JP2008101538A - Refrigerant compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To ensure an inexpensive and reliable refrigerant compressor. <P>SOLUTION: This refrigerant compressor 10 is provided with a sealed container 1, a compressor section 2 compressing a chlorine-free refrigerant; a rotating shaft 7 driving the compressor section 2; a bearing pivoting the rotating shaft 7; and an electric motor 9 moving the rotating shaft 7. The rotating shaft 7 has a main shaft part 7a fixed to the rotor 9b of the electric motor and a crank part 7b engaged with the compressor section 2. The bearing has a main bearing 6c pivoting the main shaft part 7a and a crank bearing 4c pivoting the crank part 7b. The main bearing 6c is constituted of a crank side main bearing 6c1 and an electric motor side main bearing 6c2 located adjacently to the crank side main bearing. The crank bearing 4c and crank side main bearing 6c1 are constituted of a carbon bearing impregnated with metal into pores of carbonaceous base material containing graphite. The electric motor side main bearing 6c2 is constituted of a winding bush formed by being wound with a plate member. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a refrigerant compressor, and is particularly suitable for a refrigerant compressor used for air conditioning, refrigeration, and hot water supply.

  A conventional refrigerant compressor is disclosed in Japanese Patent Application Laid-Open No. 2002-147354 (Patent Document 1). The refrigerant compressor includes a compressor unit that compresses a chlorine-free refrigerant, a rotary shaft that drives the compressor unit, a bearing that supports the rotary shaft, and a rotary shaft that rotates the rotary shaft. And an electric motor to be exercised. The rotating shaft has a main shaft portion fixed to the rotor of the electric motor and a crank portion engaged with the compressor portion. The bearing of the rotating shaft has a main bearing that supports the main shaft portion on the compressor portion side of the electric motor, and a crank bearing that supports the crank portion. It is disclosed that a carbon bearing material, a resin bearing material, a resin composite bearing material with a backing metal, or the like is used as the main bearing and the crank bearing.

JP 2002-147354 A

  In the refrigerant compressor of Patent Document 1 described above, when a carbon bearing is used for all of the main bearing and the crank bearing, there is a problem that the carbon bearing is expensive.

  In addition, when resin bearing material or resin composite bearing material with backing metal is used for all main bearings and crank bearings, it is difficult to ensure reliability such as wear resistance and seizure resistance in the boundary lubrication state. was there. Recently, refrigerants such as R410A, carbon dioxide, and propane have been used as refrigerants, and bearing loads have been increased to improve compressor performance, and a lubricating film made of lubricating oil has been partially applied at high surface pressure. The so-called boundary lubrication state, in which the bearing and the rotary shaft are in direct contact with each other, is likely to be in a so-called boundary lubrication state. In particular, the boundary lubrication state is likely to occur when the refrigerant compressor starts (starts) or when excessive refrigerant is mixed. It was.

  An object of the present invention is to provide a refrigerant compressor that is inexpensive and can ensure reliability, and an air conditioner, a refrigerator, and a water heater using the refrigerant compressor.

  According to a first aspect of the present invention for achieving the above-described object, a compressor unit that compresses a refrigerant not containing chlorine, a rotary shaft that drives the compressor unit, and the rotary shaft are provided in a sealed container. A bearing that supports the shaft, and an electric motor that rotationally moves the rotating shaft, the rotating shaft including a main shaft portion fixed to a rotor of the electric motor, and a crank portion engaged with the compressor portion. The bearing that pivotally supports the rotating shaft includes a main bearing that pivotally supports the main shaft portion and a crank bearing that pivotally supports the crank portion, wherein the main bearing is a crank-side main bearing. And an electric motor side main bearing adjacent to the crank side main bearing, and the crank bearing and the crank side main bearing are constituted by carbon bearings in which pores of a carbonaceous base material containing graphite are impregnated with metal, Side main bearing is formed by winding plate material It is those that are configured in a tree bush.

A more preferable specific configuration example in the first aspect of the present invention is as follows.
(1) The compressor unit is configured by meshing a fixed scroll in which a spiral wrap is erected on a base plate and a turning scroll in which a spiral wrap is erected on the base plate, and the crank bearing is Installed in a boss part that protrudes on the side opposite to the orbiting scroll, the main bearing pivotally supports the rotating shaft on the compressor side from the electric motor, and the rotating shaft is stored in the sealed container. An oil passage is provided to supply lubricating oil to the crank bearing and the main bearing by differential pressure.
(2) The wound bush is formed by winding a metal plate provided with a self-lubricating PTFE resin or a self-lubricating polyimide resin surface layer so that the surface layer is on the inside. thing.
(3) In (2), the wound bush is impregnated with a self-lubricating PTFE resin or a self-lubricating polyimide resin in a bronze porous body sintered on the metal plate. Having a layer.
(4) In the above (2) or (3), the crank bearing and the crank-side main bearing are formed of carbonaceous substrate pores containing 20 to 50% by weight of graphite in groups 1B, VIII excluding Fe, and Sn. Or a carbon bearing impregnated with an alloy mainly composed of these metals.
(5) In the above (2) or (3), the crank bearing and the crank side main bearing are one kind selected from Group 1B, Group VIII excluding Fe, and Sn in the pores of the carbonaceous substrate containing graphite, Or, it is composed of a carbon bearing impregnated with an alloy mainly composed of these metals and having a Shore hardness of 65 to 120.
(6) In the above (5), the crank bearing and the crank side main bearing are selected from the group consisting of 1B group, VIII group excluding Fe, and Sn in the pores of the carbonaceous substrate containing graphite, or these metals It was impregnated with an alloy mainly composed of a carbon bearing having a porosity of 0.05 to 2% by volume.
(7) In the above (2) or (3), the crank bearing and the crank side main bearing are selected from the group consisting of 1B group, VIII group excluding Fe, and Sn in the pores of the carbonaceous substrate containing graphite, Alternatively, it is constituted by a carbon bearing impregnated with an alloy mainly containing these metals and containing 0.2 wt% or less of at least one of V and Ti.
(8) The refrigerant is any one of R410A, carbon dioxide, and propane.

  Moreover, the 2nd aspect of this invention exists in the air conditioner using the refrigerant | coolant compressor in any one in the said 1st aspect of this invention and its preferable example.

  Moreover, the 3rd aspect of this invention exists in the refrigerator using the refrigerant compressor in any one in the said 1st aspect of this invention and its preferable example.

  Moreover, the 4th aspect of this invention exists in the water heater using the refrigerant compressor in any one in the said 1st aspect of this invention and its preferable example.

  According to the present invention, it is possible to obtain a refrigerant compressor that is inexpensive and can ensure reliability, and an air conditioner, a refrigerator, and a water heater using the refrigerant compressor.

  Hereinafter, a refrigerant compressor according to an embodiment of the present invention will be described with reference to the drawings.

  As shown in FIGS. 1 and 2, the refrigerant compressor 10 of the present embodiment includes a compressor unit 2 that compresses a refrigerant that does not contain chlorine in a sealed container 1, and a rotary shaft that drives the compressor unit 2. 7, the bearings 4c, 6c1, 6c2, and 6d that support the rotating shaft 7, the upper frame 6A that supports the bearings 6c1 and 6c2, the lower frame 6B that supports the bearing 6d, and the rotating shaft 7 are rotated. An electric motor 9 is provided as a main component. As the refrigerant not containing chlorine, any one of R410A, carbon dioxide, and propane is used. Lubricating oil is stored at the bottom of the sealed container 1.

  This refrigerant compressor 10 is configured by arranging the compressor unit 2 and the electric motor 9 through a rotary shaft 7 provided vertically, with the compressor unit 2 positioned upward and the electric motor 9 positioned downward. Type scroll compressor. The electric motor 9 includes a stator 9a fixed to the hermetic container 1 and a rotor 9b that is rotatably disposed inside the stator 9a.

  The compressor unit 2 includes a fixed scroll 5 in which a spiral wrap 5b is erected on a base plate 5a and a revolving scroll 4 in which the spiral wrap 4b is erected on a base plate 4a, with the wraps 5b and 4b meshing with each other. ing. A compression chamber is formed between the fixed scroll 5 and the orbiting scroll 4. A suction port 5d is formed in the outer peripheral portion of the fixed scroll 5, and a discharge port 5e is formed in the central portion. The fixed scroll 5 is fixed to the upper frame 6A by bolts. The orbiting scroll 4 is disposed between the fixed scroll 5 and the upper frame 6 </ b> A and is supported by the fixed scroll 5. The upper frame 6A is fixed to the sealed container 1 by welding or the like. The fixed scroll 5, the orbiting scroll 4 and the upper frame 6 are made of an Al-based alloy containing 5 to 15% by weight of cast iron or Si.

  An Oldham joint 8 serving as an anti-rotation mechanism is a joint for the orbiting scroll 4 to make a revolving motion without rotating with respect to the fixed scroll 5, and the rear keyway 4d of the base plate 4a of the orbiting scroll 4 and the upper frame 6A. It is engaged between the base keyway.

  The rotating shaft 7 has a main shaft portion 7 a fixed to the rotor 9 b of the electric motor 9 and a crank portion 7 b engaged with the compressor portion 2. A balance weight 3 is provided on the rotating shaft 7. The main shaft portion 7a extends vertically through the rotor 9b, and an oil introduction tube 7c is attached to the lower end portion. The crank portion 7 b is provided integrally with the upper end portion of the main shaft portion 7 a and is engaged with a boss portion 4 e provided so as to protrude to the opposite side of the orbiting scroll 4.

  In the main shaft portion 7a, the upper side of the rotor 9b is pivotally supported by the main bearing 6c, and the lower side of the rotor 9b is pivotally supported by the auxiliary bearing 6d. The main bearing 6c includes a crank side main bearing 6c1 and an electric motor side main bearing 6c2 adjacent to the crank side main bearing 6c1.

  The crank side main bearing 6c1 is formed of a carbon bearing in which pores of a carbonaceous base material containing graphite are impregnated with metal. Specifically, the crank-side main bearing 6c1 has one or more metals selected from Group 1B, Group VIII excluding Fe, and Sn in pores of a carbonaceous substrate containing 20 to 50% by weight of graphite. It is mainly composed of a carbon bearing impregnated with an alloy containing 0.2% by weight or less of at least one of V and Ti, having a Shore hardness of 65 to 120 and a porosity of 0.05 to 2% by volume.

  The motor-side main bearing 6c2 is formed of a wound bush formed by winding a plate material. Specifically, the motor-side main bearing 6c2 is formed by winding a metal plate having a surface layer of PTFE resin having self-lubricating property or polyimide resin having self-lubricating property so that the surface layer is on the inner side. It is a thing. In the present embodiment, a bronze porous material sintered on a metal plate is impregnated with PTFE resin having self-lubricating property or polyimide resin having self-lubricating property.

  The crank portion 7 is pivotally supported by a swivel bearing 4c constituting a crank bearing installed in the boss portion 4e. The slewing bearing 4c is composed of a carbon bearing in which pores of a carbonaceous substrate containing graphite are impregnated with metal. Specifically, this slewing bearing 4c is mainly composed of one or more metals selected from Group 1B, Group VIII excluding Fe, and Sn in pores of a carbonaceous substrate containing 20 to 50% by weight of graphite. It is made of a carbon bearing impregnated with an alloy containing 0.2% by weight or less of at least one of V and Ti, having a Shore hardness of 65 to 120 and a porosity of 0.05 to 2% by volume.

  Each of the bearings 4c, 6c1, and 6c2 is a sliding bearing having a length of 5 mm or more. As a result, a high load surface pressure applied to the slewing bearing 4c and the crank side main bearing 6c1 can be allowed, and a highly reliable refrigerant compressor can be obtained.

  The rotating shaft 7 is configured so that the lubricating oil stored at the bottom in the sealed container 1 is supplied to the auxiliary bearing 6d, the main bearing 6c, the swivel bearing 4c, the compressor unit 2 and the like by differential pressure. An oil passage 7d is formed through the central portion in the vertical direction. The oil passage 7d communicates with the oil introduction pipe 7c.

  In the refrigerant compressor having such a configuration, when the rotating shaft 7 is rotated by the electric motor 9 and the refrigerant compressor 10 is started, the orbiting scroll 4 is rotated to the fixed scroll 5 without rotating due to the eccentric rotation of the crank portion 7b. Performs a swivel motion. As a result, the refrigerant gas of the external refrigeration cycle is sucked into the compressor unit 2 through the suction pipe 11 through the suction port 5d, compressed in the compression chamber of the compressor unit 2, and discharged into the sealed container 1 through the discharge port 5e. The The discharged refrigerant gas is discharged from the discharge pipe 12 to the external refrigeration cycle.

  When the inside of the sealed container 1 is filled with high-pressure refrigerant gas, the lubricating oil at the bottom of the sealed container 1 passes through the oil introduction pipe 7c and the oil passage 7d due to the differential pressure, so that the auxiliary bearing 6d, the main bearing 6c, and the swivel bearing 4c and the compressor part 2 etc. are supplied, and these sliding parts are lubricated. However, at the time of start-up or when the discharge pressure of the refrigerant is high, supply of lubricating oil is insufficient and damage such as wear and seizure is likely to occur. In particular, damage such as wear and seizure is likely to occur at high load portions where the bearing surface pressure is high.

  Therefore, in the present embodiment, the crank bearing 4c and the crank side main bearing 6c1 that are high load portions with high surface pressure are constituted by carbon bearings in which pores of a carbonaceous base material containing graphite are impregnated with metal, thereby providing a boundary. By ensuring reliability such as wear resistance and seizure resistance in a lubricated state, the motor-side main bearing 6c2, which is a low load portion with low surface pressure, is constituted by a wound bush formed by winding a plate material, thereby reducing the cost. It is supposed to be.

  Next, a method for manufacturing the slewing bearing 4c and the crank side main bearing 6c1 used in the present embodiment will be described.

  First, a crucible containing a metal or alloy material is heated to a temperature 100 ° C. higher than the melting temperature of the metal or alloy in a vacuum furnace to bring the metal or alloy into a molten state. Next, a carbonaceous base material containing graphite composed of a cylinder or a rectangular body having a predetermined length is immersed in a molten metal or alloy of these metals, and pressurized with nitrogen gas, thereby The pores are impregnated with these metals and alloys. Thereafter, the carbonaceous base material is taken out from the crucible, and the carbonaceous base material is cut into a cylindrical shape, thereby forming the slewing bearing 4c and the crank side main bearing 6c1.

  Note that the carbonaceous substrate may be formed into a cylindrical shape by a near net shape and then cut into a predetermined length. Furthermore, the carbonaceous base material may be formed into a cylindrical body or a cylindrical body by a one-press molding method of a near net shape.

  Next, various bearing performances of Examples 1 to 7 which are bearing materials constituting the slewing bearing 4c and the crank side main bearing 6c1 used in the present embodiment will be described in comparison with Comparative Examples 1 to 6.

  Table 1 shows the type of impregnated metal (or impregnated alloy) and Shore hardness in Comparative Examples 1 to 4 and Examples 1 to 7.

ここで、実施例１、６におけるＳｎは、重量で、９９％である。実施例７におけるＣｕは、重量で、９９．９％である。実施例２〜５における青銅（ＢＣ３）は、重量で、Ｓｎ１０％、亜鉛２％及びＰｂ０．２％を含み、残部がＣｕである。なお、実施例３、４におけるＶ及びＴｉ量は、合金に対して各々０．１％である。

Here, Sn in Examples 1 and 6 is 99% by weight. Cu in Example 7 is 99.9% by weight. The bronze (BC3) in Examples 2 to 5 contains Sn 10%, zinc 2% and Pb 0.2% by weight, with the balance being Cu. In Examples 3 and 4, the amounts of V and Ti are each 0.1% with respect to the alloy.

  Moreover, the porosity of the bearing materials of Comparative Examples 1 to 4 having no impregnated metal has 6 to 11% as shown in FIG. 7 described later, and the hardness decreases as the porosity increases. The porosity before impregnation of a carbonaceous base material is a volume ratio, 11% in Examples 1-4 and 6% in Examples 5-7. The porosity after the impregnation is volume ratio, 1.1% in Example 1, 1.2% in Example 2, 0.6% in Example 3, 0.7% in Example 4, and Example 5 is 1.3%, Example 6 is 1.5%, and Example 7 is 0.7%. The amount of graphite of the carbonaceous substrate is 35% in Examples 1 to 7 by weight. The hardness of the bearing materials of Comparative Examples 1 to 4 having no impregnated metal varies depending on the amount of porosity, graphite, pitch, tar and the like.

  FIG. 3 shows the relationship between the Shore hardness and the coefficient of friction in a non-lubricated state in Comparative Examples 1 to 4 and Examples 1 to 7. In FIG. 3, the friction coefficient was evaluated in the gas of R410A as an example of a refrigerant that does not contain chlorine in the non-lubricated state. In FIG. 3 to FIG. 7, the triangle marks are the bearing material of the comparative example, and the circle marks are the bearing material of the embodiment. The numbers given to these marks are the numbers shown in Table 1 of the comparative examples or examples.

  It can be seen from FIG. 3 that the friction coefficient of the bearing material without lubrication tends to decrease as the Shore hardness increases in both the examples and the comparative examples. This tendency was the same when the friction was evaluated in a hydrocarbon refrigerant gas. Those using bronze (BC3) tend to have a smaller friction coefficient when the Shore hardness is 65 or higher, preferably 80 or higher.

  FIG. 4 shows the relationship between the Shore hardness and the amount of wear during no lubrication in the bearing materials of Comparative Examples 1 to 4 and Examples 1 to 7. The wear test was performed using a high-pressure atmosphere wear tester, using a carbonaceous substrate as a test piece (10 mm × 10 mm × 36 mm) as a test piece and a carburizing and quenching material of SCM415 structural steel as a movable piece, with a surface pressure of 9.8 MPa. , Sliding speed of 1.2 m / s, R410A in a refrigerant atmosphere for 10 hours, the amount of wear after the test was measured. It can be seen from FIG. 4 that the wear amount decreases as the Shore hardness of the bearing material increases. Those using bronze (BC3) show that the higher the Shore hardness is 65 or more, preferably 80 or more, the smaller the amount of wear.

  FIG. 5 shows the relationship between the Shore hardness and the friction coefficient in the lubricating oil in the bearing materials of Comparative Examples 1 to 4 and Examples 1 to 7. As is apparent from FIG. 5, Comparative Examples 2 to 4 which are not impregnated with metal have a high friction coefficient of 0.1 or more even though the Shore hardness is 65 or more. This is because the porosity of the bearing materials of Comparative Examples 1 to 4 is high as shown in FIG. 7, so that the oil is cut off in sliding in the lubricating oil, the oil film becomes thin, and mixed lubrication is preferable. Absent. In the case of using bronze (BC3), a bearing material having a Shore hardness of 65 or more, preferably 80 or more, has a small coefficient of friction. In Example 5, bronze (BC3) was used as the impregnated metal, and the friction coefficient in the lubricating oil was low.

  FIG. 6 shows the relationship between the Shore hardness and the amount of wear in the lubricating oil in the bearing materials of Comparative Examples 1 to 4 and Examples 1 to 7. FIG. 6 shows the amount of wear in a load bearing test in which the surface pressure was increased to 98 MPa at a load speed of 0.15 MPa / s at a sliding speed of 1.2 m / s during mixed lubrication of R410A refrigerant and synthetic oil. Is. A material using bronze (BC3) has a wear amount of a bearing material having a Shore hardness of 65 or more, preferably 80 or more. In Example 5, bronze (BC3) was used as the impregnated metal, and the amount of wear in the lubricating oil was the smallest. Therefore, it was found that a material having a higher Shore hardness is more suitable as a bearing material.

  FIG. 7 shows the relationship between the residual porosity and the friction coefficient in a wear test under severe conditions in lubricating oil in the bearing materials of Comparative Examples 1 to 4 and Examples 1 to 7. Synthetic oil is used as the lubricating oil, and the oil is suitable for R410A Freon refrigerant.

  The porosity was measured using a Porosimeter 2000 model manufactured by FISONS [Amco Corp.]. From the pore distribution curve collected by this method, the porosity was calculated by “cumulative pore volume” × “bulk density” × 100 (%). It can be confirmed that the smaller the porosity, the better the oil film retention and the smaller the coefficient of friction in the lubricating oil. Further, Examples 3 and 4 impregnated with bronze alloy added with V or Ti make V or Ti carbides (VC, TiC) at the time of impregnation and improve the wettability with the carbonaceous substrate. Alternatively, the porosity is lower than that in Example 1 or Example 5 in which Ti is not added, the oil film holding force during lubrication is improved, and the friction coefficient is reduced. As a result of observing the surface of the carbonaceous substrate impregnated with the alloy added with V or Ti with a scanning electron microscope, V and Ti carbides (VC, TiC) were confirmed at the interface between the carbonaceous substrate and the alloy. It was.

  FIG. 8 shows the relationship between the melting point of the impregnated metal and the coefficient of friction in the unlubricated state, which is the most severe lubricating condition. The numbers in the figure indicate the Shore hardness of the carbonaceous substrate before impregnation with the metal. Even if the Shore hardness of the carbonaceous substrate before impregnation was different, the tendency of the friction coefficient due to the difference of impregnated metal was almost the same. It has been found that Cu and Cu alloys having a melting point of 900 ° C. or higher have a friction coefficient comparable to that of low melting point metals.

  In addition, although Cu was used as a material having a high melting point, if other high melting point metals can be impregnated, wear resistance and low friction can be realized by combining with a carbonaceous substrate.

  In the present embodiment, as a process of impregnation, a method of impregnating a metal by immersing a carbonaceous substrate in molten metal and simultaneously applying pressure is adopted. In this process, lowering the melting point as much as possible is effective in improving productivity. Therefore, it is preferable to produce a bearing material by adding Sn to Cu to slightly lower the melting point. Since the strength of the impregnated metal is improved by using an alloy for the impregnated metal, it is effective for improving the hardness of the entire bearing. Furthermore, by adding an element for improving the machinability to the impregnated metal, the finished state of the friction surface of the bearing material becomes smooth and good, and it is possible to constitute a bearing portion with higher reliability.

  FIG. 9 shows the relationship between each graphite content and the non-lubricating coefficient of friction for a bearing material comprising a carbonaceous substrate containing graphite and impregnated with bronze (BC3) or Cu. No. Reference numeral 5 denotes the fifth embodiment described above, and reference numerals 5-1 to 5-4 denote additional data. As shown in FIG. 9, the coefficient of friction shows a minimum value when the graphite content is 20 to 50% by weight, particularly 20 to 40% by weight.

  FIG. 10 shows the results of a wear test of the PTFE-based winding bush of Example 8 and the carbon bearing of Example 5 in the R410A refrigerant atmosphere. The test surface of the wound bush is adjusted to a bronze exposure rate of 36%. The amount of wear after the test was measured with an atmospheric pressure of 0.5 MPa, a sliding speed of 1.2 m / s, and a test time of 2 hours. When the wear amount is 10 MPa in the low load region, the wound bush of Example 8 is less, but at a surface pressure of 20 MPa, the carbon bearing of Example 5 is less, and the carbon bearing of Example 5 having high hardness is more. It was found that the wound bushing in a high load region in a harsh environment is superior to a wound bush with low hardness and low heat resistance.

  FIG. 11 shows that the surface pressure was reduced to 98 MPa at a sliding speed of 1.2 m / s in the mixed lubrication of R410A refrigerant + synthetic oil in the PTFE-based wound bush of Example 8 and the carbon material of Example 5. The amount of wear in a load bearing test loaded at a load speed of 15 MPa / s is shown. Even in a lubricated state where oil is present, the wear amount when the surface pressure is applied to 98 MPa in the high load region is that the carbon bearing material of Example 5 having high hardness has less wear amount and excellent wear resistance. I understand.

  FIG. 12 shows a wear test in a carbon dioxide refrigerant atmosphere with a surface pressure of 9.8 MPa in the PTFE wound bush of Example 8, the polyimide wound bush of Example 9, and the carbon bearing material of Example 5. Indicates the amount of wear. The test surface of the PTFE wound bushing has a bronze exposure rate adjusted to 36%. On the other hand, bronze is not exposed on the test surface of the polyimide-based winding bush. The amount of wear is smaller in the order of the carbon bearing material of Example 5 <the PTFE winding bush of Example 8 <the polyimide winding bush of Example 9. As described above, it was found that when the surface pressure was as high as 9.8 MPa, the carbon bearing material of Example 5 was excellent in wear resistance.

  FIG. 13 shows a PTFE-based winding bush of Example 8, a polyimide-based winding bush of Example 9, and a carbon bearing material of Example 5 at a surface pressure of 9.8 MPa and during a wear test in a carbon dioxide refrigerant atmosphere. Indicates the average friction coefficient. The test surface of the PTFE wound bushing has a bronze exposure rate adjusted to 36%. On the other hand, bronze is not exposed on the test surface of the polyimide-based winding bush. Similar to the amount of wear, the average friction coefficient is lower in the order of carbon in Example 5 <PTFE winding bush in Example 8 <polyimide winding bush in Example 9. As described above, when the surface pressure was as high as 9.8 MPa, it was found that the carbon bearing material of Example 5 had low friction.

  Next, the carbon bearing with a length of 14 mm of Example 5 is used for the slewing bearing 4c of the actual compressor, the carbon bearing with a length of 21.5 mm of Example 5 is used for the crank side main bearing 6c1, and the PTFE of Example 8 is used. The test result of the refrigerant compressor using the winding bush of the system for the motor side main bearing 6c2 will be described. The test was a severe test that simulated starting and stopping of the bearing in R410A refrigerant and synthetic oil. As a result, no abnormal wear is observed on the rotary bearing side of the slewing bearing 4c and the crank side end of the crank side main bearing 6c1, and all the bearings 4c, 6c1, 6c2 are sound, and the reliability of the refrigerant compressor is improved. I was able to secure it.

  When this actual machine test was carried out in an atmosphere of carbon dioxide refrigerant and synthetic oil, no abnormal wear was observed on the rotary bearing side of the slewing bearing 4c and the crank side end of the crank side main bearing 6c1, and all the bearings 4c, 6c1 were observed. 6c2 was sound and the reliability of the refrigerant compressor could be secured.

  Furthermore, the 14 mm long carbon bearing of Example 5 is used for the slewing bearing 4c of the actual compressor, the 21.5 mm long carbon bearing of Example 5 is used for the crank side main bearing 6c1, and the polyimide of Example 9 is used. A test was conducted using the winding bush of the system for the motor-side main bearing 6c2. The test was a severe test that simulated starting and stopping of the bearing in R410A refrigerant and synthetic oil. As a result, no abnormal wear is observed on the rotary bearing side of the slewing bearing 4c and the crank side end of the crank side main bearing 6c1, and all the bearings 4c, 6c1, 6c2 are sound, and the reliability of the refrigerant compressor is improved. I was able to secure it.

  When this actual machine test was carried out in an atmosphere of carbon dioxide refrigerant and synthetic oil, no abnormal wear was observed on the rotary bearing side of the slewing bearing 4c and the crank side end of the crank side main bearing 6c1, and all the bearings 4c, 6c1 were observed. 6c2 was sound and the reliability of the refrigerant compressor could be secured.

  According to the embodiment described above, the amount of graphite contained in the carbonaceous substrate that is difficult to seize even in the boundary lubrication state is optimized so that the friction coefficient is reduced and the wear resistance is increased, and the pores of the carbonaceous substrate are optimized. In order to make it easier to form an oil film in lubricating oil, impregnate the metal, and adjust the composition and structure of the impregnated metal other than lead and antimony, and the amount of impregnation so that the friction coefficient is reduced and the wear resistance is obtained. Thus, a bearing having excellent sliding characteristics can be obtained, and the graphite in the carbonaceous substrate can be thinly cleaved by friction, whereby the friction coefficient can be reduced. And, if the graphite content is high at high loads, the carbonaceous substrate itself becomes soft and deformation resistance increases, friction increases, and at the same time wear increases, so the graphite content is 50% by weight or less, More preferably, it is 35% by weight or less. Furthermore, if the graphite content is less than 20% by weight, the carbonaceous substrate becomes hard and wears away the frictional metal material, so the graphite content is preferably 20-50%, more preferably 20-35%. By doing so, a bearing with low friction and high wear resistance can be obtained, and a highly reliable refrigerant compressor can be provided. Further, the slewing bearing 4c and the crank side main bearing 6c1 can have a highly reliable refrigerant compressor that can tolerate high load surface pressure by setting the length to 5 mm or more.

  Further, according to the present embodiment, in the refrigerant compressor exposed to unlubricated or severe sliding conditions, the carbonaceous material having a small friction coefficient and good wear resistance even in the unlubricated or severe sliding state. In order to prevent the lubricating oil from being discharged through the pores remaining in the carbonaceous base material containing graphite when used in the base material and the lubricating oil, it is difficult to form an oil film. Each of lead and antimony is 1% by weight or less, and melt impregnated with one kind of metal selected from IB, Group VIII excluding Fe and Sn, or an alloy with V or Ti added to 0.2% by weight or less. A bearing of the refrigerant compressor is formed using the bearing material, and the hardness of the bearing material is preferably 65 to 120, more preferably 80 or more, and most preferably 100 or more in terms of Shore hardness. Friction coefficient under various sliding conditions A highly reliable and long-life refrigerant compressor can be provided by keeping it small and minimizing wear. In consideration of mass productivity, workability is reduced when the Shore hardness is 90 or more. Therefore, the hardness of the bearing material is preferably 60 to 90, more preferably 80 to 90 in Shore hardness. It is possible to provide a refrigerant compressor that has wear resistance and also has productivity.

  The lead and antimony contents are preferably 0.5% or less and most preferably zero, but the use of JIS standard materials is preferred for production.

  Further, according to the present embodiment, even when lubrication is sufficiently performed in the steady operation state of the refrigerant compressor, the pores of the bearing material are controlled to be small, that is, the pores of the carbonaceous base material containing the graphite of the bearing material By setting the rate to 0.05 to 2% by volume, a lubricating oil film can be stably formed and wear can be suppressed, so that a long-life refrigerant compressor can be obtained.

  Further, according to the present embodiment, 0.2% by weight of V or Ti is added to the alloy impregnated in the pores of the carbonaceous base material used for the slewing bearing 4c and the crank side main bearing 6c1, so that The wettability is improved, the porosity is reduced, the lubricating oil film can be formed more stably, the wear can be suppressed, and a highly reliable refrigerant compressor can be obtained.

  Further, according to the present embodiment, when the melting point of the metal and the alloy impregnated in the carbonaceous base material in the slewing bearing 4c and the crank side main bearing 6c1 is set to 900 ° C. or higher, the temperature is changed when a severe sliding state continues. Even if the temperature rises, lubricity and wear resistance can be maintained and the reliability of the refrigerant compressor can be improved.

  The IB group consists of Cu, Au, and the VIII group consists of Co, Ni, Ru, Rh, Pd, Os, Ir, and Pt, with Cu, Au, Co, and Ni being preferred. Further, the alloy is preferably an alloy containing 80 to 90% copper, 5 to 11% tin and 3% or less zinc, and 1.0% or less lead, preferably 0.5% or less, by weight. These metals are difficult to form a compound with C, have high wear resistance and seizure resistance, and are easily impregnated.

  Since the carbonaceous substrate has pores, the lubricating oil flows into the pores. As a result, the oil film disappears, so that copper is impregnated with little influence on the environment and the human body. With copper alone, the impregnated part was soft, and the copper part was easily fused by friction. Therefore, alloying elements were added to strengthen and prevent fusion and further wear. By eliminating the fusion, the friction coefficient can be reduced even in the boundary lubrication state, and by using this as a bearing, a highly reliable refrigerant compressor can be obtained.

  Further, according to the present embodiment, when the melting point of the metal and the alloy impregnated in the carbonaceous base material in the slewing bearing 4c and the crank side main bearing 6c1 is set to 900 ° C. or higher, the temperature is changed when a severe sliding state continues. Even if it rises, lubricity and wear resistance can be maintained and the reliability of the refrigerant compressor can be improved.

  The present invention can be effectively applied to a compressor for an air conditioner, a compressor for a refrigerator, and a compressor for a water heater, which require seizure resistance and wear resistance.

It is a longitudinal cross-sectional view of the refrigerant compressor of one Embodiment of this invention. It is a principal part expanded sectional view of the refrigerant compressor of FIG. It is a figure which shows the relationship between the Shore hardness in the Example of a bearing material used for the refrigerant compressor of FIG. 1, and a friction coefficient in non-lubrication. It is a figure which shows the relationship between the Shore hardness in the Example and comparative example of a bearing material used for the refrigerant compressor of FIG. It is a figure which shows the relationship between the Shore hardness in the Example and comparative example of a bearing material used for the refrigerant compressor of FIG. 1, and the friction coefficient in lubricating oil. It is a figure which shows the relationship between the Shore hardness in the Example and comparative example of a bearing material used for the refrigerant compressor of FIG. 1, and the amount of wear in lubricating oil. It is a figure which shows the relationship between the porosity in the Example and comparative example of a bearing material used for the refrigerant compressor of FIG. 1, and the friction coefficient in the lubricating oil of a bearing material. It is a diagram which shows the relationship between the melting | fusing point of an Example of the bearing material used for the refrigerant compressor of FIG. 1, and a friction coefficient. It is a figure which shows the relationship between the graphite content rate of the Example of the bearing material used for the refrigerant compressor of FIG. 1, and the friction coefficient in non-lubrication. It is a figure which shows the relationship between the test surface pressure and the amount of wear of the Example of the bearing material used for the refrigerant compressor of FIG. It is a figure which shows the abrasion loss in the load resistance test in the lubricating oil of the Example of the bearing material used for the refrigerant compressor of FIG. It is a figure which shows the abrasion loss in the example of the bearing material used for the refrigerant compressor of FIG. It is a figure which shows the abrasion loss in the example of the bearing material used for the refrigerant compressor of FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Sealed container, 2 ... Compressor part, 3 ... Balance weight, 4 ... Orbiting scroll, 4a ... Base plate, 4b ... Spiral wrap, 4c ... Orbiting bearing (crank bearing), 4d ... Back keyway, 5 ... Fixed scroll, 5a ... base plate, 5b ... spiral wrap, 5d ... suction port, 5e ... discharge port, 6A ... upper frame, 6B ... lower frame, 6c ... main bearing, 6c1 ... crank side main bearing (carbon bearing) , 6c2 ... motor side main bearing (winding bush), 6d ... sub bearing, 7 ... rotating shaft, 7a ... main shaft portion, 7b ... crank portion, 7c ... oil introduction pipe, 7d ... oil passage, 8 ... Oldham coupling, 9 ... Electric motor, 9a ... stator, 9b ... rotor, 10 ... refrigerant compressor.

Claims (12)

In a sealed container, a compressor unit that compresses a refrigerant that does not contain chlorine, a rotating shaft that drives the compressor unit, a bearing that supports the rotating shaft, and an electric motor that rotates the rotating shaft are provided. ,
The rotating shaft has a main shaft portion fixed to the rotor of the electric motor, and a crank portion engaged with the compressor portion,
In the refrigerant compressor having a bearing that pivotally supports the rotating shaft, a main bearing that pivotally supports the main shaft portion, and a crank bearing that pivotally supports the crank portion,
The main bearing is composed of a crank side main bearing and a motor side main bearing adjacent to the crank side main bearing,
The crank bearing and the crank side main bearing are composed of carbon bearings in which pores of a carbonaceous substrate containing graphite are impregnated with metal,
The motor-side main bearing is constituted by a winding bush formed by winding a plate material.   2. The compressor unit according to claim 1, wherein the compressor unit is configured by meshing a fixed scroll in which a spiral wrap is erected on a base plate and an orbiting scroll in which a spiral wrap is erected on the base plate, and the crank bearing. Is installed in a boss part that protrudes on the side opposite to the orbiting scroll, the main bearing pivotally supports the rotating shaft on the compressor side from the electric motor, and the rotating shaft is stored in the sealed container. A refrigerant compressor having an oil passage so as to supply the lubricated oil to the crank bearing and the main bearing by differential pressure.   2. The wound bush according to claim 1, wherein the wound bush is formed by winding a metal plate having a self-lubricating PTFE resin or a self-lubricating polyimide resin surface layer so that the surface layer is on the inside. The refrigerant compressor characterized by being.   4. The wound bush according to claim 3, wherein the wound bush has a surface layer impregnated with a self-lubricating PTFE resin or a self-lubricating polyimide resin in a bronze porous material sintered on the metal plate. The refrigerant compressor characterized by being.   In Claim 3 or 4, the crank bearing and the crank side main bearing are one type selected from Group 1B, Group VIII excluding Fe, and Sn in the pores of the carbonaceous substrate containing 20 to 50% by weight of graphite, Alternatively, a refrigerant compressor comprising a carbon bearing impregnated with an alloy mainly containing these metals.   5. The crank bearing and the crank-side main bearing according to claim 3 or 4, wherein the crank-side main bearing is mainly made of one type selected from Group 1B, Group VIII excluding Fe and Sn, or a metal thereof, in the pores of the carbonaceous substrate containing graphite. A refrigerant compressor characterized by comprising a carbon bearing impregnated with an alloy and having a Shore hardness of 65 to 120.   7. The crank bearing and the crank side main bearing according to claim 6, wherein the pores of the carbonaceous base material containing graphite mainly include one type selected from Group 1B, Group VIII excluding Fe, and Sn, or a metal thereof. A refrigerant compressor characterized by comprising a carbon bearing impregnated with an alloy and having a porosity of 0.05 to 2% by volume.   5. The crank bearing and the crank-side main bearing according to claim 3 or 4, wherein the crank-side main bearing is mainly made of one type selected from Group 1B, Group VIII excluding Fe and Sn, or a metal thereof, in the pores of the carbonaceous substrate containing graphite. A refrigerant compressor comprising a carbon bearing impregnated with an alloy containing 0.2% by weight or less of at least one of V and Ti.   2. The refrigerant compressor according to claim 1, wherein the refrigerant is any one of R410A, carbon dioxide, and propane.   An air conditioner using the refrigerant compressor according to any one of claims 1 to 9.   A refrigerator using the refrigerant compressor according to any one of claims 1 to 9.   A water heater using the refrigerant compressor according to any one of claims 1 to 9.

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