CN1963207A - Vortex type compressor - Google Patents

Abstract

The present invention relates to a scroll compressor, which comprises: a crankshaft (101) for rotationally driving the movable scroll (120); (180) A pressure separation mechanism that is separated into a central space (181) whose pressure is approximately equal to the discharge pressure and an outer peripheral space (182) whose pressure is lower than the central space (181); a sliding bearing (104) that supports the crankshaft (101) ); Hold the frame (160) of the sliding bearing (104); and the thrust bearing (204) supporting the crankshaft (101). The thrust bearing (204) is made of another part different from the sliding bearing (104) and the frame (160), and the opposite side of the bearing surface of the thrust bearing (204) is formed by the supporting surface ( 162) support, the inner diameter of the frame support surface (162) is made smaller than the outer diameter of the sliding bearing (104).

Description

scroll compressor

technical field

The present invention relates to a scroll compressor, which is especially suitable for using HFC refrigerant, air as natural refrigerant, carbon dioxide and other compressive gases. At the same time, it has the function of separating the space pressure on the back side of the movable scroll into a central space. A scroll compressor with a pressure separation mechanism for the outer peripheral space.

Background technique

Scroll compressors are widely used in various fields as compressors for refrigeration and air conditioners. Compared with other types of compressors, they are known as compressors with advantages such as high efficiency, high reliability, and quietness.

As a conventional scroll compressor, there is a compressor disclosed in Patent Document 1: Japanese Patent No. 3344843 . The scroll compressor of Patent Document 1 has a structure in which the movable scroll is supported by the pressure of the back pressure chamber, and is separated into a central space where the lubricating oil flows in at approximately the discharge pressure, and a space maintained at the intermediate pressure between the suction pressure and the discharge pressure. Outer peripheral space, in order to supply the necessary minimum lubricating oil to the outer peripheral space, so that most of the remaining lubricating oil in the central space does not mix with the compressed gas in the closed container as much as possible and return to the lubricating oil tank at the bottom. By making this structure, it is possible to obtain high reliability and prevent the reduction of efficiency caused by the mixing of lubricating oil into the compressed gas, and the amount of lubricating oil mixed into the discharge gas from the compressor (the amount of oil leakage) is small. Scroll compressor.

In addition, as another conventional scroll compressor, there is a compressor disclosed in Patent Document 2: Japanese Patent No. 3545826 . The scroll compressor of Patent Document 2 is equipped with an oil supply passage, which is configured to pass from the center space approximately configured to discharge pressure by a sealing member through the movable scroll end plate to the low-pressure part side, and pass through the movable scroll Rotation of the disk intermittently opens the opening end, and the sliding surface of the O-ring provided on the low-pressure portion side is lubricated by lubricating oil intermittently supplied through the oil supply passage. By making such a structure, it is possible to supply necessary and sufficient lubricating oil to each sliding part, and it is possible to prevent damage to the scroll compressor caused by excessive oil supply to the O-ring of the low-pressure part provided on the back of the movable scroll. Reduced performance.

Furthermore, Patent Document 1 and Patent Document 2 are configured by including the following members: a sliding bearing that rotatably engages and supports the movable scroll side portion of the crankshaft; A thrust bearing that supports the axial movement of the crankshaft.

In Patent Document 1 and Patent Document 2, the pressing force of the movable scroll to the fixed scroll is determined by the space formed on the back side of the movable scroll, that is, the high-pressure central space approximately at the discharge pressure and the pressure of the central space. It is determined by the balance between the upward thrust of the movable scroll generated in the low-pressure outer peripheral space and the downward thrust of the movable scroll generated in the compression chamber.

Here, the space size of the high-pressure central part, which is approximately the discharge pressure, has a minimum value limited by the size of the thrust bearing part. Therefore, in order to properly press the movable scroll to the fixed scroll, it is important to have a design margin that can constitute a high-pressure center space that is substantially equal to the discharge pressure as small as possible. If the space in the high-pressure central part, which is approximately the discharge pressure, is too large, the thrust force of the movable scroll becomes too high, and the mechanical sliding loss between the movable scroll and the fixed scroll increases, resulting in a problem that the energy conversion efficiency decreases.

However, in the scroll compressors of Patent Document 1 and Patent Document 2, if only the outer diameter of the thrust bearing is reduced to reduce the space in the central part, the support area of the frame supporting the thrust bearing decreases and the As a problem of loss of function of the thrust bearing. Therefore, it is considered to reduce the inner diameter of the thrust bearing to reduce the inner diameter of the support surface of the frame to ensure the support area of the frame, but in this case, the diameter of the thrust bearing and the crankshaft need to be reduced, and the function loss of the thrust bearing and the crankshaft will occur. question.

Furthermore, in Patent Document 1 and Patent Document 2, the lubricating oil supplied from the oil supply passage of the crankshaft through the sliding bearing flows to the oil discharge passage only through the bearing surface of the thrust bearing, so it is difficult to sufficiently supply oil to the sliding bearing.

Contents of the invention

A first object of the present invention is to provide a scroll compressor capable of reducing mechanical sliding loss between the movable scroll and the fixed scroll while ensuring an appropriate thrust force of the movable scroll and improving energy conversion efficiency.

A second object of the present invention is to provide a scroll compressor that sufficiently ensures oil supply to sliding bearings and is excellent in reliability.

A first aspect of the present invention for achieving the above-mentioned first object is a scroll compressor comprising: a fixed scroll having a spiral wrap vertically arranged on an end plate; The movement in the in-plane direction is restricted; the movable scroll, which has a spiral wrap plate installed upright on the end plate and meshes with the above-mentioned fixed scroll, does not rotate on its own axis in the plane perpendicular to the wrap plate, but makes a rotational movement and shrinks The volume of the compression chamber formed between the above-mentioned fixed scroll; the crankshaft, which cooperates with the shaft support part of the above-mentioned movable scroll and drives the movable scroll in rotation; the pressure separation mechanism, which is located at the shaft support part of the above-mentioned movable scroll The end surface of the movable scroll separates the space formed on the back side of the movable scroll into a central space with a pressure approximately equal to the discharge pressure and an outer peripheral space with a pressure lower than the central space; a sliding bearing rotatably fits and supports the above-mentioned The movable scroll side part of the crankshaft; the frame, which holds the above-mentioned sliding bearing on the inner peripheral surface; The support is characterized in that the above-mentioned thrust bearing is constituted by another part different from the above-mentioned sliding bearing and the above-mentioned frame, and the opposite side of the bearing surface of the above-mentioned thrust bearing is supported by the support surface formed by the above-mentioned frame, and the frame The inner diameter of the supporting surface of the frame is made smaller than the outer diameter of the above-mentioned sliding bearing.

A more preferred specific constitution example of the first scheme of the present invention is as follows:

(1) An enlarged portion opposite to the orbiting scroll is formed on the inner peripheral surface of the frame, and the outer peripheral portion of the sliding bearing is accommodated in the enlarged portion, and the sliding bearing is mounted on the frame.

(2) Form an oil supply passage for supplying lubricating oil through the crankshaft, and form a second oil discharge passage for the lubricating oil supplied from the oil supply passage of the crankshaft to flow to the oil discharge passage through the rotary bearing provided inside the shaft support portion of the movable scroll. An oil supply passage, an oil passage is provided between the above-mentioned sliding bearing and the above-mentioned oil discharge passage, forming a second supply passage for lubricating oil supplied from the oil supply passage of the above-mentioned crankshaft to flow from the above-mentioned sliding bearing to the above-mentioned oil discharge passage through the above-mentioned oil passage. oil channel.

(3) A space communicating with one side of the sliding bearing is formed on the inside of the thrust bearing along the entire circumference, and a space communicating with the oil discharge passage is formed on the outside of the thrust bearing along the entire circumference. On both sides or at least one side of the bearing surface of the bearing and the opposite surface of the bearing surface, a plurality of grooves connecting the inner space and the outer space of the thrust bearing are formed, and serve as oil passages for the second oil supply passage.

(4) A space constituting a part of the first oil supply passage is formed on the outside of the thrust bearing, and a linear through-hole communicating from the outer periphery of the frame to the outer space of the thrust bearing is formed to form the oil discharge passage. The through hole is continuous in its axial direction and forms grooves on the thrust bearing support surface and the thrust bearing pressure plate of the above-mentioned frame as the oil passage of the above-mentioned second oil supply passage.

(5) Grooves are formed on both sides of the bearing surface of the thrust bearing and the surface opposite to the bearing surface, and serve as oil passages for the second oil supply passage.

(6) A rotation stopper is provided on the thrust bearing, and the rotation stopper is incorporated into an oil passage formed in a part of the pressure plate part of the thrust bearing.

In addition, a second aspect of the present invention for achieving the above-mentioned first object is a scroll compressor including: a fixed scroll having a spiral wrap vertically provided on an end plate, The movement in the vertical in-plane direction is limited; the movable scroll, which has a spiral coil plate vertically arranged on the end plate and meshes with the above-mentioned fixed scroll, does not rotate but rotates in a plane perpendicular to the coil And reduce the volume of the compression chamber formed between the above-mentioned fixed scroll; the crankshaft, which cooperates with the shaft support protruding from the central part of the above-mentioned movable scroll to rotate and drive the movable scroll; the pressure separation mechanism, which is located at The end surface of the shaft support portion of the movable scroll is arranged to separate the space formed on the back side of the movable scroll into a central space with a pressure approximately equal to the discharge pressure and an outer peripheral space with a pressure lower than the central space; sliding a bearing that rotatably fits and supports the movable scroll side portion of the above-mentioned crankshaft; a frame that holds the above-mentioned slide bearing on the inner peripheral surface; and a thrust bearing that is located closer to the movable scroll side than the above-mentioned slide bearing position and support relative to the axial movement of the above-mentioned crankshaft, it is characterized in that the above-mentioned thrust bearing part is integrated with the above-mentioned machine frame by another member different from the above-mentioned sliding bearing, and the bearing surface of the above-mentioned thrust bearing part is The inner diameter is made smaller than the outer diameter of the above-mentioned sliding bearing.

The more preferred concrete constitution example of the second scheme of the present invention is as follows:

(1) On the inner peripheral surface of the above-mentioned frame, an enlarged portion on the opposite side of the orbiting scroll is formed, and the outer peripheral portion of the above-mentioned sliding bearing is accommodated in the enlarged portion, and the sliding bearing is mounted on the above-mentioned frame to form a The oil supply passage for supplying lubricating oil in the crankshaft forms a first oil supply passage for supplying lubricating oil supplied from the oil supply passage of the crankshaft to the oil discharge passage through the rotary bearing provided inside the shaft support portion of the movable scroll, In order to form a second oil supply passage for supplying lubricating oil supplied from the oil supply passage of the crankshaft to the oil discharge passage through the sliding bearing, the side of the bearing surface side and the opposite side of the bearing surface of the thrust bearing are bypassed. Oil channels on two sides or at least one side.

(2) A space constituting part of the first oil supply passage is formed on the outside of the thrust bearing, and a linear through-hole communicating from the outer periphery of the frame to the outer space of the thrust bearing is formed to form the oil discharge passage. The through hole is continuous toward its axial direction and forms a groove on the support surface of the above-mentioned frame as an oil passage of the above-mentioned second oil supply passage.

Furthermore, a third aspect of the present invention for achieving the above-mentioned second object is a scroll compressor comprising: a fixed scroll having a spiral wrap vertically arranged on an end plate, The movement of the plate in the direction perpendicular to the plane is limited; the movable scroll, which has a spiral coil plate arranged upright on the end plate and meshes with the above-mentioned fixed scroll, does not rotate but rotates in the plane perpendicular to the coil plate Move and reduce the volume of the compression chamber formed between the above-mentioned fixed scroll; the crankshaft, which cooperates with the shaft support part of the above-mentioned movable scroll and rotates to drive the movable scroll; the pressure separation mechanism, which is located on the above-mentioned movable scroll The end surface of the shaft support part divides the space formed on the back side of the movable scroll into a central space whose pressure is approximately equal to the discharge pressure and an outer peripheral space whose pressure is lower than the central space; the sliding bearing is rotatably fitted and supports the movable scroll side portion of the above-mentioned crankshaft; the frame, which holds the above-mentioned slide bearing on the inner peripheral surface; It is supported to move, and it is characterized in that an oil supply passage for supplying lubricating oil through the above-mentioned crankshaft is formed, and the lubricating oil supplied from the oil supply passage of the above-mentioned crankshaft is formed to pass through the inner side of the shaft support part of the above-mentioned movable scroll. The bearing then flows to the first oil supply passage of the oil discharge passage, and an oil passage is provided between the above-mentioned sliding bearing and the above-mentioned oil discharge passage, so that the lubricating oil supplied from the oil supply passage of the above-mentioned crankshaft flows from the above-mentioned sliding bearing through the above-mentioned oil passage to The second oil supply channel to the above oil discharge channel.

The more preferred concrete constitution example of the third scheme of the present invention is as follows:

(1) A space constituting a part of the first oil supply passage is formed outside the thrust bearing, and a linear through-hole communicating with the space outside the thrust bearing is formed from the outer periphery of the frame to form the oil discharge passage. The through hole is continuous toward its axial direction and forms a groove on the support surface of the above-mentioned frame as an oil passage of the above-mentioned second oil supply passage.

According to the first and second aspects of the present invention, it is possible to realize a scroll compressor capable of ensuring an appropriate thrust force of the movable scroll, reducing the mechanical sliding loss of the movable scroll and the fixed scroll, and improving energy conversion efficiency.

In addition, according to the third aspect of the present invention, it is possible to realize a scroll compressor that sufficiently ensures oil supply to the sliding bearings and is excellent in reliability.

Description of drawings

Fig. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention.

Fig. 2 is an enlarged view of part A of Fig. 1 .

Fig. 3 is a diagram of the frame of view 2 from above (line B-B of Fig. 2).

FIG. 4 is a plan view of the thrust bearing of FIG. 2 .

FIG. 5 is a side view of the thrust bearing of FIG. 2 .

Fig. 6 is a plan view of a thrust bearing of a scroll compressor according to a second embodiment of the present invention.

Fig. 7 is a plan view of a scroll compressor housing according to a third embodiment of the present invention viewed from above.

Fig. 8 is an enlarged view of the vicinity of the upper part of the scroll compressor crankshaft according to the fourth embodiment of the present invention.

Figure 9 is a view of the frame of view 8 from above.

Fig. 10 is an enlarged view of the vicinity of the upper part of the scroll compressor crankshaft according to the fifth embodiment of the present invention.

Detailed ways

Hereinafter, several embodiments of the present invention will be described using the drawings. The same symbols in the drawings of the respective embodiments represent the same members or equivalent members. In addition, the present invention includes a more efficient compressor by appropriately combining the various embodiments as necessary.

first embodiment

A scroll compressor according to a first embodiment of the present invention will be described using FIGS. 1 to 5 .

First, the overall structure of the scroll compressor according to the present embodiment will be described with reference to FIG. 1 . Fig. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention.

The scroll compressor 1 is configured by accommodating a compression unit 2 and a drive unit 3 in an airtight container 100 . Compression unit 2 is configured using fixed scroll 110 , movable scroll 120 , and frame 160 as basic components.

The fixed scroll 110 is composed of a spiral wrap 110a, an end plate 110b, and a discharge port 110e as basic components. The roll plate 110a is vertically erected on the end plate 110b. The fixed scroll 110 is installed so as to restrict movement in at least an in-plane direction perpendicular to the axial direction in which the coil 110a is erected, and is fixed to the frame 160 with bolts in this embodiment.

The movable scroll 120 is composed of a spiral wrap 120a, an end plate 120b, a shaft support portion 120e, and a shaft support portion end surface 120f as basic components. The roll plate 120a is vertically erected on the end plate 120b. The shaft support portion 120e is protrudingly formed on the side of the end plate 120b opposite to the coiled plate. The movable scroll 120 is set so that it does not rotate on its own axis but rotates in a plane perpendicular to the direction in which the coil 120a is erected, that is, the axial direction.

The fixed scroll 110 and the movable scroll 120 are engaged to form a compression chamber 130 between the two scrolls 110 , 120 . The compression operation for compressing the working fluid is performed by reducing the volume of the compression chamber 130 by rotating the movable scroll 120 . In this compression operation, the working fluid is sucked into the compression chamber 130 through the suction port 140 and the suction space 135 along with the rotary motion of the movable scroll 120 , and the sucked working fluid passes through the compression stroke from the discharge port 110 e of the fixed scroll 110 to the airtight container 100 . It is discharged from the discharge space 136 inside, and then discharged from the airtight container 100 through the discharge port 150 . Thus, the space in the airtight container 100 is maintained at the discharge pressure. In addition, as working fluids, HFC refrigerants, air as natural refrigerants, carbon dioxide, and other compressive gases are used.

In addition, in order to prevent overcompression during operation at a low pressure ratio lower than the design pressure ratio, an overcompression prevention device is provided. This overcompression preventing device is configured by including: a passage 138 communicating with the compression chamber 130 and the discharge space 136; and a valve 139 that opens the passage 138 during overcompression.

The frame 160 has its outer peripheral surface fixed to the airtight container 100 , a sliding bearing 104 is arranged on the inner peripheral surface, and a thrust bearing 204 is arranged above the portion supporting the sliding bearing 104 .

The drive unit 3 that drives the movable scroll 120 in rotation is composed of the stator 108 and the rotor 107; the crankshaft 101; the European ring 134 that is the main part of the rotation prevention mechanism of the movable scroll 120; the frame 160; the sliding bearings 104, 105; 204; and the rotary bearing 103 is constituted as a basic component.

Here, the stator 108 and the rotor 107 are components constituting the rotary drive device 4, and are components when the rotary drive device 4 is used as a motor. The outer periphery of the stator 108 is fixed to the airtight container 100 . In the rotor 107 , the crankshaft 101 is attached to the center and rotates inside the stator 108 .

The crankshaft 101 is configured integrally with a main shaft portion 101b and an eccentric pin portion 101a. The main shaft portion 101b is fixed to the rotor 107 . Inside the crankshaft 101, an oil supply passage 102 penetrating up and down and oil supply passages 102a, 102b branching from the oil supply passage 102 are provided. The supply line 102 communicates with an external oil supply pump 106 . The oil supply passage 102 a is provided for supplying lubricating oil to the sliding bearing 104 , and the oil supply passage 102 b is provided for supplying lubricating oil to the sliding bearing 105 .

The sliding bearings 104 and 105 constitute a main shaft support portion rotatably engaged with the main shaft portion 101b of the crankshaft 101 . The sliding bearings 104 and 105 are disposed on the side of the compression chamber and the side opposite to the compression chamber of the rotary drive device 4, respectively. In the present invention, it is necessary to use the sliding bearing 104 as the main shaft support portion on the side of the compression chamber. However, as the main shaft support portion on the opposite side of the compression chamber, in addition to the slide bearing 105 shown in the figure, a rolling bearing or other shaft support member that can be used according to the conditions of use may be used.

The thrust bearing 204 is located closer to the orbiting scroll side than the slide bearing 104 and is located on the space side of the central portion, and can be installed to support the axial movement of the crankshaft 101 .

The rotary bearing 103 is disposed inside the shaft support portion 120e of the movable scroll 120 so as to be movable in the direction of the rotary axis and rotatably engaged with the eccentric pin portion 101a of the crankshaft 101 .

The Oldham ring 134 is disposed in the space formed by the movable scroll 120 and the frame 160 , that is, the outer peripheral space 182 a. One of the two sets of orthogonal key portions formed on the Euro ring 134 slides in the key groove 141 as a receiving portion of the Euro ring 134 formed in the frame 160, and the remaining group slides on the key formed on the rotating coil 120a. slides in the keyway on the back side. As a result, the movable scroll 12 does not rotate on its own axis but rotates in a plane perpendicular to the direction of the upright winding, that is, the axial direction.

Next, the pressure separation mechanism for the pressure separation formed in the space on the back side of the movable scroll 120 will be described with reference to FIGS. 1 and 2 . FIG. 2 is an enlarged view of the vicinity of the upper part of the crankshaft 101 of the scroll compressor 1 of FIG. 1 (portion A in FIG. 1 ).

The space formed on the rear side of the movable scroll 120 is a space surrounded by the movable scroll 120 , the frame 160 , and the fixed scroll 110 (hereinafter referred to as a back pressure chamber). The pressure separation mechanism is composed of the following components: the end surface 120f of the rotating shaft support part; the end surface 164 of the frame 160 facing it; the annular groove 161 formed in the end surface 164; The sealing member 172 in.

Here, the rotating shaft supporting portion end surface 120f is an end surface formed on the side opposite to the compression chamber (rotating drive mechanism side) of the rotating shaft supporting portion 120e, and is formed in a plane perpendicular to the axial direction to constitute a sealing surface. The seal 172 pressure-isolates the back pressure chamber 180 into a central space 181 and an outer peripheral space 182 . The center space 181 includes: a space formed between the rotating shaft supporting portion 120e and the eccentric pin portion 101a, that is, a first central portion space 181a; space, that is, the second central portion space 181b.

The central part space 181 is directly connected to the oil supply passage 102 to the bearing or the sliding part, and serves as an approximate discharge pressure that receives the boosting action by the pumping action of the external oil supply pump 106 and the decompression action by passing the bearing part or the gap part. pressure space. In addition, the outer peripheral space 182 includes: the outer peripheral space 182a as a space constituted by the movable scroll 120 and the frame 160; , Outer peripheral space 182b. The outer peripheral space 182b communicating with the outer peripheral space 182a communicates intermittently or continuously with the compression chamber 130 during compression through the communication hole 137, and is in an intermediate pressure state between the suction pressure and the discharge pressure.

The discharge pressure in the central space 181 and the intermediate pressure in the outer peripheral space 182 function as follows: push the back of the movable scroll end plate 120b upward toward the fixed scroll 110, and keep the compression chamber 130 properly airtight. sex. In addition, depending on the specification of the compression part or the operating range of the scroll compressor 1, the required thrust force of the movable scroll is different, so it is also preferable to make the outer peripheral space 182 not an intermediate pressure between the suction pressure and the discharge pressure, but When configured as a suction pressure state. In this case, the outer peripheral space 182 is configured to communicate with the suction side.

The thrust cover 190, which receives the load when the crankshaft 101 moves upward, is constituted by a protrusion provided on the back side of the rotating coil 120a, and is provided in the center so as not to block the oil supply passage 102 when the crankshaft 101 contacts the thrust pad 190. recessed part. Furthermore, it is set in such a way that when the crankshaft 101 moves to the uppermost position, the shaft support portion end surface 120f of the movable scroll 120 does not come into contact with the annular portion upper surface 101c of the crankshaft 101, and the eccentric pin portion 101a is received by the thrust pad 190. to form an axial gap constituting the central space 181a and an axial gap constituting the central space 181b.

Oil supply to the rotary bearing 103 and the sliding bearings 104 , 105 is performed by the oil supply passages 102 , 102 a , 102 b provided in the crankshaft 101 and an external oil supply pump 106 . That is, the lubricating oil 131 accumulated in the lower space of the airtight container 100 is sucked by the external oil supply pump 106 and supplied to each part through the oil supply passages 102, 102a, and 102b.

The lubricating oil 131 supplied from the oil supply passage 102 reaches the center space 181a above the eccentric pin portion 101a, lubricates the rotary bearing 103, and flows out into the center space 181b. The lubricating oil flowing out into the central space 181b supplies a small amount of lubricating oil 131 to the outer peripheral space 182 through the sealing portion provided on the end surface 120f of the rotating shaft support portion, but most of the lubricating oil 131 passes through the annular portion formed on the crankshaft 101. The oil supply channel 183 between the outer peripheral portion of 101d and the opposite surface 166 of the frame, the oil discharge channel 184 provided on the frame 160 , the oil discharge pump 185 , and the return oil tank 131 . In addition, the oil supply passage 183 is formed on the outer side of the thrust bearing 204 along the entire circumference, and constitutes a part of the central part space 181b.

The lubricating oil 131 supplied from the oil supply passage 102 a branched from the oil supply passage 102 lubricates the slide bearing 104 and flows out to an oil supply passage 186 formed between a part 163 of the frame 160 and the main shaft portion 101 b of the crankshaft 101 . The oil supply passage 186 is formed inside the thrust bearing 204 along the entire circumference. The lubricating oil 131 flowing out to the oil supply passage 186 passes through the oil passage 204b formed on the bearing surface of the thrust bearing 204 and the oil passage 204d formed on the opposite side of the bearing surface of the thrust bearing 204 from the inner peripheral surface of the thrust bearing 204 to reach The oil supply passage 183 merges with the lubricating oil lubricating the rotating bearing 103 and then flows into the oil discharge passage 184 provided on the frame 160 . Also, the lubricating oil 131 flowing out to the oil supply passage 186 merges with the oil discharge passage 184 through the oil passage 184 a provided in the frame 160 . The lubricating oil 131 flowing into the oil discharge passage 184 is returned to the oil sump 131 by the oil discharge pump 185 . Thereby, the lubricating oil 131 lubricating the shaft support portion 103 of the movable scroll and the shaft support portion 104 of the crankshaft 101 can be prevented from directly mixing with the working fluid passing through the suction port 140 . In addition, as the oil supply pump, it is also possible to use a centrifugal pump function configured on the crankshaft 101 by an eccentric rotation operation.

In order to lubricate the sliding parts such as the Oval ring 134 disposed in the outer peripheral space 182a with lubricating oil supplied to the central part space 181b, the central part space 181b and the outer peripheral part space 182a are provided on the end surface 120f of the rotating shaft supporting part. Small holes 170, 171 that communicate intermittently or continuously. In addition, depending on the operating conditions of the scroll compressor 1 , when the required amount of oil can be ensured only by supplying oil through the seal 172 , the small holes 170 and 171 are unnecessary. The small holes 170 and 171 may be any number as long as the necessary amount of oil can be ensured. In addition, when frequent oil supply is required, by making the size of the small holes 170 and 171 larger than the sheet width of the seal member 172, constant oil supply can be achieved.

Next, the thrust bearing 204 that receives the load when the crankshaft 101 moves downward will be described with reference to FIGS. 2 to 5 . FIG. 3 is a view of the frame of top view 2 from above (line B-B of FIG. 2 ), FIG. 4 is a top view of the thrust bearing 204 of FIG. 2 , and FIG. 5 is a side view of the thrust bearing 204 of FIG. 2 . In addition, in FIG. 3 , the crankshaft 101 and the thrust bearing 204 are omitted and shown.

Thrust bearing 204 is disposed on a thrust bearing support portion composed of thrust bearing support surface 162 provided on frame 160 and thrust bearing platen portion 165 that restricts radial movement of thrust bearing 204 . A part 163 of the frame 160 formed between the thrust bearing support surface 162 and the upper end surface of the sliding bearing 104 bears the end surface of the compression chamber side of the sliding bearing 104 on the one hand (in the lower part) and constitutes a thrust force (in the upper part) on the other hand. Bearing support surface 162 . One feature of the present invention is a structure in which a part 163 of the frame 160 is disposed between the sliding bearing 104 and the thrust bearing support portion 162 .

In the present embodiment, an enlarged portion 160a with an open side opposite to the movable scroll is formed on the inner peripheral surface of the frame 160, and the outer peripheral portion of the sliding bearing 104 is accommodated in the enlarged portion 160a. Mounted on the frame 160. According to such a structure, the slide bearing 104 can be easily attached to a predetermined position.

In order not to hinder the flow of the lubricating oil 131 supplied by the oil supply passage 102, a part of the thrust bearing support surface 162 and the thrust bearing pressure plate part 165 of the frame 160 is formed to communicate with the oil supply passage 102a and be located on the frame 160. The oil passage 184 a of the oil discharge passage 184 .

In this embodiment, an oil discharge passage 184 is formed by forming a linear through hole communicating from the outer periphery of the frame 160 to the oil supply passage 183 serving as the outer space of the thrust bearing 204, and the oil discharge passage 184 is formed continuously in the axial direction from the through hole. Grooves are formed on the supporting surface of the frame 160 to serve as oil passages 184 . According to this structure, the oil passage 184 can be easily provided, and the lubricating oil 131 can flow more smoothly from the oil supply passage 183 through the oil passage 184 .

In addition, in order not to hinder the flow of lubricating oil 131 supplied from the oil supply passage 102a, an oil passage 204d is formed on the side 204c opposite to the bearing surface of the thrust bearing 204 as shown in FIG. In order to prevent the thermal sticking of the thrust bearing 204, as shown in FIG.

In this embodiment, a plurality of grooves 204b and 204d connecting the inner space 186 and the outer space 183 of the thrust bearing 204 are formed on both sides of the bearing surface 204a of the sliding bearing 204 and the opposite surface 204c of the bearing surface 204c, serving as a flow path from the sliding bearing 104 to the row. The oil passage of the oil passage 184 can further increase the amount of lubricating oil 131 that lubricates the sliding bearing 104 .

In the above structure, the pressing force to the movable scroll 120 of the fixed scroll 110 is the central part space 181 of the space 180 constituted on the back side of the movable scroll 120 at approximately the discharge pressure and the pressure at approximately the discharge pressure and approximately It is determined by the balance between the upward thrust of the movable scroll generated in the outer peripheral space 182 which is a pressure between the suction pressure and the suction pressure, and the downward thrust of the movable scroll generated in the compression chamber 130 . Here, the minimum value of the size of the central space 181 acting as substantially the discharge pressure is limited by the size of the diameter of the ring portion 101d of the crankshaft 101 (in other words, the size of the thrust bearing 204). Therefore, in order to properly press the movable scroll 120 against the fixed scroll 110 over a wide operating range, it is important to have a design margin for the central space 181 that can constitute a small high pressure.

According to the structure of this embodiment, the diameter of the frame facing surface 166 constituting the outer peripheral portion of the annular portion 101d of the crankshaft 101 can be minimized, and the orientation of the movable scroll 120 to the fixed scroll can be appropriately set within a wide operating range. 110 pushing force. Furthermore, in order to prevent thermal sticking, an oil passage is formed on the thrust bearing sliding contact surface 204a, and an oil passage 204c on the thrust bearing 204 is formed for not obstructing the flow of lubricating oil supplied by the oil supply passage 102a, or an oil passage 204c is formed on the thrust bearing. The support surface 162 and a part of the thrust bearing platen portion 165 form the oil discharge passage 184, so that the oil supply to the sliding bearing 104 and the thrust bearing 204 can be accurately performed.

Through the above, it is possible to realize a scroll compressor that accurately and appropriately adjusts the mechanical sliding loss of the movable scroll 120 and the fixed scroll 110 to ensure high energy conversion efficiency, and can suppress the movable scroll 120 and the fixed scroll. The excess pressing of the mechanical sliding part of 110 is also suitable for ensuring high reliability by accurately supplying oil to the sliding bearing 104 and the thrust bearing 204 .

second embodiment

Next, a second embodiment of the present invention will be described using FIG. 6 . Fig. 6 is a plan view of a thrust bearing 212 used in a scroll compressor according to a second embodiment of the present invention. This second embodiment differs from the first embodiment in the points described below, and is basically the same as the first embodiment in other points, so repeated descriptions are omitted.

In the second embodiment, the thrust bearing 212 is provided with a detent 212 e, and this detent 212 e is incorporated into the oil passage 184 formed in a part of the thrust bearing platen portion 165 . According to such a structure, thrust bearing 212 can be prevented from being rotated by the rotation of crankshaft 101, and abnormal wear of thrust bearing 212 can be prevented.

In addition, the sliding contact surface 212a and the oil passage 212b of the annular lower surface portion 101e of the crankshaft 101 have the same functions as those of the first embodiment.

third embodiment

Next, a third embodiment of the present invention will be described using FIG. 7 . FIG. 7 is a top view of a frame 160 of a scroll compressor according to a third embodiment of the present invention, and corresponds to FIG. 3 . This third embodiment differs from the first embodiment in the points described below, and is basically the same as the first embodiment in other points, so repeated description is omitted.

This third embodiment is characterized by an oil passage 240 provided on the thrust bearing support surface 162 . The oil passage 240 is characterized in that it is processed in line with the axial direction of the oil discharge passage 184 when the oil discharge passage 184 is processed, and is formed in a part of the thrust bearing support surface 162 and the thrust bearing pressure plate portion 165 . By processing the oil passage 240 in this way, the processing becomes easy, and the oil passage can be formed on the thrust bearing support surface 162 at low cost. In order not to interfere with the flow of lubricating oil supplied from the oil supply passage 102a, the oil passage 241 may be provided as necessary.

Fourth Embodiment

Next, a fourth embodiment of the present invention will be described using FIGS. 8 and 9 . FIG. 8 is an enlarged view of the vicinity of the upper part of the crankshaft 101 of a scroll compressor according to a fourth embodiment of the present invention, corresponding to FIG. 2 . FIG. 9 is a plan view of the rack 160 of View 8 from above, and is a view corresponding to FIG. 3 .

This fourth embodiment differs from the first embodiment in the points described below, and is basically the same as the first embodiment in other points, so repeated descriptions are omitted. In other words, in addition to the thrust bearing support surfaces 362, 388, a part 363 of the frame 160 formed between the thrust bearing support surfaces 362, 388 and the sliding bearing 104, the oil discharge channel 384 formed on the frame 160, and the oil discharge channel Except for the structure of the oil passages 387 and 389 where 384 joins and the oil supply passage 386, it is the same as the first embodiment, so only the different parts will be described.

This fourth embodiment is characterized in that an oil passage 387 is formed in a part 363 of the frame 160 while the thrust bearing support surface 388 remains. The lubricating oil 131 supplied from the oil supply passage 102a lubricates the sliding bearing 104, then flows into the oil supply passage 386 formed between the main shaft portion 101b of the crankshaft 101 and a part 363 of the frame 160, and passes through the oil passage 387 to the oil supply passage 387 provided on the machine. The oil discharge channels 384 on the frame 160 converge, and return to the oil tank 131 through the oil discharge pump 185. A part 363 of the frame 160 is formed between the thrust bearing support surfaces 362, 388 and the sliding bearing 104.

On the other hand, most of the lubricating oil supplied from the oil supply passage 102 passes through the oil supply passage 183 formed between the outer peripheral portion of the ring portion 101d of the crankshaft 101 and the frame facing surface 166 thereof after lubricating the rotary bearing 103 . Then it passes through the oil passage 389 arranged on the frame 160 and merges with the oil discharge passage 384 .

In order not to hinder the flow of lubricating oil supplied from the oil supply passage 102a, it is preferable to provide an oil passage 341 on the thrust bearing support surfaces 362, 388.

According to this fourth embodiment, the lubricating oil 131 supplied from the oil supply passage 102a can be more properly distributed to the thrust bearing 204 and the sliding contact surface 101c above the annular portion of the crankshaft 101; and the thrust bearing 204 and the underside of the annular portion of the crankshaft 101 The ground contact surface 101 e can prevent the sliding contact surface of the thrust bearing 204 from sticking, and can sufficiently supply the lubricating oil 131 to the sliding bearing 104 . Furthermore, since the thrust bearing support surfaces 362, 388 do not form a notch shape, the thrust load can be supported more accurately.

Fifth Embodiment

Next, a fifth embodiment of the present invention will be described using FIG. 10 . Fig. 10 is an enlarged view of the vicinity of the upper part of the crankshaft 101 of a scroll compressor according to a fifth embodiment of the present invention, corresponding to Fig. 2 . This fifth embodiment differs from the first embodiment in the points described below, and is basically the same as the first embodiment in other points, so repeated descriptions are omitted.

This fifth embodiment is characterized in that the thrust bearing portion is integrally formed with the frame 160 . Unlike the first embodiment, there is no thrust bearing support surface, and instead, the thrust bearing surfaces 462 , 488 are formed integrally with the frame 160 . As the material of the frame 160, a material having self-lubricating properties such as casting is used.

According to the fifth embodiment, a simple and low-cost configuration can be achieved in a scroll compressor having a small thrust load.

Claims (12)

1. A scroll compressor, having: a fixed scroll having a spiral wrap disposed upright on an end plate, the movement of which is restricted in an in-plane direction perpendicular to the wrap; The movable scroll, which has a spiral coil set upright on the end plate and meshes with the above-mentioned fixed scroll, does not rotate on its own axis in a plane perpendicular to the coil, but makes a rotary motion and shrinks between the fixed scroll and the above-mentioned fixed scroll the volume of the compression chamber formed; a crankshaft, which cooperates with the shaft support portion of the above-mentioned movable scroll and drives the movable scroll in rotation; The pressure separation mechanism is located on the end surface of the shaft support portion of the movable scroll, and separates the space formed on the back side of the movable scroll into a central space whose pressure is approximately equal to the discharge pressure and an outer periphery whose pressure is lower than the central space. internal space; a sliding bearing rotatably fitted to and supporting the movable scroll side portion of the crankshaft; a frame holding the above-mentioned sliding bearing on the inner peripheral surface; and, A thrust bearing positioned closer to the movable scroll than the sliding bearing and supporting the axial movement of the crankshaft, wherein The above-mentioned thrust bearing is constituted by another part different from the above-mentioned sliding bearing and the above-mentioned frame, and the opposite side of the bearing surface of the above-mentioned thrust bearing is supported by the support surface formed by the above-mentioned frame, and the inner diameter of the support surface of the frame is It is made smaller than the outer diameter of the above-mentioned sliding bearing. 2. The scroll compressor according to claim 1, wherein: An enlarged portion opposite to the orbiting scroll is formed on an inner peripheral surface of the frame, and an outer peripheral portion of the sliding bearing is accommodated in the enlarged portion, and the sliding bearing is mounted on the frame. 3. The scroll compressor according to claim 1 or 2, characterized in that, An oil supply passage for supplying lubricating oil through the crankshaft is formed, and a first oil supply passage is formed for the lubricating oil supplied from the oil supply passage of the crankshaft to flow to the oil discharge passage through the rotary bearing provided inside the shaft support portion of the movable scroll. An oil passage is provided between the slide bearing and the oil discharge passage to form a second oil supply passage through which lubricating oil supplied from the oil supply passage of the crankshaft flows from the slide bearing to the oil discharge passage through the oil passage. 4. The scroll compressor of claim 3, wherein: A space communicating with one side of the sliding bearing is formed on the inside of the thrust bearing along the entire circumference, and a space communicating with the oil discharge passage is formed on the outside of the thrust bearing along the entire circumference. On both sides or at least one side of the surface and the opposite surface of the bearing surface, a plurality of grooves connecting the inner space and the outer space of the thrust bearing are formed, and serve as oil passages for the second oil supply passage. 5. The scroll compressor of claim 3, wherein: A space constituting a part of the first oil supply passage is formed outside the thrust bearing, and a linear through hole communicating from the outer periphery of the frame to the outer space of the thrust bearing is formed to form the oil discharge passage. A groove is formed continuously in the axial direction thereof on the thrust bearing support surface of the frame and the thrust bearing pressure plate portion as an oil passage of the second oil supply passage. 6. The scroll compressor of claim 3, wherein: Grooves are formed on both sides of the bearing surface of the thrust bearing and the surface opposite to the bearing surface, and serve as oil passages for the second oil supply passage. 7. The scroll compressor of claim 5, wherein: A rotation stopper is provided on the thrust bearing, and the rotation stopper is incorporated into an oil passage formed in a part of the pressure plate part of the thrust bearing. 8. A scroll compressor, having: a fixed scroll having a spiral wrap disposed upright on an end plate, the movement of which is restricted in an in-plane direction perpendicular to the wrap; The movable scroll, which has a spiral coil set upright on the end plate and meshes with the above-mentioned fixed scroll, does not rotate on its own axis in a plane perpendicular to the coil, but makes a rotary motion and shrinks between the fixed scroll and the above-mentioned fixed scroll the volume of the compression chamber formed; a crankshaft that cooperates with a shaft support protruding from the central portion of the movable scroll to rotationally drive the movable scroll; The pressure separation mechanism is installed on the end surface of the shaft support portion of the movable scroll, and separates the space formed on the back side of the movable scroll into a central space whose pressure is approximately equal to the discharge pressure and a pressure ratio of the central space. low peripheral space; a sliding bearing rotatably fitted to and supporting the movable scroll side portion of the crankshaft; a frame holding the above-mentioned sliding bearing on the inner peripheral surface; and, A thrust bearing which is positioned closer to the movable scroll than the slide bearing and supports the axial movement of the crankshaft, wherein The thrust bearing unit is integrally built with the frame using a member different from the sliding bearing, and the inner diameter of the bearing surface of the thrust bearing unit is made smaller than the outer diameter of the sliding bearing. 9. The scroll compressor of claim 8, wherein: An enlarged portion on the opposite side of the orbiting scroll is formed on the inner peripheral surface of the above-mentioned frame, and the outer peripheral portion of the above-mentioned sliding bearing is accommodated in the enlarged portion, and the sliding bearing is installed on the above-mentioned frame to form a supply through the above-mentioned crankshaft. The oil supply passage for lubricating oil forms a first oil supply passage for supplying lubricating oil supplied from the oil supply passage of the crankshaft to the oil discharge passage through the rotary bearing provided inside the shaft support portion of the movable scroll. Lubricating oil supplied from the oil supply passage of the crankshaft passes through the sliding bearing to the second oil supply passage to the oil discharge passage, forming a bypass to both the bearing surface side and the opposite side of the bearing surface of the thrust bearing or at least one side of the oil channel. 10. The scroll compressor of claim 9, wherein: A space constituting a part of the first oil supply passage is formed outside the thrust bearing, and a linear through hole communicating with the space outside the thrust bearing from the outer periphery of the frame is formed to form the oil discharge passage. A groove is formed axially continuous thereto on the supporting surface of the above-mentioned frame as an oil passage of the above-mentioned second oil supply passage. 11. A scroll compressor, having: a fixed scroll having a spiral wrap disposed upright on an end plate, the movement of which is restricted in an in-plane direction perpendicular to the wrap; The movable scroll, which has a spiral coil set upright on the end plate and meshes with the above-mentioned fixed scroll, does not rotate on its own axis in a plane perpendicular to the coil, but makes a rotary motion and shrinks between the fixed scroll and the above-mentioned fixed scroll the volume of the compression chamber formed; a crankshaft, which cooperates with the shaft support portion of the above-mentioned movable scroll and drives the movable scroll in rotation; The pressure separation mechanism is located on the end surface of the shaft support portion of the movable scroll, and separates the space formed on the back side of the movable scroll into a central space whose pressure is approximately equal to the discharge pressure and an outer periphery whose pressure is lower than the central space. internal space; a sliding bearing rotatably fitted to and supporting the movable scroll side portion of the crankshaft; a frame holding the above-mentioned sliding bearing on the inner peripheral surface; and, A thrust bearing positioned closer to the movable scroll than the sliding bearing and supporting the axial movement of the crankshaft, wherein An oil supply passage for supplying lubricating oil through the above-mentioned crankshaft is formed, and a first supply passage is formed for the lubricating oil supplied from the oil supply passage of the above-mentioned crankshaft to flow to the oil discharge passage through the rotary bearing provided inside the shaft support part of the above-mentioned movable scroll. An oil passage is provided between the sliding bearing and the oil discharge passage to form a second oil supply passage through which lubricating oil supplied from the oil supply passage of the crankshaft flows from the sliding bearing to the oil discharge passage through the oil passage. . 12. The scroll compressor of claim 11, wherein: A space constituting a part of the first oil supply passage is formed outside the thrust bearing, and a linear through hole communicating with the space outside the thrust bearing from the outer periphery of the frame is formed to form the oil discharge passage. A groove is formed axially continuous thereto on the supporting surface of the above-mentioned frame as an oil passage of the above-mentioned second oil supply passage.

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