JP2015161209A - Compressor and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor capable of suppressing biting of foreign substances and abrasion particles and abrasion in a gap between a crank shaft and a sliding bearing by facilitating discharge of the foreign substances flowed into a slide surface of the sliding bearing and the abrasion particles occurring on the slide surface.SOLUTION: A compressor includes a crank shaft including an eccentric part and rotating, an oil supply hole for opening from the inside of the crank shaft to an outer periphery of the crank shaft and a sliding bearing for sliding with the crank shaft and supporting the rotation of the crank shaft, and the compressor lubricates between the crank shaft and the sliding bearing by a lubrication oil supplied from the oil supply hole. On the outer periphery of the crank shaft, the compressor includes an oil supply groove for communicating with the oil supply hole and extending in a crank shaft direction, a slide region which has no grooves and a discharge groove extending in the crank shaft direction without communicating with the oil supply hole, from a crank shaft rotation direction front side in this order.

Description

  The present invention relates to a compressor including a sliding bearing portion that slides on an outer periphery of a rotating shaft via a lubricating oil, and a refrigeration cycle device including the compressor.

  A scroll compressor is a rotating machine that compresses a gas such as a refrigerant by relatively rotating two scroll members having a spiral tooth shape. In general, the scroll compressor is configured such that the other movable orbiting scroll orbits with respect to the fixed scroll constrained by screw fastening or welding.

  The orbiting scroll is provided with an orbiting slide bearing that engages and slides with the eccentric portion of the crankshaft. Then, while the eccentric portion of the crankshaft and the orbiting slide bearing slide through the lubricating oil, the swinging rotational motion of the eccentric portion of the crankshaft is transmitted to the orbiting scroll, and the orbiting scroll is caused to orbit. A crankshaft that is connected to the rotor of the electric motor and rotates is supported by sliding through a lubricating oil with respect to a plain bearing called a main bearing and a sub-bearing fixed in the scroll compressor.

  Lubricating oil is sealed in the internal space of the compressor. Lubricating oil is supplied to each slide bearing by the pressure difference between the suction side and the discharge side in the compression mechanism or the oil supply pump mechanism, and after passing through the gap between the slide bearing and the crankshaft, returns to the internal space of the compressor again. Circulate.

  When foreign matter or wear particles are mixed in the lubricant, or when wear particles are generated by sliding between the crankshaft and the slide bearing, if these particles stay on the sliding surface of the slide bearing without being discharged, There is a possibility that it will get caught in the gap in the sliding area with the slide bearing or promote wear. Therefore, it is necessary to suppress the bearing damage due to such foreign matters and wear particles.

  Japanese Unexamined Patent Application Publication No. 2007-239530 (Patent Document 1) is known as a conventional technique for suppressing damage to the bearing due to foreign matters mixed in the lubricating oil. In this document, “a main shaft supported by a bearing and transmitting power to a compression portion, a hollow space provided inside the main shaft to serve as an oil supply path, and a hollow space penetrating from the hollow space to the outer periphery of the main shaft is provided. An oil supply communication port, a notch-shaped oil supply groove formed in the axial direction on the outer peripheral surface of the main shaft in communication with the oil supply communication port, and the oil supply communication on the outer peripheral surface of the main shaft so as to be within the area of the bearing. A compressor having a spiral oil supply groove formed at a position shifted in the axial direction from the opening and inclined with respect to the main axis.

  In the compressor described in Patent Document 1, a notch-shaped oil supply groove communicating with the oil supply path and a spiral oil supply groove different from the oil supply groove are provided at different positions in the axial direction. With such a structure, among foreign matters contained in the lubricating oil from the oil supply passage, those having a size exceeding the sum of the gap between the main shaft and the bearing and the depth of the notched oil supply groove are transferred to the spiral oil supply groove. Restricts the inflow of foreign materials and suppresses damage caused by foreign objects.

  As another conventional technique, there is one described in JP-A-2005-233021 (Patent Document 2). In Patent Document 2, “each plate-like spiral tooth has a fixed scroll and an orbiting scroll meshed so as to form a compression chamber therebetween, and by driving the orbiting scroll by a main shaft, A compression mechanism that compresses the refrigerant in the compression chamber and an electric motor that rotates the main shaft by an electric motor are provided in a sealed container, and an axial oiling hole that is formed in the axial direction inside the main shaft is provided. Refrigeration oil at the bottom of the hermetic container is supplied to a sliding part such as a bearing through the axial oiling hole by differential pressure lubrication utilizing the pressure difference between the discharge pressure and the suction pressure in the hermetic container. In addition, a foreign matter discharge hole having an opening that opens into the sealed container is formed in the main shaft so as to communicate with the axial oil supply hole in the middle of oil supply to the sliding portion of the bearing or the like, and the foreign matter discharge hole is frozen. With respect to the machine oil pressure, The pressure head formed by the centrifugal force due to rotation during operation is made larger than the pressure head formed by the distance from the lower end of the main shaft of the foreign matter discharge hole, and the refrigerating machine oil in the opening is introduced into the sealed container. The scroll compressor is characterized in that the foreign matter discharge hole is provided so that the discharge pressure becomes larger than the discharge pressure in the sealed container. "

  In the compressor described in Patent Document 2, a foreign matter discharge hole communicating with the oil supply hole and the space in the sealed container is provided in the main shaft, and the pressure of the lubricating oil flowing in the foreign matter discharge hole is reduced by the centrifugal force accompanying the rotation of the main shaft. Increase. With such a structure, foreign matters contained in the lubricating oil are easily discharged into the space in the sealed container through the foreign matter discharge holes, and foreign matters flowing into other bearing portions are reduced.

JP 2007-239530 A JP 2005-233021 A

  However, in Patent Document 1, although the large-diameter foreign material having a size exceeding the sum of the gap between the main shaft and the bearing and the depth of the notch-shaped oil supply groove is suppressed, the bearing slides. The retention of wear particles caused by the sliding of the small-diameter foreign matter flowing into the surface and the main shaft and the bearing is not particularly reduced as compared with other general bearings.

  Further, in Patent Document 2, it is possible to separate foreign matter using centrifugal force before the lubricating oil flows into the bearing, and to reduce the inflow of foreign matter to the sliding surface of the bearing. The retention of wear particles generated by sliding between small particles or the main shaft and the bearing is not particularly reduced as compared with other general bearings.

  The present invention promotes the discharge of foreign matter that has flowed into the sliding surface of the slide bearing and the wear particles generated on the slide surface, thereby preventing the foreign matter and wear particles from being caught and worn in the gap between the crankshaft and the slide bearing. It is an object to provide a compressor that can be suppressed.

  The compressor of the present invention includes a crankshaft that rotates with an eccentric portion, an oil supply hole that opens from the inside of the crankshaft to the outer periphery of the crankshaft, and a slide bearing that slides on the crankshaft and supports the rotation of the crankshaft. , And a lubricant that lubricates between the crankshaft and the slide bearing with the lubricating oil supplied from the oil supply hole, and communicates with the oil supply hole on the outer periphery of the crankshaft in order from the front side in the rotation direction of the crankshaft. An oil supply groove extending in the crankshaft direction, a sliding region where no groove exists, and a discharge groove extending in the crankshaft direction without communicating with the oil supply hole are provided.

  According to the present invention, even when foreign matter is mixed in the clearance between the outer periphery of the crankshaft that rotates and the slide bearing, or when wear particles are generated by sliding between the crankshaft and the slide bearing, the foreign matter and wear particles Can be discharged from the sliding surface of the sliding bearing at an early stage, and the retention on the sliding surface can be reduced to prevent biting and wear and to improve the reliability of the bearing.

Vertical section showing scroll compressor Enlarged sectional view near the main bearing in a scroll compressor 2A-A sectional view A graph showing the relationship between the groove start position on the outer periphery of the crankshaft and the relative oil film thickness Expanded sectional view of the vicinity of the main bearing according to the first modification Enlarged sectional view near the main bearing according to the second modification Enlarged sectional view near the main bearing according to the third modification Enlarged sectional view near the main bearing according to the fourth modification

  The compressor of the present invention includes a crankshaft that rotates with an eccentric portion, an oil supply hole that opens from the inside of the crankshaft to the outer periphery of the crankshaft, and a slide bearing that slides on the crankshaft and supports the rotation of the crankshaft. , And a lubricant that lubricates between the crankshaft and the slide bearing with the lubricating oil supplied from the oil supply hole, and communicates with the oil supply hole on the outer periphery of the crankshaft in order from the front side in the rotation direction of the crankshaft. An oil supply groove extending in the crankshaft direction, a sliding region where no groove exists, and a discharge groove extending in the crankshaft direction without communicating with the oil supply hole are provided. The oil supply groove and the discharge groove are provided across the sliding area, so that foreign matter that has flowed into the sliding surface of the slide bearing and wear particles generated by the sliding are collected and discharged at an early stage. The reliability as a bearing can be improved.

  Embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view showing a scroll compressor 100 according to an embodiment of the present invention. In the present embodiment, the scroll compressor 100 will be described as an example. The scroll compressor 100 is a hermetic compressor used for refrigeration and air conditioning such as an air conditioner such as an air conditioner or a refrigeration apparatus. The scroll compressor 100 has a hermetic container 102, and includes a fixed scroll 103 and a revolving scroll 104 that meshes with the fixed scroll 103 and rotates. The fixed scroll 103 and the orbiting scroll 104 each have a spiral tooth shape portion.

  In the sealed container 102, an electric motor 105 as a rotational power source is provided. A crankshaft (shaft) 106 is connected to the rotor of the electric motor 105. A crankshaft 106 connected to the electric motor 105 and rotationally moves is constituted by a main bearing (slide bearing) 108 provided on a frame 107 fixed in the sealed container 102 and a sub-bearing 110 provided on a lower frame 109. , Supported rotatably.

  An eccentric portion 106 a having an eccentricity with respect to the axial center of the portion supported by the main bearing 108 and the auxiliary bearing 110 of the crankshaft 106 is provided on the upper portion of the crankshaft 106. The eccentric portion 106a is engaged with and slides on the orbiting bearing 112 provided on the lower surface (rear surface) side of the end plate 104a of the orbiting scroll 104, and the whirling rotation motion (eccentric motion) of the eccentric portion 106a is the orbiting scroll 104. Is transmitted to.

  The rotation of the orbiting scroll 104 is restricted by the Oldham ring 113 and revolves with respect to the fixed scroll 103. The Oldham ring 113 is attached to a groove formed on the lower surface (back surface) side of the end plate 104 a of the orbiting scroll 104 and a groove formed on the frame 107. When the orbiting scroll 104 orbits through the crankshaft 106 that is rotationally driven by the electric motor 105, low-pressure refrigerant gas is sucked from the suction port 114 and guided to the compression chamber formed by the orbiting scroll 104 and the fixed scroll 103. . Here, the refrigerant gas is compressed by reducing the volume as it moves in the center direction of the scrolls 103, 104, and then discharged to the outside of the compressor through the inside of the sealed container 102 and the discharge port 115.

  The crankshaft 106 has an oil supply hole 116 penetrating from the lower end to the end surface (upper end surface) side of the eccentric portion 106a along the axial direction. The lubricating oil 117 stored in the lower portion of the hermetic container 102 is supplied to the oil supply hole 116 by a pressure difference using the discharge pressure of the refrigerant gas or by a pump (not shown) separately attached to the lower end portion of the crankshaft 106. The inside is pushed up and supplied to the gap between the inner peripheral surface of each bearing (main bearing 108, sub-bearing 110, slewing bearing 112) and the outer peripheral surface of the crankshaft 106.

  In the compressor of the present embodiment, the inside of the sealed container 102 has a discharge pressure, and an intermediate chamber (back pressure chamber) 118 formed on the lower surface side of the end plate 104a of the orbiting scroll 104 is an intermediate between the discharge pressure and the suction pressure. Pressure. For this reason, the lubricating oil 117 stored in the lower part of the sealed container 102 is pushed up in the oil supply hole 116 due to the pressure difference between the discharge pressure and the intermediate pressure, and is supplied to each bearing.

  FIG. 2 is an enlarged cross-sectional view of the vicinity of the main bearing 108 of the compressor 100. As shown in FIG. 2, the main bearing 108 is configured such that two cylindrical slide bearing bushes 120 are connected via an intermediate passage 121 inside a bearing housing (housing portion) provided with a frame 107 made of cast iron, for example. Arranged side by side. The crankshaft 106 has an oil supply port 119 communicating with an internal oil supply hole 116 that opens to the outer periphery of the crankshaft 106 within the range of the main bearing 108 in the axial direction. On the outer periphery of the crankshaft 106, a first groove (oil supply groove) 122 and a second groove (discharge groove) 123 are provided at different positions in the circumferential direction.

  The oil supply groove 122 extends in the axial direction from the oil supply port 119 toward the intermediate chamber side space 124 (the discharge space from which the lubricating oil that lubricated the bearing is discharged), and opens to the oil supply port 119 and the intermediate chamber side space 124. The intermediate chamber side space 124 communicates with the intermediate chamber 118 having a pressure lower than that of the oil supply hole 116 through the passage 125. The motor-side end of the main bearing 108 faces the sealed container 102, which is the discharge pressure, and the pressure of the intermediate passage 121 is smaller than the discharge pressure or the pressure of the oil supply hole 116 and more than the pressure of the intermediate chamber 118. Become. For this reason, the lubricating oil that has flowed into the oil supply port 119 from the oil supply hole 116 due to the pressure difference flows out into the intermediate chamber side space 124 through the oil supply groove 122, or once flows into the gap between the crankshaft 106 and the bearing bush 120. Later, it flows out into the intermediate chamber side space 124, and a part flows out into the intermediate passage 121.

  On the other hand, the discharge groove 123 has one end opened to the intermediate chamber side space 124 and the other end opened to the intermediate passage 121, but does not directly open to the oil supply hole 116 or the oil supply port 119. Therefore, the lubricating oil once flows into the gap between the crankshaft 106 and the bearing bush 120 from the oil supply port 119 and then passes through the sliding region 106b, or reaches the discharge groove 123 via the intermediate passage 121, and finally Then, the gas flows out into the intermediate chamber side space 124 through the discharge groove 123 or the clearance between the crankshaft 106 and the bearing bush 120 on the rear side in the rotation direction. Therefore, even when the discharge groove 123 is provided, the flow resistance decrease from the oil supply port 119 to the intermediate chamber side space 124 is small and the increase in the flow rate of the lubricating oil is also small.

  The lubricating oil that has flowed out of the main bearing 108 into the intermediate chamber side space 124 flows into the intermediate chamber 118 through the passage 125. When the amount of lubricating oil flowing into the intermediate chamber 118 increases, loss due to stirring in the intermediate chamber 118 tends to increase. Therefore, in the compressor, it is desirable to control the flow rate of the lubricating oil to an appropriate flow rate without increasing the flow rate of the lubricating oil more than necessary in order to suppress the reduction in efficiency and increase in power consumption due to the increase in loss.

  3 is a cross-sectional view taken along line AA of FIG. 2 at a certain moment during operation of the scroll compressor. The crankshaft 106 swings and rotates in the rotation direction 126 within the bearing bush 120, and a load 127 is applied to the crankshaft 106. The arrangement on the outer periphery of the crankshaft 106 is in order of the oil supply groove 122, the sliding area 106 b without the groove, and the discharge groove 123 from the front side in the rotation direction 126.

  In the gap between the crankshaft 106 and the bearing bush 120, the grooved portion is larger by the depth of the groove than the others. The oil supply groove 122 opens to the oil supply port 119 and the intermediate chamber side space 124, and serves as an oil supply groove that supplies lubricating oil to the sliding region 106 b from the front side in the rotation direction 126. Also, the oil supply groove 122 discharges foreign matter flowing from the oil supply port 119 to the intermediate chamber side space 124, and reduces the amount of foreign matter flowing into the sliding region 106b and other sliding surfaces.

  In general, it is known that in the initial operation of the compressor, the crankshaft 106 and the bearing bush 120 are adapted to be rubbed together with slight wear. In FIG. 3, when wear particles are generated by sliding between the crankshaft 106 and the bearing bush 120 in the sliding area 106 b, the wear particles are sandwiched between the crankshaft 106 and the bearing bush 120. Is carried rearward in the circumferential direction.

  The discharge groove 123 is installed behind the sliding region 106 b with respect to the rotation direction 126, and the gap between the crankshaft 106 and the bearing bush 120 is enlarged by the depth of the discharge groove 123 in this portion. For this reason, the wear particles carried rearward in the circumferential direction are released into the lubricating oil when they reach the discharge groove 123 and are collected in the discharge groove 123. The discharge groove 123 is open to the intermediate chamber side space 124, and the wear particles are discharged to the intermediate chamber side space 124. Similarly, foreign matter that has flown into the gap between the crankshaft 106 and the bearing bush 120 without being discharged through the oil supply groove 122 is released into the lubricating oil when it reaches the discharge groove 123, and is discharged into the intermediate chamber side space 124. .

  In this manner, the discharge groove 123 has a function of collecting wear particles and foreign matters and discharging them to the intermediate chamber side space 124, and the retention of wear particles and foreign matters on the sliding surface of the bearing and the sliding surfaces resulting therefrom. To prevent the wear and biting of the product. In particular, it is known that the familiar phenomenon progresses in a short time in high-load operation, and the frequency of generation of wear particles is high, and as in this embodiment, the exhaustability of wear particles from the sliding surface is improved. Thus, the reliability as a bearing can be improved even during high-load operation.

  FIG. 4 is a graph showing the relationship between the starting position of the groove on the outer periphery of the crankshaft and the relative oil film thickness (a diagram for explaining the relationship between the starting position of the discharge groove 123 and the relative minimum oil film thickness). In order to specify the position where the discharge groove 123 can be installed, the position is changed on the outer periphery of the crankshaft 106 to provide the discharge groove 123, and the crankshaft 106 is slid with respect to the cylindrical slide bearing through the lubricating oil. The minimum oil film thickness was measured. In this verification, a scroll compressor for an air conditioner having an eccentric shaft diameter of 14 to 25 mm is assumed.

In FIG. 4, the horizontal axis represents the circumferential start position of the discharge groove 123 when the position of the eccentric portion 106 a of the crankshaft 106 is 0 °, and the vertical axis represents the minimum oil film thickness when a crankshaft without the discharge groove 123 is used. The relative minimum oil film thickness with respect to 100% is shown. As shown in FIG. 4, when the start position of the discharge groove 123 is less than 150 degrees, the start position of the discharge groove 123 is near the angle at which the minimum oil film thickness is obtained. If the bearing is provided, the bearing behavior becomes unstable, the minimum oil film thickness decreases, and wear due to contact between the shaft and the bearing tends to proceed. Therefore, the start position of the discharge groove 123 can be determined at least 150 degrees or more. preferable. In addition, from the viewpoint of collecting the wear particles generated in the sliding region at an early stage, it is desirable that the circumferential start position of the discharge groove 123 be as small as possible.
(First modification)
FIG. 5 is an enlarged cross-sectional view of the vicinity of the main bearing 108 according to the first modification of the present embodiment. The configuration and operation similar to those of the first embodiment shown in FIGS. 1 to 3 will not be described in detail because they are incorporated in the first modification, and different points will be described (further described below). The same applies to the modified example).

As shown in FIG. 5, the first modification is different from the first embodiment in that the lower end of the discharge groove 123 in the drawing is within the range of the bearing bush 120 and does not reach the intermediate passage 121. According to such a first modification, the lubricating oil flow path from the intermediate passage 121 through the discharge groove 123 to the intermediate chamber side space 124 passes through the gap between the crankshaft 106 and the bearing bush 120. As compared with the first embodiment, the channel resistance is increased. Therefore, in the first modified example, in addition to being able to achieve the same operational effects as in the first embodiment, it is possible to reduce the amount of lubricating oil flowing out from the main bearing 108 to the intermediate chamber side space 124. Further, compared to the first embodiment, even if the width and depth of the discharge groove 123 are increased, the amount of lubricating oil can be maintained at the same level, and it is possible to cope with the collection of larger foreign matters and wear particles.
(Second modification)
FIG. 6 is an enlarged cross-sectional view of the vicinity of the main bearing 108 according to the second modification of the present embodiment. As shown in FIG. 6, the second modification is the first implementation in that the end of the discharge groove 123 is a narrowed portion 123 a having a smaller cross-sectional area (channel area) in the direction perpendicular to the axial direction than the other portions. It differs from the form. According to such a second modification of the first embodiment, the flow path of the lubricating oil from the intermediate passage 121 through the discharge groove 123 to the intermediate chamber side space 124 has a cross-sectional area (flow It passes through the narrowed portion 123a having a small road area. Thereby, in addition to being able to have the same operational effects as in the first embodiment in the first modification, the axial cross-sectional area of the discharge groove 123 is enlarged with the aim of improving the collection of foreign matters and wear particles. However, it is possible to suppress an increase in the amount of lubricating oil flowing out from the main bearing 108 into the intermediate chamber side space 124.

In FIG. 6, the narrowed portion 123 a is provided on both the intermediate chamber side space 124 side and the intermediate passage 121 side of the discharge groove 123, but lubrication from the intermediate passage 121 through the discharge groove 123 to the intermediate chamber side space 124 is performed. From the viewpoint of narrowing the oil flow path, the same effect can be obtained even if the throttle portion 123a is provided on one side.
(Third Modification)
FIG. 7 is an enlarged cross-sectional view of the vicinity of the main bearing 108 according to the third modification of the present embodiment. As shown in FIG. 7, the third modification is the first implementation in that the intermediate chamber side space 124 side of the discharge groove 123 is inclined rearward in the rotational direction 126 with respect to the central passage 121 side of the discharge groove 123. It differs from the form and other modifications. According to the third modified example, foreign matter and wear particles collected in the discharge groove 123 are easily moved in the direction of the intermediate chamber side space 124 by the rotational movement of the crankshaft 106, and thus the discharge performance is improved. To do.
(Fourth modification)
FIG. 8 is an enlarged cross-sectional view of the vicinity of the main bearing 108 according to the fourth modification of the present embodiment. As shown in FIG. 8, in the fourth modified example, the fuel filler 119 is formed in the intermediate passage 121, and the sectional area (flow passage area) in the direction perpendicular to the axial direction of the throttle portion 123 a communicating with the intermediate passage 121 is set. The difference from the first embodiment and other modified examples is that the oil supply groove 122 is smaller than the cross-sectional area (flow passage area) in the direction perpendicular to the axial direction. According to such a fourth modification, in addition to being able to achieve the same operational effects as the first embodiment, a part of the foreign matter that has flowed into the main bearing 108 from the fuel filler port 119 is collected by the intermediate passage 121. Thus, it is possible to reduce the amount flowing into the sliding surface of the bearing bush 120. Further, since the cross-sectional area (flow passage area) in the direction perpendicular to the axial direction of the throttle portion 123 a is made smaller than the cross-sectional area (flow passage area) in the direction perpendicular to the axial direction of the oil supply groove 122, the lubricating oil takes precedence over the oil supply groove 122. Therefore, the supply of the lubricating oil to the sliding region 106b is the same as in the first embodiment and other modified examples.
(Cross sectional shape)
In the first embodiment and the modification, the oil supply groove 122 and the discharge groove 123 are formed as notched grooves in which a part of the outer periphery of the crankshaft 106 is cut on a flat surface. It may be formed as a recessed digging groove. The notch groove has an advantage that it can be easily processed, but the circumferential width is greatly enlarged with respect to the radial depth, and the axial sectional area of the groove is easily enlarged. On the other hand, since the digging groove can be freely formed in depth and width, it is possible to collect and discharge particles having a large diameter with a small axial cross-sectional area, and to reduce the amount of lubricating oil passing therethrough.

  As mentioned above, although this invention was demonstrated based on embodiment, this invention is not limited to a scroll compressor, The other compressor which has a similar shaft and bearing structure is also included. Examples of other compressors include a rotary compressor, a rolling piston compressor, and a reciprocating compressor.

  Moreover, although the example of the main bearing of the scroll compressor was demonstrated, it is not necessarily limited to what is provided with all the demonstrated structures. Any bearing mechanism provided with a rotating shaft (swinging) in the compressor, a plain bearing, and an oil supply path from the inside of the shaft to the sliding surface of the bearing is included in the implementation target. In this case, for example, a slewing bearing, a secondary bearing, and the like are included in the implementation object by using the intermediate chamber side space 124 as a name of a portion from which the lubricant flows out from each bearing. Further, the present invention includes, for example, a vertical compressor and a horizontal compressor regardless of the direction of the rotating shaft.

  Further, the slide bearing in which the bearing bush 120 is inserted into the bearing housing portion provided in a part of the frame 107 has been described. However, the structure is not limited to this structure as long as it is a general journal slide bearing. Also included are those in which the bearing portion is directly formed.

  Moreover, this invention can be comprised as a refrigeration cycle apparatus provided with the compressor which concerns on this invention as a refrigerant | coolant compressor for refrigeration or an air conditioning. The refrigeration cycle apparatus includes a compressor according to the present invention, a condenser that radiates heat from a refrigerant gas that has been compressed by the compressor into high temperature and pressure, a decompression device that decompresses high-pressure refrigerant from the condenser, An evaporator for evaporating liquid refrigerant from the apparatus. Such a refrigeration cycle apparatus is used for a refrigeration apparatus, an air conditioner, a heat pump type hot water heater, and the like.

100 ... Compressor (scroll compressor)
DESCRIPTION OF SYMBOLS 102 ... Sealed container 103 ... Fixed scroll 104 ... Orbiting scroll 105 ... Electric motor 106 ... Crankshaft (shaft)
106a ... eccentric part 106b ... sliding area 107 ... frame 108 ... main bearing (slide bearing)
109 ... Lower frame 110 ... Sub bearing 112 ... Slewing bearing 113 ... Oldham ring 114 ... Suction port 115 ... Discharge port 116 ... Oil supply hole 117 ... Lubricating oil 118 ... Intermediate chamber (back pressure chamber)
119: Oil supply port 120 ... Bearing bush 121 ... Intermediate passage 122 ... Groove (oil supply groove)
123 ... groove (discharge groove)
123a ... throttle part 124 ... intermediate chamber side space 125 ... passage 126 ... rotation direction 127 ... load

Claims (10)

A crankshaft rotating with an eccentric part;
An oiling hole that opens from the inside of the crankshaft to the outer periphery of the crankshaft;
A slide bearing that slides on the crankshaft to support rotation of the crankshaft;
With
A compressor that lubricates a space between the crankshaft and the slide bearing with lubricating oil supplied from the oil supply hole;
On the outer periphery of the crankshaft, in order from the front side of the crankshaft rotation direction,
An oil supply groove communicating with the oil supply hole and extending in the crankshaft direction;
A sliding area where no groove exists,
A discharge groove extending in the crankshaft direction without communicating with the oil supply hole;
A compressor comprising: In claim 1,
One end of the oil supply groove communicates with a discharge space from which lubricating oil lubricated between the crankshaft and the slide bearing is discharged,
One end of the discharge groove is a compressor communicating with the discharge space. In claim 1 or 2,
The discharge groove is a compressor provided at a position of 150 ° or more in the counter-rotating direction of the crankshaft from the eccentric portion. In any one of Claims 1 thru | or 3,
The sliding bearing includes a first sliding bearing bush located on one end side in the crankshaft direction, a second sliding bearing bush located on the other end side in the crankshaft direction, the first sliding bearing bush and the second sliding bearing. An intermediate passage located between the bearing bushes,
A compressor in which the other end of the discharge passage communicates with the intermediate passage. In any one of Claims 1 thru | or 3,
The sliding bearing includes a first sliding bearing bush located on one end side in the crankshaft direction, a second sliding bearing bush located on the other end side in the crankshaft direction, the first sliding bearing bush and the second sliding bearing. An intermediate passage located between the bearing bushes,
A compressor in which the other end of the discharge passage is not the intermediate passage. In any of claims 1 to 5,
At least one end or the other end of the discharge groove has a throttle portion, and the throttle portion has a smaller flow path area than a portion of the discharge groove other than the throttle portion. In any one of Claims 1 thru | or 6,
One end of the discharge groove communicates with a discharge space from which lubricating oil lubricated between the crankshaft and the slide bearing is discharged,
The compressor in which the one end side of the discharge groove is inclined more to the counter-rotating direction side of the crankshaft than the other end side of the discharge groove. In any one of Claims 1 thru | or 7,
The sliding bearing includes a first sliding bearing bush located on one end side in the crankshaft direction, a second sliding bearing bush located on the other end side in the crankshaft direction, the first sliding bearing bush and the second sliding bearing. An intermediate passage located between the bearing bushes,
The oiling hole communicates with the intermediate passage;
The other end of the discharge groove communicates with the intermediate passage,
The other end of the discharge groove is a compressor having a flow path area smaller than that of the oil supply groove.   The compressor according to any one of claims 1 to 8, wherein the compressor is a scroll compressor.   A refrigeration cycle apparatus comprising the compressor according to any one of claims 1 to 9.