressor which compresses refrigerant gas by changing the volume of a compression chamber formed by a pair of opposed scrolls. Scroll compressors are more efficient than reciprocating compressors or rotary compressors, have low vibration and noise, are compact and lightweight, and thus are widely used in air conditioners.

The scroll compressor can be classified into low pressure type and high pressure type according to the pressure of the refrigerant filling the inner space of the casing. In the low pressure scroll compressor, a suction pipe communicates with an inner space of a casing, and a discharge pipe communicates with a discharge side of the compression unit so that refrigerant is indirectly sucked into the compression chamber. On the other hand, in the high pressure scroll compressor, the suction pipe is directly connected to the suction side of the compression unit, and the discharge pipe is connected to the inner space of the casing so that the refrigerant is directly sucked into the compression chamber. In the case of the low pressure scroll compressor, the inner space of the casing is divided into a suction space and a discharge space, and a compression unit is disposed between the suction space and the discharge space.

In the low pressure scroll compressor, a tip seal method and a back pressure method are widely known as a method for sealing between a fixed scroll and a rotating scroll. The tip seal method is to install a tip seal on the end surface of the wrap of each scroll to seal between the compression chamber while the tip seal is in close contact with the opposite hard plate portion, the back pressure method is to press the back of the fixed scroll or swing scroll to scroll both sides It is to seal between the compression chamber while the wrap and the hard plate portion of the close.

In the method of adding the bottom surface of the turning scroll in the back pressure method as described above, the intermediate pressure hole is formed in the turning scroll in the axial direction so that the medium pressure refrigerant compressed in the compression chamber moves between the turning scroll and the main frame. It is known to allow a medium pressure refrigerant moving between the scroll and the mainframe to support the swing scroll.

In this case, in order to lubricate the bearing surface between the fixed scroll and the swinging scroll, a lubrication hole is formed in the hard plate portion of the swinging scroll in the axial direction to draw oil sucked up in the suction space of the casing scroll. It is known to supply to the fixed scroll side bearing surface.

However, in the low pressure scroll compressor using the conventional back pressure method, the back pressure chamber must maintain a high sealing state to closely adhere between the fixed scroll and the swing scroll to prevent inter-compression refrigerant leakage. However, if a gap is generated between the main frame, the fixed scroll, and the turning scroll forming the intermediate compression chamber, the pressure of the back pressure chamber is not kept constant, and refrigerant leakage occurs between the compression chambers. There was a problem.

In addition, the conventional back pressure type low pressure scroll compressor as described above forms an oil supply hole in the axial direction of the pivoting plate portion of the swing scroll to supply oil that is sucked between the fixed scroll and the swing scroll. In this case, the centrifugal force is reduced so that the oil sucked from the casing may not pass smoothly through the narrow frame side bearing surface, thereby increasing the friction loss of the compressor without supplying sufficient oil to the bearing surface between both scrolls. There was also a problem that the compressor performance is lowered.

In the conventional back pressure type low pressure scroll compressor, the swing scroll is supported by the back side pressure toward the fixed scroll, but in this case, if the back pressure supporting the swing scroll is excessively increased, the swing scroll There was also a problem in that the friction loss between the swing scroll and the fixed scroll increases because it is too close toward the fixed scroll.

It is an object of the present invention to provide a scroll compressor and a refrigerating apparatus employing the same so that the back pressure chamber can maintain a high sealing state, thereby improving compressor efficiency.

Another object of the present invention is to provide a scroll compressor and a refrigerating apparatus using the same, which allow oil to be smoothly supplied between both scrolls even when the compressor operates at a low speed.

Another object of the present invention is to properly support the upper and lower sides of the swing scroll to prevent the swing scroll is in close contact with the main frame or fixed scroll, thereby reducing the friction loss between the two scrolls through the performance of the compressor It is to provide a scroll compressor that can increase the and a refrigeration apparatus using the same.

In order to solve the object of the present invention, the frame is installed in the inner space of the casing; A fixed scroll installed on the frame; And a pivoting scroll installed between the frame and the fixed stroke to form a compression chamber while pivoting in engagement with the fixed scroll, and having a boss portion formed at one side thereof to be coupled to the crankshaft. The oil passage penetrating from one side of the turning scroll to the other side inside the boss portion is formed to penetrate through the bearing surface between the fixed scroll and the turning scroll, and the fixed scroll or the turning scroll communicates with the outlet of the oil passage. And a groove is formed in which a groove is formed which is not smaller than the cross section of the oil passage.

In addition, to solve the object of the present invention, the frame is installed in the inner space of the casing; A fixed scroll installed on the frame; And a rotation scroll installed between the frame and the fixed stroke, the compression scroll being engaged with the fixed scroll to pivot, and a boss portion formed at one side thereof to be coupled to the crankshaft. An oil passage penetrating from one side of the turning scroll belonging to the boss portion to the other side is provided, and the oil passage is provided with a scroll compressor penetrating before the compression start time of the compression chamber.

In addition, to solve the object of the present invention, the frame is installed in the inner space of the casing; A fixed scroll installed on the frame; And a pivoting scroll installed between the frame and the fixed stroke to form a compression chamber while pivoting in engagement with the fixed scroll, and having a boss portion formed at one side thereof to be coupled to the crankshaft. The first oil passage which penetrates from one side of the turning scroll belonging to the boss portion to the other side passes through the bearing surface between the fixed scroll and the turning scroll, and the turning scroll belongs to the inside of the boss portion of the turning scroll. There is provided a scroll compressor which is formed so that the second oil passage penetrating from one side of the other side to the other side of the compression chamber before the compression start time of the compression chamber.

In addition, to achieve the object of the present invention, a compressor; A condenser connected to the discharge side of the compressor; An expander coupled to the condenser; And an evaporator connected to the inflator and connected to the suction side of the compressor, wherein the compressor includes a back pressure flow path that guides the fluid in the discharge space to the bearing surface between the frame and the turning scroll and the bearing surface between both scrolls. A refrigeration machine is provided in which an oil passage for guiding oil and a second oil passage for guiding oil before the start angle of the compression chamber are provided.

The scroll compressor according to the present invention and the refrigerating apparatus employing the same support the turning scroll stably by guiding the oil in the discharge space to the back pressure chamber between the main frame and the turning scroll to support the turning scroll at the pressure of the back pressure chamber. In addition, as the oil is filled in the back pressure chamber, the sealing force of the back pressure chamber is increased, so that the swing scroll can be more stably supported, thereby increasing the efficiency of the compressor, and thereby the energy efficiency of the refrigeration apparatus to which the compressor is applied. Can improve.

And as the oil sucked through the oil passage of the crankshaft is supplied to the thrust bearing surface with the fixed scroll through the oil passage provided in the turning scroll, the lubrication performance of the bearing surface can be improved, and the turning scroll is fixed with the fixed scroll It is possible to prevent excessive contact and increase the friction loss. In addition, as some of the oil is supplied to the compression chamber through the oil passage, the sealing effect of the compression chamber may be increased and lubrication performance may be improved.

Hereinafter, a scroll compressor according to the present invention and a refrigerating apparatus to which the same is applied will be described in detail with reference to an embodiment shown in the accompanying drawings.

1 is a longitudinal cross-sectional view showing a scroll compressor of the present invention, Figure 2 is a perspective view showing the compression unit in the scroll compressor according to Figure 1, Figure 3 is a longitudinal cross-sectional view of the compression unit in the scroll compressor according to Figure 1, 4 is an enlarged perspective view of the first oil passage and the second oil passage in the compression unit according to FIG. 3, and FIG. 5 is a perspective view illustrating the compression unit in the scroll compressor according to FIG. 1.

As shown in FIG. 1, the low-pressure scroll compressor according to the present invention includes a casing 10 having a closed inner space, a main frame 20 and a sub which are respectively fixed to upper and lower inner spaces of the casing 10. A drive motor 40 mounted between the frame 30, the main frame 20 and the subframe 30 to generate a rotational force, and a fixed scroll 50 fixed to the upper surface of the main frame 20. And a pivoting scroll 60 which is pivotably mounted on an upper surface of the main frame 20 to engage the fixed scroll 50 to form a compression chamber P, and the pivoting scroll 60 and the main frame 20. Oldham's ring 70 is provided between the swing to prevent the rotation of the swing scroll (60) while rotating.

The casing 10 is a sealed inner space is divided into the suction space (S1) and the discharge space (S2) by the main frame 20 and the fixed scroll (50) in the suction space (S1) gas suction pipe ( 11) is connected to the gas discharge pipe 12 is connected to the discharge space (S2). And the bottom surface of the suction space (S1) of the casing 10 is filled with oil.

The main frame 20 is formed through the bearing hole 21 in the center thereof, the oil storage groove 22 to collect the oil sucked through the crank shaft 43 to be described later in the upper end of the bearing hole 21 Is formed.

The drive motor 40 is fixed to the inside of the casing (10) and the power is applied from the outside and the stator 41 is disposed with a predetermined gap in the interior of the stator 41 and mutually The rotor 42 rotates while acting, and the crank shaft 43 is coupled to the rotor 42 in a shrink fit and transmits the rotational force of the drive motor 40 to the swing scroll 60. The crankshaft 43 has an oil passage 43a formed therethrough in the axial direction, and an oil pump 44 is installed at the lower end of the oil passage 43a.

The fixed scroll (50) is formed on the bottom surface of the hard plate portion 51, a fixed wrap 52 constituting a pair of two compression chambers (P) in a spiral form, the side of the hard plate portion 51, the casing ( The suction groove 53 is formed in communication with the suction space S1 of the 10, and the discharge port 54 for discharging the compressed refrigerant to the discharge space (S2) of the casing 10 in the center of the upper surface of the hard plate portion 51. ) Is formed. A check valve 55 is installed at the upper end of the discharge port 54 to prevent the refrigerant discharged into the discharge space S2 from flowing back into the compression chamber P.

The orbiting scroll (60) is formed on the upper surface of the hard plate portion 61 of the orbiting wrap (62) forming a pair of compression chamber (P) together with the fixed wrap (52) of the fixed scroll (50) in a spiral form The boss portion 63 is coupled to the crankshaft 43 at the center of the bottom surface of the hard plate portion 61 to receive power from the driving motor 40.

On the other hand, the fixed scroll (50) and the revolving scroll (60) may be formed in an asymmetrical length of about 180 ° longer than the wrap length of the revolving scroll (60), but in some cases The lap lengths of both scrolls 50 and 60 may be formed in the same symmetrical shape.

The scroll compressor of the present invention as described above operates as follows.

That is, when power is applied to the drive motor 40, the crankshaft 43 rotates together with the rotor 42 to transmit rotational force to the turning scroll 60, and the rotational force is transmitted. The scroll 60 is pivoted by the Oldham ring 70 by the eccentric distance from the upper surface of the main frame 20 while the fixed wrap 52 of the fixed scroll 50 and the pivoting wrap of the pivoting scroll 60. A pair of compression chambers P continuously moving between the 62 are formed. And this compression chamber (P) is to move to the center by the continuous swing motion of the swing scroll 60 to compress the refrigerant sucked in the volume decreases.

At the same time, the oil pump 44 installed at the lower end of the crankshaft 43 pumps the oil filled in the casing 10, and the oil passes through the oil flow path 43a of the crankshaft 43. The bearing between the main frame 20 and the turning scroll 60 is supplied to the bearing hole 21 of the main frame 20 or collected in the oil storage groove 22 of the main frame 20 while being sucked to the upper end. Lubricate the face.

On the other hand, the fixed scroll (50) and the revolving scroll (60) is the end surface of the fixed wrap (52) and the revolving wrap (62), respectively, in close contact with the hard plate portion 51, 61 of each scroll (50) 60 The leakage of the refrigerant between the compression chamber (P) must be prevented. To this end, in the related art, as described above, a back pressure chamber is formed between the main frame 20 and the turning scroll 60, and a portion of the refrigerant in the intermediate compression chamber P is formed by drilling a hole in the turning scroll 60. It is introduced into the back pressure chamber so that the turning scroll is supported by the medium pressure of the refrigerant. However, in this case, the sealing state of the back pressure chamber may be poor due to the characteristics of the scroll compressor whose behavior of the swing scroll 60 is not constant. As a result, the refrigerant in the back pressure chamber leaks into the suction space, thereby causing the turning scroll 60 to fail. ) May not be sufficiently supported. On the other hand, if the pressure in the back pressure chamber is excessively increased, the bearing surface between the turning scroll and the fixed scroll may be crimped, causing frictional losses.

In view of this, in the present invention, a portion of the refrigerant and oil discharged to the discharge space (S2) is introduced into the back pressure chamber to improve the sealing state of the back pressure chamber by the viscosity of the oil. For example, as shown in FIGS. 1 to 3, the main frame (51) of the fixed scroll (50), that is, the upper surface of the hard plate (51) of the edge portion where the fixing wrap (52) is not formed. The back pressure passage 110 penetrates the upper surface of the back surface 20, that is, the surface forming the pivoting scroll 60 and the bearing surface, and is formed at the outlet side of the back pressure passage 110, that is, the upper surface of the main frame 20. On both sides of the back pressure passage 110 with the back pressure passage 110 interposed therebetween, sealing members 120 to be described below are respectively installed to form the back pressure chamber 130.

The back pressure passage 110 communicates with the first discharge pressure hole 111 formed through the outer hard plate portion 51 of the fixed scroll 50 and the first discharge pressure hole 111 to communicate with the main frame. It may be made of a second discharge pressure hole 112 formed through the 20.

As shown in the drawing, the first discharge pressure hole 111 may be formed in the fixed scroll 50 in the axial direction, and in some cases, may be inclined in the fixed scroll 50. And, as shown in Figure 2, the inlet end of the first discharge pressure hole 111 is discharged into the discharge space (S2) and the oil flowing down the upper surface of the hard plate portion 51 of the fixed scroll 50 can be gathered together. A guide groove 113 wider than a cross section of the first discharge pressure hole 111 may be formed so as to be wide. The guide groove 113 is preferably formed in a funnel-shaped inverted trapezoid cross-sectional shape it may be preferable to smooth oil inflow. And the upper surface of the hard plate portion 51 of the fixed scroll 50 is so that the oil flowed down to the upper surface of the hard plate portion 51 of the fixed scroll 50 can be guided to the first discharge pressure hole 111 more smoothly. May be inclined toward the first discharge pressure hole 111.

The second discharge pressure hole 112 is formed in a 'U' shape in the turning scroll, the inlet end of the second discharge pressure hole 112 is in communication with the first discharge pressure hole 111 while the outlet end Is formed to communicate with the back pressure chamber 130, that is, the bearing surface between the main frame 20 and the swing scroll (60). The second discharge pressure hole 112 may be formed such that a single flow path, that is, an outlet, communicates with the back pressure chamber 130, but in some cases, a plurality of flow paths, that is, the middle of the second discharge pressure hole 112, may be formed. The exhaust hole (not shown) may be further formed toward the suction space S1 of the casing 10. When the exhaust hole is formed, when the refrigerant flows into the second discharge pressure hole 112, the refrigerant leaks into the suction space S1, so that pure oil is introduced into the back pressure chamber 130 as much as possible. do. In this case, the exhaust hole may have a smaller inner diameter than the inner diameter of the second discharge pressure hole 112, thereby reducing the pressure of the refrigerant leaking from the second discharge pressure hole 112 to the suction space S1. It may be desirable. Of course, the exhaust hole may be formed in the first discharge pressure hole.

In addition, a guide tube 114 may be inserted between the first discharge pressure hole 111 and the second discharge pressure hole 112 so that both holes 111 and 112 may communicate without being distorted. To this end, the first discharge pressure hole 111 is wider than the second discharge pressure hole 112, and the guide tube 114 is extended to the insertion end of the second discharge pressure hole 112. And a guide tube 114 inserted into the second discharge pressure hole 112 is inserted into the first discharge pressure hole 111 to form the first discharge pressure hole 111 and the second discharge pressure hole 112. It may be desirable to prevent the oil from leaking into the joint between them.

The sealing members 120 are inserted into and coupled to the sealing grooves 23 provided on the upper surface of the main frame 20, respectively. The sealing members 120 may be manufactured in any shape as long as the sealing member 120 can block leakage of the refrigerant and oil in the radial direction. In this embodiment, a sealing member which is a kind of face seal having elasticity therein may be applied to increase the sealing force. For example, the sealing member of the present embodiment is formed in the shape of a cross section (c) as shown in Figure 2, the one side is in close contact with the bottom surface of the turning scroll 60 and the sealing portion 121 The support part 122 is inserted into the inner space 121a of the support member and elastically supports the sealing part 121.

The sealing part 121 and the support part 122 are both formed in an annular shape when projecting, and the plurality of sealing grooves 23 into which the sealing members 120 are inserted are also formed in an annular shape when projecting.

Here, as shown in FIG. 2, the radial interval between the sealing members 120, that is, the cross section of the back pressure chamber 130 is at least greater than the cross section of the back pressure passage 110, that is, the second discharge pressure hole 112. It is preferable not to be small, but to be large, to widen the cross-sectional area of the intermediate pressure chamber and to stably support the turning scroll 60.

In addition, although the inside of the back pressure chamber 130 may be formed to be flat to form a bearing surface, the first back pressure groove 131 having a predetermined depth and width may be formed as shown in FIG. 2. In this case, the refrigerant and oil flowing into the back pressure chamber 130 through the back pressure passage 110, that is, the second discharge pressure hole 112, are quickly formed along the first back pressure groove 131. The total pressure of the back pressure chamber 130, that is, the intermediate pressure chamber can be quickly and uniformly moved to the whole, so that the turning scroll 60 can be more stably supported.

For example, the first back pressure groove 131 is formed in an annular shape along the circumferential direction, and the outlet of the back pressure passage 110, that is, the second discharge pressure hole 112, is formed in the first back pressure groove 131. Preferably, the outlet is formed to communicate. The cross section of the first back pressure groove 131 may be smaller than the cross section of the back pressure chamber 130. In addition, the first back pressure groove 131 may be formed in a rectangular cross-sectional shape, but may be advantageously formed in a semi-circular cross section or a trapezoidal cross-sectional shape in order to move the refrigerant and oil quickly.

On the other hand, although not shown in the drawings, the sealing grooves may be formed on the bottom surface of the turning scroll. Even in this case, the sealing members may be formed in the same manner. The first back pressure groove may be formed on a bottom surface of the swing scroll. Even in this case, the shape of the first back pressure groove may be formed in the same manner as in the above-described embodiment.

Effects of the scroll compressor according to the present invention as described above are as follows.

That is, when the turning scroll 60 is pivoting, the refrigerant and oil sucked into the suction space S1 of the casing 10 are compressed through the suction groove 53 of the fixed scroll 50. The refrigerant and oil are sucked into P) and gradually move toward the center along the movement trajectory of the compression chamber P, and then discharged to the discharge space S2 of the casing 10 through the discharge port 54.

While the refrigerant and oil discharged into the discharge space S2 collide with the inner wall surface of the casing 10 constituting the discharge space S2, the refrigerant moves to the refrigeration cycle apparatus through the gas discharge pipe 12. Most of the oil flows down the upper surface of the fixed scroll 50 along the inner wall surface of the casing 10. The oil flowing down the upper surface of the fixed scroll 50 is collected around the first discharge pressure hole 111 constituting the back pressure flow path 110. In this case, when the guide groove 113 is formed on the upper surface of the fixed scroll 50, the oil may be collected into the first discharge pressure hole 111 more quickly.

The oil gathered into the first discharge pressure hole 111 flows into the first discharge pressure hole 111 by the weight of the oil and the pressure of the discharge space S2, and the oil is again returned to the main frame 20. It flows into the back pressure chamber 130 between the main frame 20 and the turning scroll 60 through the second discharge pressure hole (112). Then, the oil flowing into the back pressure chamber 130 increases the pressure of the back pressure chamber 130 to pressurize the back surface of the swing scroll 60 so that the swing scroll 60 is pushed up to closely contact the fixed scroll 50. Done. As a result, the compression chamber P between the fixed scroll 50 and the turning scroll 60 is tightly sealed to prevent refrigerant leakage from the compression chamber P, thereby improving the efficiency of the compressor.

Here, as described above, the refrigerant and oil discharged into the discharge space S2 flow into the back pressure chamber 130, so that a relatively large amount of refrigerant and oil flows into the intermediate pressure chamber, that is, the back pressure chamber 130. Can be supplied. That is, as the inlet end of the back pressure passage 110 forms the discharge pressure, the oil is pressurized by the pressure difference, and thus the oil in the discharge space S2 can be smoothly supplied to the back pressure chamber 130. will be.

As such, when a relatively large amount of oil is supplied to the back pressure chamber 130, the oil filled in the back pressure chamber 130 is filled with a sealing member (although a slight unstable behavior occurs due to the movement characteristics of the scroll compressor. It is possible to prevent the pressure in the back pressure chamber 130 from lowering by intercepting between the 120 and the turning scroll 60, thereby stably supporting the turning scroll 60. At this time, when an exhaust hole (not shown) is formed in the middle of the second discharge pressure hole 112, a small amount of refrigerant flowing into the back pressure passage 110 leaks into the suction space S1 through the exhaust hole. Thus, the back pressure chamber 130 may be filled with only oil as much as possible.

On the other hand, if excessive refrigerant and oil are introduced into the back pressure chamber through the back pressure passage, the pressure in the back pressure chamber is excessively high and the turning scroll is excessively in close contact with the fixed scroll, thereby increasing the friction loss between both scrolls. Can be. Therefore, in order to reduce the friction loss between both scrolls and increase the performance, a refrigerant or oil with a constant pressure is supplied to the upper thrust bearing surface of the swing scroll, that is, the surface forming the thrust bearing surface together with the bottom surface of the fixed scroll. It may be desirable to lubricate.

To this end, in the present invention, as shown in FIGS. 2 to 5, a portion of the oil sucked up through the crankshaft 23 to the hard plate portion 61 of the swinging scroll 60 is fixed scroll 50 and the swinging scroll. A first oil passage 150 for guiding to the thrust bearing surface between the 60 may be formed in the radial direction.

The first oil passage 150 is a first connection hole 151 communicated in a radial direction in the oil groove 65 formed in the center of the bottom surface of the turning scroll 60 to a predetermined depth, and the first The first outlet passage 152 is formed to a predetermined depth in the axial direction so as to communicate with the thrust bearing surface opposite to the thrust bearing surface of the fixed scroll 50 near the outer end of the connection hole 151.

The first connection hole 151 is formed radially out of the range of the suction groove 53 provided in the fixed scroll 50, the outer end of the first connection hole 151 is a separate small, such as a bolt To prevent the oil from leaking.

The first outlet passage 152 may have a cross section the same as a cross section of the second discharge pressure hole 112 of the back pressure passage 110, but the pivot scroll 60 may be fixed to the fixed scroll 50. In order to seal stably, it may be preferable to be smaller than a cross section of the second discharge pressure hole 112. In addition, since the pressure supplied through the back pressure passage 110 is a discharge pressure and the pressure supplied through the first oil passage 150 is an intermediate pressure lower than the discharge pressure, for example, an outlet of the back pressure passage 110 is provided. Even if the cross section and the outlet cross section of the first oil passage 150 are the same, the turning scroll 60 may float due to the pressure difference. However, when the compressor is started, that is, when the discharge pressure does not sufficiently increase, the intermediate pressure may be higher, so that the pressure of the first oil passage 150 may be higher than or equal to the pressure of the back pressure passage 110. . Therefore, in consideration of such a case, the second discharge pressure hole 112 of the back pressure passage 110 should be formed to be somewhat wider than the first outlet passage 152 of the first oil passage 150 than the back pressure passage 110. A large amount of refrigerant and oil is supplied to allow the swing scroll 60 to float.

In addition, at the end of the first oil passage 150, that is, at the end of the first oil passage 150, oil supplied through the first oil passage 150 is quickly replaced with a bearing surface of the fixed scroll 50. A second back pressure groove (not shown) may be formed so as to be diffused therein.

The second back pressure groove (not shown) may be formed in an arc shape extending in the circumferential direction, such as the first back pressure groove 131 described above, the cross section of the second back pressure groove (not shown) is at least a first It may be preferable not to be formed smaller than the cross section of the outlet passage (152).

The scroll compressor as described above has the following effects.

As shown in FIG. 6, a portion of oil drawn through the crankshaft 23 flows into the upper thrust bearing surface between the fixed scroll 50 and the turning scroll 60 through the first oil passage 150. do. Then, the oil flowing into the first outlet passage 152 flows into the first back pressure groove 131 provided in the fixed scroll 50 or is provided at the end of the first outlet passage 152. It is introduced into the back pressure groove 153 and spread widely on the upper thrust bearing surface. Then, the medium pressure between the fixed scroll 50 and the turning scroll 60 by the oil flowing into the upper thrust bearing surface is lower than the intermediate pressure between the main frame 20 and the turning scroll 60. Pressure is formed to prevent the swing scroll 60 from rising above the proper amount, thereby preventing the swing scroll 60 from being excessively in close contact with the fixed scroll 50 to increase the friction loss, thereby improving the performance of the compressor. Can be.

Then, as a predetermined amount of oil is supplied to the upper thrust bearing surface of the turning scroll 60 through the first oil passage 150, the upper thrust bearing surface is lubricated by the oil, so that the turning scroll 60 is lubricated. It is possible to further improve the performance of the compressor by reducing the friction loss between both scrolls during the pivoting motion.

Meanwhile, in the present invention, a portion of the oil sucked through the oil passage of the crankshaft is guided to the inlet of the compression chamber, that is, before the compression start time, so that the oil sucked directly enters the compression chamber, thereby increasing the sealing force of the compression chamber. At the same time, friction loss in the compression chamber can be reduced.

3 to 5, the second oil passage 160 belongs to the suction groove 53 in a radial direction in the oil groove 65, that is, does not coincide with the first connection hole 151. The second connecting hole 161 communicates radially in the range and the second connecting hole 161 penetrates in the axial direction so as to communicate with the suction groove 53 near the outer end of the second connecting hole 161. It consists of an outlet passage 162.

The second connection hole 161 is formed through the outer circumferential surface in the center direction, like the first connection hole 151, the outer end may be sealed by a small bolt.

The second outlet passage 162 is preferably formed through the upper end so that the end thereof is located in the suction groove 53 range of the fixed scroll (50). Of course, the second outlet passage 162 may be formed at an end thereof, that is, the outlet end of the intermediate compression chamber outside the suction groove 53, but in this case, refrigerant leakage may occur, which is not preferable.

Even when the oil drawn up through the crankshaft to the compression chamber as described above the effect is as follows.

That is, as shown in FIG. 6, a part of the oil sucked through the crankshaft 23 flows into the inlet side of the compression chamber P through the second oil passage 160. Then, the oil flowing into the second outlet passage 162 is quickly introduced into the compression chamber P together with the refrigerant sucked from the end of the second outlet passage 162 and along the track of the compression chamber together with the refrigerant. Will move. Then, the fixed scroll 50 and the rotating scroll 60 which form the compression chamber are tightly sealed by the oil flowing in the compression chamber P, and the fixed scroll 50 and the rotating scroll 60 are also sealed. By preventing friction loss between the compressor performance can be further improved.

When the scroll compressor according to the present invention is applied to a refrigerator, the efficiency of the refrigerator can be improved.

For example, in the refrigerator 700 having a refrigerant compression type refrigeration cycle including a compressor, a condenser, an expander and an evaporator as shown in FIG. 7, the main board 710 controls the overall operation of the refrigerator in the refrigerator 700. The scroll compressor (C) is connected to the back wheel, and the back pressure chamber between the main frame 20 and the swing scroll (60) installed inside the scroll compressor (C) communicates with the discharge space (S2). By stably supporting the scroll 60, the lubrication between the swing scroll 60 and the fixed scroll 50 can be effectively lubricated, thereby improving the performance of the scroll compressor and improving the energy efficiency of the refrigeration machine to which the compressor is applied. In addition, by supplying oil drawn up through the crankshaft 23 to the bearing surface between the two scrolls 50 and 60 and the compression chamber, the turning scroll 60 is prevented from being excessively floated and the both scrolls 50 Performance of the scroll compressor by reducing the friction loss between the (60) and at the same time, increasing the sealing force of the compression chamber (P) and reducing the friction loss between both scrolls (50) and (60) forming the compression chamber (P). In this case, the energy efficiency of the refrigerating apparatus to which the compressor is applied may be improved.

The scroll compressor according to the present invention can be widely used in refrigeration machines such as air conditioners.

1 is a longitudinal sectional view showing a scroll compressor of the present invention;

2 is an exploded perspective view of the compression unit in the scroll compressor according to FIG. 1;

3 is a longitudinal cross-sectional view showing the assembly of the compression unit in the scroll compressor according to FIG.

4 is an enlarged perspective view of the first oil passage and the second oil passage in the compression unit according to FIG. 3;

5 is an exploded perspective view of the compression unit in the scroll compressor according to FIG. 1;

6 is a schematic view showing a state in which the oil is guided to the bearing surface and the compression chamber in the scroll compressor according to FIG.

7 is a schematic view showing a refrigerating machine equipped with a scroll compressor according to FIG. 1.

** Description of symbols for the main parts of the drawing **

10: casing 20: mainframe

50: fixed scroll 60: turning scroll

110: back pressure flow passage 111: first discharge pressure hole

112: second discharge pressure hole 120: sealing member

121: sealing part 122: support part

130: back pressure chamber 131: first back pressure groove

150: first oil passage 160: second oil passage

Claims (10)

A frame installed in the inner space of the casing; A fixed scroll installed on the frame; And It is installed between the frame and the fixed stroke, engaging the fixed scroll to form a compression chamber while the pivoting movement, one side includes a rotating scroll is formed boss portion to be coupled to the crank shaft, An oil passage penetrating from one side of the turning scroll to the other side inside the boss portion of the turning scroll passes through the bearing surface between the fixed scroll and the turning scroll. The fixed scroll or the rotating scroll is a scroll compressor that is formed in communication with the outlet of the oil passage and not smaller than the cross section of the oil passage. A frame installed in the inner space of the casing; A fixed scroll installed on the frame; And It is installed between the frame and the fixed stroke, engaging the fixed scroll to form a compression chamber while the pivoting movement, one side includes a rotating scroll is formed boss portion to be coupled to the crank shaft, An oil passage penetrating from one side of the turning scroll to the other side inside the boss portion of the turning scroll is formed. And the oil passage penetrates before the compression start time of the compression chamber. A frame installed in the inner space of the casing; A fixed scroll installed on the frame; And It is installed between the frame and the fixed stroke, and forms a compression chamber while pivoting in engagement with the fixed scroll, one side includes a rotating scroll is formed boss portion to be coupled to the crank shaft, The first oil passage penetrating from one side of the turning scroll to the other side inside the boss portion of the turning scroll is passed through the bearing surface between the fixed scroll and the turning scroll, And a second oil passage penetrating from one side of the turning scroll to the other side inside the boss portion of the turning scroll to pass before the compression start time of the compression chamber. The method of claim 3, wherein The fixed scroll or the rotating scroll is a scroll compressor that is formed in communication with the outlet of the oil passage and not smaller than the cross section of the oil passage. The method of claim 3, wherein And a cross section of the first oil passage no longer than a cross section of the second oil passage. The method according to any one of claims 1 to 3, The bearing surface between the frame and the rotating scroll scroll outlet is formed to communicate with the inner space of the casing is formed. The method of claim 6, And a sealing member is provided at both sides of the back pressure flow path at the outlet side of the back pressure flow path to form a back pressure chamber. The method of claim 7, wherein And a back pressure groove is formed along the circumferential direction at the outlet of the back pressure flow path, and the back pressure groove is formed between the plurality of sealing members. The method of claim 8, And a cross section of the back pressure groove is not smaller than a cross section of the outlet side of the back pressure flow path. compressor; A condenser connected to the discharge side of the compressor; An expander coupled to the condenser; And And an evaporator connected to the inflator and connected to the suction side of the compressor. The compressor comprises a compressor of any one of claims 1 to 9.

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