JP6862294B2 - Scroll compressor - Google Patents

Description

The present invention relates to a scroll compressor provided with a refueling pump, and particularly handles HFC-based refrigerants, natural refrigerants such as air and carbon dioxide, and other compressible gases, and constitutes the refueling pump. Related to inner rotors, pump covers, etc. that suppress wear.

Scroll compressors are widely used in various fields as compressors for refrigerating and air-conditioning equipment. In addition, the efficiency of compressors is rapidly increasing due to energy-saving regulations to prevent global warming. On the other hand, it is also essential that the sliding portion is not fatally damaged even if the scroll compressor is operated under extremely harsh conditions. Furthermore, in recent years, in order to reduce costs, there is an urgent need to develop smaller and faster scroll compressors and slide bearings for main bearings and auxiliary bearings.

As described in Japanese Patent Application Laid-Open No. 2015-203337 (Patent Document 1), in a scroll compressor in which a main bearing and an auxiliary bearing are composed of rolling bearings, a refueling pump is used for refueling these bearings. Is provided. A part of the oil (lubricating oil) discharged from the oil supply pump is supplied to the auxiliary bearing through the oil passage formed in the rotating shaft. Most of the remaining oil is sent from the upper end of the crank portion of the rotary shaft into the swivel boss portion of the swivel scroll through the oil passage, from which the swivel bearing of the swivel scroll is lubricated and then composed of a rolling bearing. It is supplied to the main bearing. As described above, in the above-mentioned Patent Document 1, the series refueling method is used.

However, in a scroll compressor, when the main bearing and the sub bearing are composed of slide bearings, the reliability of these bearings cannot be ensured unless a sufficient amount of lubricating oil is reliably supplied to each bearing. There is a big problem. In order to solve this problem, a distributed oil supply system must be adopted in which oil is directly supplied to each bearing from the oil passage provided at the center of the rotating shaft.

Further, when the distributed refueling method is adopted, the amount of refueling from the refueling pump must be increased as compared with the case where the series refueling method is adopted, and the volume (maximum discharge volume) of the refueling pump is doubled. If the above settings are not made, the required amount of lubrication for each bearing cannot be sufficiently secured. If the volume of the refueling pump is increased in order to increase the amount of refueling, the pressure difference between the suction side pressure and the discharge side pressure of the refueling pump will increase.

The refueling pump is composed of an inner rotor, an outer rotor, a pump cover, a pump case for accommodating these, and the like, and the refueling pump is fixed to a housing fixed to a lower frame (secondary frame) with a fitting such as a bolt. ing. In addition, due to manufacturing tolerances of the parts that make up the compressor, assembly tolerances during assembly, and tilting and swinging of the rotating shaft that occur during operation, there is a gap between the inner rotor and outer rotor and the pump cover. A gap is provided in consideration of dimensional tolerances and the like.

Japanese Unexamined Patent Publication No. 2015-203337

In the above-mentioned Patent Document 1, if the gap is increased, oil leakage increases, which causes a decrease in refueling efficiency. Further, when the gap is made smaller in order to improve the refueling efficiency, the inner rotor and the outer rotor are inclined during operation and strongly come into contact with the pump cover because the gap is provided, which causes wear and lowers reliability. There are challenges.

Further, the above-mentioned Patent Document 1 also describes that the pump cover can be freely moved in the axial direction of the rotation shaft, and the pump cover is supported by a cover retainer via an elastic body.

With such a configuration, it is possible to eliminate the axial gap between the inner rotor and the outer rotor and the pump cover, so that the refueling efficiency (volumetric efficiency) can be improved. However, in this configuration, the pump cover, the inner rotor, and the outer rotor are always in contact with the pump cover regardless of the rotation speed. Therefore, if the pressure difference between the suction side pressure and the discharge side pressure of the refueling pump increases as the volume of the refueling pump increases, the pump cover, the inner rotor, and the outer rotor cause abnormal wear, which also reduces reliability. There is a challenge to invite. Further, in order to support the pump cover with the elastic body, the cover presser is required, and there is also a problem that the cost is high.

An object of the present invention is to obtain a scroll compressor capable of suppressing wear of an inner rotor and a pump cover constituting a refueling pump and improving reliability.

In order to achieve the above object, the present invention has a closed container, a main frame and a subframe attached to the closed container, an end plate and a spiral wrap erected on the end plate, and the main frame. A swivel scroll that has a fixed scroll attached to the bearing, an end plate and a spiral wrap that stands on the end plate, and is meshed with the fixed scroll to form a compression chamber, and an eccentricity that swivels the swivel scroll. A rotary shaft having a pin portion, a swivel boss portion having a swivel bearing provided on the back surface side of the end plate of the swivel scroll and into which the eccentric pin portion is inserted, and a main shaft of the rotary shaft provided on the main frame. In a scroll compressor provided with a main bearing that rotatably supports a portion and an auxiliary bearing provided in an auxiliary bearing housing attached to the subframe and rotatably supporting the subshaft portion of the rotating shaft, the sub A pump case attached to a bearing housing, a refueling pump having an inner rotor and an outer rotor provided in the pump case, and a pump case of the refueling pump with respect to the sub-bearing housing in the axial clearance and the radial direction. It is provided with a plurality of support bolts to be attached while maintaining the gap between the bearings and an elastic support member provided between the auxiliary bearing housing and the pump case so as to surround the periphery of the plurality of support bolts. It is a feature.

Another feature of the present invention is a closed container, a main frame and a subframe attached to the closed container, an end plate and a spiral wrap erected on the end plate, and attached to the main frame. A fixed scroll, a swivel scroll having an end plate and a spiral wrap erected on the end plate, and meshed with the fixed scroll to form a compression chamber, and an eccentric pin portion for swiveling the swivel scroll. A rotary shaft having a rotary shaft, a swivel boss portion having a swivel bearing provided on the back side of the end plate of the swivel scroll and into which the eccentric pin portion is inserted, and a swivel boss portion provided on the main frame to rotate the spindle portion of the rotary shaft In a scroll compressor provided with a main bearing that freely supports and an auxiliary bearing that is provided in the auxiliary bearing housing attached to the auxiliary frame and rotatably supports the auxiliary shaft portion of the rotating shaft, the auxiliary bearing housing is provided. With respect to the attached pump case, the refueling pump having the inner rotor and the outer rotor provided in the pump case, and the sub-bearing housing, the pump case of the refueling pump is provided with an axial gap and a radial gap. It is provided with a plurality of support bolts to be attached while being maintained, and an elastic support member provided in the circumferential direction between the auxiliary bearing housing and the pump case on the inner peripheral side of the plurality of support bolts. ..

According to the present invention, there is an effect that it is possible to obtain a scroll compressor capable of suppressing wear of the inner rotor and the pump cover constituting the refueling pump and improving reliability.

The vertical sectional view which shows Example 1 of the scroll compressor of this invention. An enlarged cross-sectional view of a main part in the vicinity of the refueling pump shown in FIG. FIG. 2 is an enlarged cross-sectional view of a main part near the support bolt shown in FIG. It is a figure explaining Example 2 of the scroll compressor of this invention, and is the figure corresponding to FIG. It is a figure explaining Example 3 of the scroll compressor of this invention, and is the figure corresponding to FIG. It is a figure explaining Example 4 of the scroll compressor of this invention, and is the figure corresponding to FIG. It is a top view of the refueling pump shown in FIG. It is a figure explaining Example 5 of the scroll compressor of this invention, and is the figure corresponding to FIG. It is a figure explaining Example 6 of the scroll compressor of this invention, and is the figure corresponding to FIG. A vertical cross-sectional view showing a conventional scroll compressor. The figure explaining the operating principle of a refueling pump. The graph which shows the relationship between the rotation frequency of a refueling pump and the discharge pressure ratio.

Hereinafter, specific examples of the scroll compressor of the present invention will be described with reference to the drawings. In each figure, the parts with the same reference numerals indicate the same or corresponding parts.

Example 1 of the scroll compressor of the present invention will be described with reference to FIGS. 1 to 3. FIG. 1 is a vertical cross-sectional view of the scroll compressor showing the first embodiment, FIG. 2 is an enlarged cross-sectional view of a main part near the refueling pump shown in FIG. 1, and FIG. 3 is an enlarged cross-sectional view of a main part near the support bolt shown in FIG. Is.

First, the overall structure of the scroll compressor of the first embodiment will be described with reference to FIG.
The scroll compressor 1 is configured such that a compression mechanism unit 2 and a drive unit 3 and the like are housed in a closed container 100.

The compression mechanism unit 2 is composed of a fixed scroll 110, a swivel scroll 120, a frame (main frame) 160, and the like.
The fixed scroll 110 has an end plate 110b and a spiral wrap 110a standing vertically on the end plate 110b, and a discharge port 110c is provided on the lap center portion side of the end plate 110b. Further, the outer peripheral portion of the end plate 110b is fixed to the frame 160 by a plurality of bolts 21.

The swivel scroll 120 has an end plate 120b and a spiral wrap 120a standing vertically on the end plate 120b, and a swivel boss portion 120c is formed on the back surface side of the end plate 120b, and the swivel scroll 120 is swiveled. A swivel bearing 103 is provided on the inner peripheral surface of the boss portion 120c. Reference numeral 120d is an end face (end face of the swivel boss portion) of the swivel boss portion 120c.

The fixed scroll 110 and the swivel scroll 120 are meshed with each other to form a compression chamber 130, and the volume of the compression chamber 130 is reduced by the swivel motion of the swivel scroll 120 to perform a compression operation. In this compression operation, a working fluid such as a refrigerant gas is sucked into the compression chamber 130 through the suction pipe 140 along with the swirling motion of the swirling scroll 120, and the sucked working fluid goes through a compression stroke and is described as described above. It is discharged from the discharge port 110c formed in the fixed scroll 110 into the discharge space 136 in the closed container 100.

After that, the compressed refrigerant gas is transferred to the drive unit 3 in the closed container 100 via a passage (not shown) formed on the outer peripheral surfaces of the fixed scroll 110 and the frame 160.
It flows to the side and is discharged from here to the refrigeration cycle or the like outside the closed container 100 via the discharge pipe 150. Therefore, the space inside the closed container 100 is maintained at the discharge pressure.

The drive unit 3 that swivels the swivel scroll 120 is composed of an electric motor 107 including a rotor 107a and a stator 107b, a rotating shaft 101, and the like. The swivel scroll 120 is configured to prevent rotation by an oldham joint 134, which is a main component of the rotation prevention mechanism, and to perform a swivel motion.

The Oldham joint 134 is provided in a back pressure chamber 180 formed between the swivel scroll 120 and the frame 160. Further, two sets of orthogonal keys are formed in the Oldham joint 134, one set of keys slides in a key groove formed in the frame 160, and the remaining one set of keys is the back surface of the swivel scroll 120. It is configured to slide through the keyway configured in.

The rotating shaft 101 has a main shaft portion 101a, a sub-shaft portion 101b, and an eccentric pin portion 101c, and the main shaft portion 101a is rotatably supported by a main bearing 104 provided in the frame 160, and the sub-shaft The portion 101b is rotatably supported by the auxiliary bearing 105 provided in the auxiliary bearing housing 133.

The auxiliary bearing housing 133 is attached to an auxiliary frame (lower frame) 137 fixed to the lower part of the closed container 100 by tack welding with a plurality of bolts 22. An oil reservoir 131 is formed at the bottom of the closed container 100, the main bearing 104 is on the compression mechanism 2 side of the electric motor 107, and the sub bearing 105 is on the oil reservoir 131 side. Have been placed.

The eccentric pin portion 101c of the rotating shaft 101 is inserted into the swivel bearing 103 provided in the swivel boss portion 120c of the swivel scroll 120. Therefore, the eccentric pin portion 101c of the rotating shaft 101 is movably and rotatably engaged with the swivel bearing 103 in the direction of the rotating shaft.

In this embodiment, plain bearings are used for the main bearing 104, the sub bearing 105, and the swivel bearing 103, respectively. Further, oil supply to the swivel bearing 103, the main bearing 104, and the auxiliary bearing 105 is provided in the oil passage (oil supply path) 102 formed in the rotary shaft 101 and on the lower end side of the rotary shaft 101. This is done by the refueling pump 106.

That is, a path for sucking the oil (lubricating oil) stored in the oil reservoir 131 in the lower space of the closed container 100 by the oil supply pump 106 and supplying the oil to the swivel bearing 103 via the oil passage 102. Oil is supplied to the main bearing 104 via a path for supplying oil to the auxiliary bearing 105 via a branch oil passage 102a branching from the oil passage 102 and a branch oil passage 102b branching from the oil passage 102. A route is formed.

The back pressure chamber 180 formed on the back side of the swivel scroll 120 is a space surrounded by the fixed scroll 110, the swivel scroll 120, and the frame 160. Further, the inside of the swivel boss portion 120c is a high pressure chamber 181 through which oil having a discharge pressure is substantially guided. The back pressure chamber 180 and the high pressure chamber 181 are pressure-separated by a sealing means.

The sealing means is arranged in a ring-shaped groove 161 formed in an end face portion of the frame 160 facing the end face 120d of the swivel boss portion 120c provided on the back surface of the swivel scroll 120, and in the ring-shaped groove 161. It is composed of the provided seal member 172. The swivel boss end surface 120d is a seal surface in contact with the seal member 172. Further, in order to lubricate the sliding portion such as the Oldham joint 134 arranged in the back pressure chamber 180, the sealing means is formed on the swivel boss portion end surface 120d and straddles the sealing member 172. A groove 170 having a slit shape or a round hole shape is also provided so that the high pressure chamber 181 and the back pressure chamber 180 are continuously or intermittently communicated with each other as the swivel scroll 120 swivels.

Therefore, the high-pressure oil discharged from the swivel bearing 103 and the main bearing 104 is sealed by the sealing member 172, and the outflow to the back pressure chamber 180 side is suppressed, so that the high-pressure chamber 181 is substantially discharged. It becomes a pressure space of about pressure. That is, since the oil having almost the discharge pressure in the closed container 100 is boosted by the pumping action of the refueling pump 106, the high pressure chamber is subjected to the depressurizing action when passing through the gaps such as the swivel bearing 103 and the main bearing 104. 181 is almost the discharge pressure.

Reference numeral 204 denotes a thrust bearing provided on the frame 160 and supporting the brim portion 101d of the rotating shaft 101, and 184 is for guiding the oil discharged from the swivel bearing 103 and the main bearing 104 to the oil sump portion 131. The oil drain pipe 138 is a support bolt for supporting the oil supply pump 106 on the auxiliary bearing housing 133.

Here, the configuration of the conventional scroll compressor will be described with reference to FIG. FIG. 10 is a vertical cross-sectional view showing a conventional scroll compressor, and the description of the same portion as that of the scroll compressor of the first embodiment of the present invention shown in FIG. 1 will be omitted, and different portions will be mainly described. The same or corresponding parts as those in FIG. 1 are designated by the same reference numerals.

In the conventional scroll compressor shown in FIG. 10, rolling bearings are used for the main bearing 104 and the sub bearing 105. Further, the oil discharged from the oil supply pump 106 is supplied to the swivel bearing 103 via the oil passage 102 of the rotating shaft 101. A part of the oil discharged from the swivel bearing 103 passes through the seal member 172 and is supplied to the back pressure chamber 180, and most of the remaining oil goes to the main bearing 104 composed of rolling bearings. It is a series refueling system that is supplied.
A part of the oil flowing through the oil passage 102 is supplied to the auxiliary bearing 105 composed of the rolling bearings via the branch oil passage 102a.

On the other hand, in this embodiment shown in FIG. 1, since the slide bearing is used not only for the swivel bearing 103 but also for the main bearing 104 and the sub bearing 105, a sufficient amount of oil is applied to each bearing portion 103 to 105. Bearing reliability cannot be ensured unless it is supplied reliably. Therefore, in this embodiment, as described above, the distributed oil supply system is used in which the oil from the oil passage 102 is distributed in parallel from the oil passage 102 to the bearing portions 103 to 105. In the case of this distributed refueling method, since it is necessary to increase the supply amount as compared with the series refueling method, each bearing 103 to 103 unless the volume of the refueling pump 106 is set to be more than twice as large as that of the conventional one shown in FIG. The required amount of refueling to 105 cannot be secured.

In this way, in order to reduce the cost of the scroll compressor, it is necessary to increase the volume of the refueling pump 106 in order to reduce the size and speed, and to increase the volume of the refueling pump 106 as each bearing becomes a plain bearing. It will be described with reference to FIGS. 11 and 12 that the pressure difference between the pressure and the suction pressure increases. FIG. 11 is a diagram for explaining the operating principle of the refueling pump, and FIG. 12 is a graph showing the relationship between the rotation frequency of the refueling pump and the discharge pressure ratio.

As shown in FIG. 11, as the refueling pump 106, an inscribed gear type gear pump generally called a trochoid type pump is used. As shown in FIG. 11, this trochoidal pump has an inscribed gear-shaped structure composed of an inner rotor 106a whose tooth profile is formed by a trochoidal curve and an outer rotor 106b driven by meshing with the inner rotor 106a. A hole 106aa is formed in the center of the inner rotor 106a, and the lower end portion of the rotating shaft 101 (see FIG. 1) is inserted into the hole 106aa and engaged with the inner rotor 106a. It is driven to rotate. As the inner rotor 106a rotates, the outer rotor 106b also rotates.

The number of teeth of the inner rotor 106a is Z (8 in this example), and the number of teeth of the outer rotor 106b is Z + 1 (9 in this example). Due to the number of teeth, the inner rotor 106a and the outer rotor 106b mesh with each other, so that the space formed between them gradually expands in volume as the inner rotor 106a rotates, and then gradually decreases. Oil is sucked from the suction port 106c in the process of increasing the volume, and oil is discharged from the discharge port 106d in the process of decreasing the volume and supplied to the oil passage 102 of the rotating shaft 101.

A part of the oil supplied to the oil passage 102 is supplied to the auxiliary bearing 105 from the branch oil passage 102a, and then flows out into the internal space between the auxiliary bearing housing 133 and the rotating shaft 101, and further, the auxiliary bearing housing. It passes through the axial gap formed between the 133 and the oil supply pump 106 and is discharged to the oil sump 131.

FIG. 12 shows the relationship between the refueling pump A having a reference volume and the rotation frequency of the pump and the discharge pressure ratio of the pump in the refueling pump B having a volume 2.5 times that of the refueling pump A. That is, the discharge pressure ratio when the rotation frequency of the refueling pump A is 100 Hz is set to 1, and the discharge pressure ratio at each rotation frequency of the refueling pump A is shown by a curve A. Further, the curve B shows the discharge pressure ratio at each rotation frequency in the refueling pump B having a volume 2.5 times the volume of the refueling pump A.

As shown in FIG. 12, as the rotation frequency of the refueling pump is lowered, the discharge pressure ratio is lowered. Further, the discharge pressure ratio of the refueling pump B whose volume is increased 2.5 times is 2.5 when the rotation frequency is 100 Hz, and the discharge pressure ratio decreases as the rotation frequency decreases. It can be seen that the discharge pressure ratio of the refueling pump B is increased to about 2.5 times when the rotation frequency is the same as the discharge pressure ratio of the refueling pump A.

The refueling pump A is a refueling pump used in a conventional scroll compressor that employs rolling bearings for the main bearing and the sub bearing and uses a series refueling method. The refueling pump B slides on the main bearing and the sub bearing. This is a refueling pump used in the scroll compressor according to the first embodiment, which employs bearings and uses a distributed refueling system. In the refueling pump of the first embodiment, slide bearings are used for the main bearing and the sub bearing, and a sufficient amount of oil is supplied to each slide bearing as a distributed refueling method. Therefore, the volume of the refueling pump is 2.5 times that of the conventional one. Need to be about.

Therefore, in the refueling pump of the present embodiment, the discharge pressure of the refueling pump is about 2.5 times higher than that of the refueling pump in the conventional scroll compressor, and the pressure difference between the suction side pressure and the discharge side pressure of the refueling pump is large. It turned out to increase.

At the pressure level of the conventional refueling pump, the amount of wear of the pump cover, inner rotor and outer rotor is small, but at the pressure level of the first embodiment, which increases the volume of the refueling pump to about 2.5 times that of the conventional one, the refueling pump It was found that the pressure difference between the suction side pressure and the discharge side pressure increased, and the vibration of the refueling pump increased accordingly, causing a phenomenon in which the pump cover and the inner rotor were abnormally worn.

Next, the configuration of the refueling pump unit in the first embodiment in which abnormal wear of the pump cover, inner rotor, etc. in the refueling pump can be avoided will be described with reference to FIGS. 1, 2 and 3.
As shown in FIG. 1, an auxiliary bearing 105 composed of a slide bearing is inserted and provided on the inner peripheral surface of the auxiliary bearing housing 133. A refueling pump 106 is attached to the lower end of the auxiliary bearing housing 133 by a support bolt 138.

The configuration of the refueling pump 106 will be described in detail with reference to FIGS. 2 and 3.
As the refueling pump 106 attached to the auxiliary bearing housing 133, an inscribed gear type gear pump called a trochoid type pump is used as described above with reference to FIG. The trochoidal pump is composed of an inner rotor 106a and an outer rotor 106b that is driven by meshing with the inner rotor 106a. As shown in FIG. 2, the inner rotor 106a has a hole 106aa formed in the center thereof, and the hole 106aa has a hole 106aa. The lower end of the rotating shaft 101 is inserted and engaged. When the rotation shaft 101 rotates, the inner rotor 106a is rotationally driven, and the outer rotor 106b also rotates with the rotation of the inner rotor 106a.

The number of teeth of the inner rotor 106a is Z (for example, 8), and the number of teeth of the outer rotor 106b is Z + 1 (for example, 9). The space formed between the inner rotor 106a and the outer rotor 106b decreases after the volume increases with the rotation of the inner rotor 106a, and the oil of the oil sump 131 (see FIG. 1) is sucked from the suction port 106c and discharged. Oil is discharged from 106d and supplied to the oil passage 102 of the rotating shaft 101.

The inner rotor 106a and the outer rotor 106b are housed in a pump case 106e, and are rotatably supported by the pump case 106e. The upper end surfaces of the rotors 106a and 106b are covered with a pump cover 106f fixed to the pump case through a small gap. The pump cover 106f has a function of maintaining airtightness between the suction chamber (suction port 106c) and the discharge chamber (discharge port 106d).

The pump case 106e is attached to the auxiliary bearing housing 133 by a plurality of support bolts 138 while maintaining an axial gap s1 and a radial gap s2, and the pump case 106e is attached to the shaft. It can be displaced with respect to the auxiliary bearing housing 133 within the range of the directional gap s1 and the radial gap s2. Therefore, even if the inner rotor 106a is tilted due to the swing of the rotating shaft 101, the pressure imbalance acting on the inner rotor itself, or the like, the pump case 106e is also the inner rotor 106a due to the axial gap s1 and the radial gap s2. It is configured so that it can tilt following the tilt.

That is, as shown in FIG. 3, the diameter of the through hole 106 g formed in the pump case 106e into which the support bolt 138 is inserted is set from the outer diameter of the large diameter portion (root portion) 138a of the support bolt 138. Is also increased to secure the radial gap s2. Further, by forming the axial length a of the large-diameter portion 138a of the support bolt 138 longer than the axial length b of the through hole 106g provided in the pump case 106e, the axial gap s1 Is secured.

Further, in the first embodiment, an elastic support member 190 is provided between the auxiliary bearing housing 133 and the pump case 106e so as to surround the support bolt 138 for each of the plurality of support bolts 138. Has been done. In this embodiment, the elastic support member 190 is composed of an annular resin ring 191 and an annular corrugated washer 192 so as to surround the support bolt 138, as shown in FIG.

The resin ring 191 and the corrugated washer 192 are provided in the annular concave groove 133a formed on the lower end surface of the auxiliary bearing housing 133, and the pump case 106e is passed through the resin ring 191 by the corrugated washer 192. The oil pump 106 is elastically supported by the elastic support member 190.

A part of the oil supplied from the oil supply pump 106 to the oil passage 102 is supplied to the auxiliary bearing 105 from the branch oil passage 102a, and then flows out into the internal space between the auxiliary bearing housing 133 and the rotary shaft 101. Further, the oil is discharged to the oil sump 131 through the axial gap s1 formed between the auxiliary bearing housing 133 and the oil supply pump 106.

As described above, in the present embodiment, the pump case 106e of the refueling pump 106 is attached to the auxiliary bearing housing 133 while maintaining the axial gap s1 and the radial gap s2, and the above. An elastic support member 190 composed of a resin ring 191 and a corrugated washer 192 is provided between the auxiliary bearing housing 133 and the pump case 106e of the refueling pump 106.

Therefore, as the volume and speed of the refueling pump 106 increase, the pressure difference between the suction side pressure and the discharge side pressure increases, and the inner rotor 106a tilts due to the occurrence of pressure imbalance in the circumferential direction of the rotor and the rotation shaft 101 vibrates. Even if the inclination of the inner rotor 106a is increased due to the above, the inclination of the inner rotor 106a can be absorbed by the inclination of the pump case 106e. Further, the vibration of the refueling pump 106 due to the increase in the pressure difference due to the increase in the volume of the refueling pump 106 and the vibration due to the high-speed rotation of the rotating shaft can also be absorbed by the elastic support member 190.

As a result, it is possible to suppress strong contact between the pump cover 106f constituting the refueling pump 106 and the inner rotor 106a and the outer rotor 106b, and to reduce the wear of the pump cover 106f and the inner rotor 106a. The reliability of the compressor can be improved.
Further, since the cover presser in the conventional scroll compressor as described in Patent Document 1 is not required, the scroll compressor capable of reducing the cost can be obtained.

As the material of the resin ring 191, a super engineering plastic (super engineering plastic) having a heat resistance of 150 ° C. or higher such as portetrafluoroethylene (PTFE), polyphenylene sulfide (PPS) or polyetheretherketone (PEEK) is used. Good to use.

Further, in the first embodiment, the annular groove 133a is provided on the auxiliary bearing housing 133 side, but instead, the resin ring 191 and the corrugated washer 192 are housed in the upper end surface of the pump case 106e. The concave groove 133a may be formed.

Example 2 of the scroll compressor of the present invention will be described with reference to FIG. FIG. 4 is a view for explaining the second embodiment, which corresponds to FIG. 3, and is an enlarged cross-sectional view of a main part in the vicinity of the support bolt 138. In the description of the second embodiment, the description of the same parts as those of the first embodiment described above will be omitted, and different parts will be mainly described.

In the first embodiment, the elastic support member 190 is composed of a resin ring 191 and a corrugated plate washer 192 so that the oil supply pump 106 is elastically supported by the auxiliary bearing housing 133. The elastic support member 190 is composed of an annular O-ring 193 made of nitrile rubber, and the O-ring 193 is arranged between the pump case 106e of the refueling pump 106 and the auxiliary bearing housing 133 to form the refueling pump. The 106 is elastically supported.

More specifically, also in the second embodiment, an annular recess 133a is formed on the lower end surface of the auxiliary bearing housing 133 so as to surround the periphery of the plurality of support bolts 138, and the annular recess 133a is formed. , The annular O-ring 193 is arranged. As a result, the pump case 106e is pressed downward by the O-ring 193, and the refueling pump 106 is elastically supported by the O-ring 193.

Also in this embodiment, the pump case 106e of the refueling pump 106 is attached to the auxiliary bearing housing 133 while maintaining the axial gap s1 and the radial gap s2. Other configurations are the same as those in the first embodiment.

In the second embodiment as well, as in the first embodiment, even if the inclination of the inner rotor 106a increases due to the pressure imbalance generated in the refueling pump 106 or the vibration of the rotating shaft 101, the pump case 106e can be inclined, so that the inner rotor can be inclined. It can absorb the inclination of 106a. Further, the vibration of the refueling pump 106 due to the increase in the pressure difference due to the increase in the volume of the refueling pump 106 and the vibration due to the high-speed rotation of the rotating shaft can also be absorbed by the O-ring 193.

As a result, it is possible to suppress strong contact between the pump cover 106f constituting the refueling pump 106 and the inner rotor 106a and the outer rotor 106b, and to reduce the wear of the pump cover 106f and the inner rotor 106a. The same effect as in the first embodiment can be obtained, such as improving the reliability of the compressor.

Further, according to the second embodiment, since the elastic support member 190 can be configured only by the O-ring 193, the configuration is simple and there is an effect that the elastic support member 190 can be manufactured at a lower cost than that of the first embodiment.
Although an example in which the annular groove 133a is provided on the auxiliary bearing housing 133 side has been described, instead of this, in the second embodiment as well, the recess for accommodating the O-ring 193 on the upper end surface of the pump case 106e. The groove 133a may be formed.

Example 3 of the scroll compressor of the present invention will be described with reference to FIG. FIG. 5 is a view for explaining the third embodiment, which corresponds to FIG. 3, and is an enlarged cross-sectional view of a main part in the vicinity of the support bolt 138. In the description of the third embodiment as well, the description of the same parts as those of the first embodiment described above will be omitted, and different parts will be mainly described.

In the third embodiment, the elastic support member 190 is composed of a compression coil spring 194, and the compression coil spring 194 is arranged between the pump case 106e of the refueling pump 106 and the auxiliary bearing housing 133, and the refueling pump is described. The 106 is elastically supported.

More specifically, in the third embodiment, a slightly deeper annular groove 133b is formed on the lower end surface of the auxiliary bearing housing 133 so as to surround the periphery of the plurality of support bolts 138, and the pump of the refueling pump 106 An annular concave groove 133c is also formed in a portion of the case 106e facing the concave groove 133b. Further, the compression coil spring 194 is arranged so as to straddle the concave grooves 133b and 133c. Therefore, the support bolt 138 is arranged inside the compression coil spring 194.

As a result, the pump case 106e is pressed downward by the compression coil spring 194, and the refueling pump 106 is elastically supported by the compression coil spring 194.
Also in this embodiment, the pump case 106e of the refueling pump 106 is attached to the auxiliary bearing housing 133 while maintaining the axial gap s1 and the radial gap s2. Other configurations are the same as those in Examples 1 and 2.

In the third embodiment as well, as in the first embodiment, even if the inner rotor 106a is tilted due to the pressure imbalance generated in the refueling pump 106 or the vibration of the rotating shaft 101, the pump case 106e can be tilted, so that the inner rotor can be tilted. It can absorb the inclination of 106a. Further, the vibration of the refueling pump 106 due to the increase in the pressure difference due to the increase in the volume of the refueling pump 106 and the vibration due to the high-speed rotation of the rotating shaft can also be absorbed by the compression coil spring 194.

As a result, it is possible to suppress strong contact between the pump cover 106f constituting the refueling pump 106 and the inner rotor 106a and the outer rotor 106b, and to reduce the wear of the pump cover 106f and the inner rotor 106a. The same effect as in the first embodiment can be obtained, such as improving the reliability of the compressor.
Further, also in the third embodiment, since the elastic support member 190 can be configured only by the compression coil spring 194, the configuration is simple and there is an effect that the elastic support member 190 can be manufactured at a lower cost than that of the first embodiment.

In the third embodiment, the annular recessed groove 133c is also formed on the upper end surface of the pump case 106e, but if the lower end of the compression coil spring 194 is formed on a flat surface, the recessed groove 133c is not always necessary. is not it.

Example 4 of the scroll compressor of the present invention will be described with reference to FIGS. 6 and 7. 6 is a diagram for explaining the fourth embodiment, FIG. 6 is a diagram corresponding to FIG. 2, and FIG. 7 is a plan view of the refueling pump shown in FIG. In the description of the fourth embodiment as well, the description of the same parts as those of the first embodiment described above will be omitted, and different parts will be mainly described.

In Examples 1 to 3 described above, for each of the plurality of support bolts 138, an elastic support member 190 is provided between the auxiliary bearing housing 133 and the pump case 106e so as to surround the support bolts 138. Explained. On the other hand, in the fourth embodiment, the elastic support member 190 is provided in the circumferential direction between the auxiliary bearing housing 133 on the inner peripheral side of the plurality of support bolts 138 and the pump case 106e. Is.

That is, even in the fourth embodiment, the elastic support member 190 is similar to the first embodiment in that the elastic support member 190 is composed of an annular resin ring and an annular corrugated washer. However, in this embodiment, the elastic support member is not provided so as to surround the circumference of the support bolt 138, but the inner peripheral side of the plurality of support bolts 138 is connected, that is, the circumference of the rotation shaft 101 is surrounded. As described above, between the auxiliary bearing housing 133 and the pump case 106e, a large annular elastic support member 190 in the circumferential direction, that is, an annular resin ring 191a and a corrugated washer 192a are provided.

The resin ring 191a and the corrugated washer 192a are arranged in an annular concave groove 133d formed on the lower end surface of the auxiliary bearing housing 133 so as to connect the inner peripheral sides of the plurality of support bolts. The pump case 106e is pressed downward by the corrugated washer 192a via the resin ring 191a, whereby the refueling pump 106 is elastically supported by the elastic support member 190.

Also in this embodiment, the pump case 106e of the refueling pump 106 is attached to the auxiliary bearing housing 133 while maintaining the axial gap s1 and the radial gap s2.

Further, in the fourth embodiment, the elastic support member 190, that is, the annular resin ring 191a is annularly formed between the auxiliary bearing housing 133 on the inner peripheral side of the support bolt 138 and the pump case 106e. Since the corrugated washer 192a is provided, the space inside the elastic support member 190 (inside space of the auxiliary bearing housing) and the space outside (outside space of the auxiliary bearing housing) are sealed. Therefore, the auxiliary bearing 105 (see FIG. 1) is lubricated and the discharge path of the oil discharged into the auxiliary bearing housing 133 is blocked, so that the oil cannot be discharged to the oil sump 131 (see FIG. 1).

Therefore, in the fourth embodiment, as shown in FIGS. 6 and 7, a plurality of oil discharge grooves (oil discharge paths) 106h communicating the internal space and the external space of the auxiliary bearing housing 133 are provided to provide an oil discharge path. I have secured it. Other configurations are the same as those in the first embodiment.

In the fourth embodiment as well, as in the first embodiment, even if the inner rotor 106a is tilted due to the pressure imbalance generated in the refueling pump 106 or the vibration of the rotating shaft 101, the pump case 106e can be tilted, so that the inner rotor can be tilted. It can absorb the inclination of 106a. Further, the vibration of the refueling pump 106 due to the increase in the pressure difference due to the increase in the volume of the refueling pump 106 and the vibration due to the high-speed rotation of the rotating shaft are also caused by the elastic support member 190, that is, the resin ring 191a and the corrugated washer 192a. It can also be absorbed.

As a result, it is possible to suppress strong contact between the pump cover 106f constituting the refueling pump 106 and the inner rotor 106a and the outer rotor 106b, and to reduce the wear of the pump cover 106f and the inner rotor 106a. The same effect as in the first embodiment can be obtained, such as improving the reliability of the compressor.

Further, according to the fourth embodiment, the annular elastic support member 190 is provided between the auxiliary bearing housing 133 and the pump case 106e on the inner peripheral side of the plurality of support bolts 138. The elastic support member 190 can be made into one, and there is also an effect that the number of parts can be reduced and the cost can be reduced as compared with those of Examples 1 to 3.

An example of providing the annular groove 133d on the auxiliary bearing housing 133 side has been described, but instead, the resin ring 191a and the corrugated washer 192a are housed on the upper end surface of the pump case 106e. The concave groove 133d may be formed.

Further, as the material of the resin ring 191a, the heat resistance of portetrafluoroethylene (PTFE), polyphenylene sulfide (PPS), polyetheretherketone (PEEK), or the like is 150 ° C. or higher, as in Example 1. Use super engineering plastic.

Further, in the above description of the fourth embodiment, the concave groove 133d is formed so that the inner peripheral side of the plurality of support bolts 138 is continuous in an annular shape, and the annular elastic support member 190 is arranged in the concave groove 133d. However, it is not necessarily limited to this form. For example, concave grooves are intermittently formed on the inner peripheral side of the plurality of support bolts 138 in the circumferential direction, and the concave grooves are composed of an arc-shaped or linear resin plate material, a corrugated washer, and a coil spring. Almost the same effect can be obtained even if the pump case is elastically supported by providing the elastic support member or the like.

Example 5 of the scroll compressor of the present invention will be described with reference to FIG. FIG. 8 is a diagram for explaining the fifth embodiment, and is a diagram corresponding to FIG. 2 or FIG. Further, also in the description of the fifth embodiment, the description of the same part as that of the first embodiment described above will be omitted, and the description will be focused on the different parts.

In the fifth embodiment as well, similarly to the fourth embodiment, the elastic support member 190 is provided in the circumferential direction between the auxiliary bearing housing 133 on the inner peripheral side of the plurality of support bolts 138 and the pump case 106e. It is a thing.

That is, also in the fifth embodiment, the elastic support member is not provided so as to surround the circumference of the support bolt 138, but the inner peripheral side of the plurality of support bolts 138 is connected, that is, the circumference of the rotation shaft 101 is connected. A large annular elastic support member 190 is provided between the auxiliary bearing housing 133 and the pump case 106e so as to surround the pump case 106e.

Further, in the fourth embodiment, the elastic support member 190 is composed of the resin ring 191a and the corrugated plate washer 192a so that the refueling pump 106 is elastically supported by the auxiliary bearing housing 133. However, in the fifth embodiment, the elastic support member 190 is elastically supported by the auxiliary bearing housing 133. The elastic support member 190 is composed of an annular O-ring 193a made of nitrile rubber, and the O-ring 193a is arranged between the pump case 106e of the refueling pump 106 and the auxiliary bearing housing 133. The refueling pump 106 is elastically supported.

More specifically, also in the fifth embodiment, the auxiliary bearing housing is connected to the lower end surface of the auxiliary bearing housing 133 so as to connect the inner peripheral sides of the plurality of support bolts 138, that is, to surround the rotation shaft 101. An annular elastic support member 190, that is, an annular O-ring 193a, which is large in the circumferential direction, is provided between the 133 and the pump case 106e.

The O-ring 193a is arranged in an annular concave groove 133d formed on the lower end surface of the auxiliary bearing housing 133 so as to connect the inner peripheral sides of the plurality of support bolts 138, and the pump case. The 106e is pressed downward by the O-ring 193a, whereby the refueling pump 106 is elastically supported by the elastic support member 190.

Also in this embodiment, the pump case 106e of the refueling pump 106 is attached to the auxiliary bearing housing 133 while maintaining the axial gap s1 and the radial gap s2. Other configurations are the same as those in Examples 1 and 4.

In the fifth embodiment as well, as in the first and fourth embodiments, the pump case 106e can be tilted even if the inner rotor 106a is tilted due to the pressure imbalance generated in the refueling pump 106 or the vibration of the rotating shaft 101. The inclination of the inner rotor 106a can be absorbed. Further, the vibration of the refueling pump 106 due to the increase in the pressure difference due to the increase in the volume of the refueling pump 106 and the vibration due to the high-speed rotation of the rotating shaft can also be absorbed by the O-ring 193a.

As a result, it is possible to suppress strong contact between the pump cover 106f constituting the refueling pump 106 and the inner rotor 106a and the outer rotor 106b, and to reduce the wear of the pump cover 106f and the inner rotor 106a. Therefore, the reliability of the scroll compressor can be improved, and the same effects as those of the first and fourth embodiments can be obtained.

Further, according to the fifth embodiment, since the elastic support member 190 can be configured only by the O-ring 193a, the configuration is simple and there is an effect that the elastic support member 190 can be manufactured at a lower cost than that of the fourth embodiment.
An example in which the annular groove 133d is provided on the auxiliary bearing housing 133 side has been described. Instead, in the fifth embodiment as well, the O-ring 193a is accommodated on the upper end surface of the pump case 106e. The concave groove 133d may be formed.

Example 6 of the scroll compressor of the present invention will be described with reference to FIG. FIG. 9 is a diagram illustrating the sixth embodiment and corresponds to FIG. 2 or FIG. Further, also in the description of the sixth embodiment, the description of the same part as that of the first embodiment described above will be omitted, and the description will be focused on the different parts.

In the sixth embodiment as well, similarly to the fourth and fifth embodiments, an elastic support member 190 is provided in the circumferential direction between the auxiliary bearing housing 133 on the inner peripheral side of the plurality of support bolts 138 and the pump case 106e. It is provided.

That is, also in the sixth embodiment, the auxiliary bearing housing 133 and the auxiliary bearing housing 133 are connected so as to connect the inner peripheral sides of the plurality of support bolts 138, instead of providing the elastic support members so as to surround the circumference of the support bolts 138. An annular elastic support member 190 that is large in the circumferential direction is provided between the pump case 106e and the pump case 106e.

Further, in the fourth embodiment, the elastic support member 190 is composed of the resin ring 191a and the corrugated washer 192a so that the refueling pump 106 is elastically supported by the auxiliary bearing housing 133. However, in the sixth embodiment, the elastic support member 190 is elastically supported by the auxiliary bearing housing 133. The elastic support member 190 is composed of only an annular corrugated washer 192b, and the corrugated washer 192b is arranged between the pump case 106e of the refueling pump 106 and the auxiliary bearing housing 133 to form the refueling pump. The 106 is elastically supported.

The corrugated washer 192b is arranged in an annular concave groove 133d formed on the lower end surface of the auxiliary bearing housing 133 so as to connect the inner peripheral sides of the plurality of support bolts 138, and the pump. The case 106e is pressed downward by the corrugated washer 192b, whereby the refueling pump 106 is elastically supported by the corrugated washer 192b, which is the elastic support member 190.

In the sixth embodiment, since the elastic support member 190 is composed of only the annular corrugated washer 192b, the portion of the pump case 106e in contact with the corrugated washer 192b may be worn. In order to suppress this wear, it is preferable that the end portion of the corrugated washer 192b on the pump case 106e side is formed on a flat surface.

Also in this embodiment, the pump case 106e of the refueling pump 106 is attached to the auxiliary bearing housing 133 while maintaining the axial gap s1 and the radial gap s2. Other configurations are the same as those in Examples 1 and 4.

In the sixth embodiment as well, as in the first and fourth embodiments, the pump case 106e can be tilted even if the inner rotor 106a is tilted due to the pressure imbalance generated in the refueling pump 106 or the vibration of the rotating shaft 101. The inclination of the inner rotor 106a can be absorbed. Further, the vibration of the refueling pump 106 due to the increase in the pressure difference due to the increase in the volume of the refueling pump 106 and the vibration due to the high-speed rotation of the rotating shaft can also be absorbed by the corrugated washer 192b.

As a result, it is possible to suppress strong contact between the pump cover 106f constituting the refueling pump 106 and the inner rotor 106a and the outer rotor 106b, and to reduce the wear of the pump cover 106f and the inner rotor 106a. Therefore, the reliability of the scroll compressor can be improved, and the same effects as those of the first and fourth embodiments can be obtained.

Further, according to the sixth embodiment, since the elastic support member 190 is composed of only the corrugated washer 192b, it can be manufactured at a lower cost than that of the fourth embodiment.
Instead of providing the annular groove 133d on the auxiliary bearing housing 133 side, the concave groove 133d accommodating the corrugated washer 192b may be formed on the upper end surface of the pump case 106e.

The present invention is not limited to the above-described examples, and includes various modifications. Further, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment.
Furthermore, the above-described examples have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the described configurations.

1 ... scroll compressor, 2 ... compression mechanism, 3 ... drive,
21 and 22 ... Bolts,
100 ... Sealed container, 101 ... Rotating shaft, 101a ... Main shaft, 101b ... Sub-shaft,
101c ... Eccentric pin part, 101d ... Brim part ,
102 ... Oil passage (refueling route), 102a, 102b ... Branch oil passage,
103 ... Swivel bearing, 104 ... Main bearing, 105 ... Sub bearing,
106 ... refueling pump, 106a ... inner rotor, 106aa ... hole,
106b ... Outer rotor, 106c ... Suction port, 106d ... Discharge port,
106e ... Pump case, 106f ... Pump cover, 106g ... Through hole,
106h ... Oil discharge groove (oil discharge route),
107 ... electric motor, 107a ... rotor, 107b ... stator,
110 ... Fixed scroll,
110a ... spiral wrap, 110b ... end plate, 110c ... discharge port,
120 ... swivel scroll, 120a ... spiral wrap, 120b ... end plate,
120c ... Swivel boss part, 120d ... Swivel boss end face,
130 ... compression chamber, 131 ... oil sump,
133 ... Auxiliary bearing housing 133a, 133b, 133c, 133d ... Recessed groove,
134 ... Oldham fittings,
136 ... Discharge space, 137 ... Sub-frame (lower frame),
138 ... Support bolt, 138a ... Large diameter part,
140 ... suction pipe, 150 ... discharge pipe,
160 ... frame (main frame), 161 ... ring-shaped groove,
170 ... groove, 172 ... seal member,
180 ... Back pressure chamber, 181 ... High pressure chamber, 184 ... Oil drain pipe,
190 ... Elastic support member, 191, 191a ... Resin ring,
192,192a, 192b ... Corrugated washer,
193, 193a ... O-ring, 194 ... compression coil spring,
204 ... Thrust bearing.

Claims (10)

A closed container, a main frame and a sub-frame attached to the closed container, an end plate and a fixed scroll having a spiral wrap standing on the end plate, and a fixed scroll attached to the main frame, and an end plate. A swivel scroll having a spiral wrap erected on the end plate and meshing with the fixed scroll to form a compression chamber, a rotary shaft having an eccentric pin portion for swiveling the swivel scroll, and the swivel scroll. A swivel boss portion provided on the back surface side of the end plate and having a swivel bearing into which the eccentric pin portion is inserted, and a main bearing provided on the main frame to rotatably support the spindle portion of the rotating shaft. In a scroll compressor provided in an auxiliary bearing housing attached to the auxiliary frame and provided with an auxiliary bearing that rotatably supports the auxiliary shaft portion of the rotating shaft.
A pump case attached to the auxiliary bearing housing, and a refueling pump having an inner rotor and an outer rotor provided in the pump case.
A plurality of support bolts for attaching the pump case of the refueling pump to the auxiliary bearing housing while maintaining an axial gap and a radial gap.
A scroll compressor comprising an elastic support member provided between the auxiliary bearing housing and the pump case so as to surround the periphery of the plurality of support bolts. A closed container, a main frame and a sub-frame attached to the closed container, an end plate and a fixed scroll having a spiral wrap standing on the end plate, and a fixed scroll attached to the main frame, and an end plate. A swivel scroll having a spiral wrap erected on the end plate and meshing with the fixed scroll to form a compression chamber, a rotary shaft having an eccentric pin portion for swiveling the swivel scroll, and the swivel scroll. A swivel boss portion provided on the back surface side of the end plate and having a swivel bearing into which the eccentric pin portion is inserted, and a main bearing provided on the main frame to rotatably support the spindle portion of the rotating shaft. In a scroll compressor provided in an auxiliary bearing housing attached to the auxiliary frame and provided with an auxiliary bearing that rotatably supports the auxiliary shaft portion of the rotating shaft.
A pump case attached to the auxiliary bearing housing, and a refueling pump having an inner rotor and an outer rotor provided in the pump case.
A plurality of support bolts for attaching the pump case of the refueling pump to the auxiliary bearing housing while maintaining an axial gap and a radial gap.
A scroll compressor comprising an elastic support member provided in the circumferential direction between the auxiliary bearing housing and the pump case on the inner peripheral side of the plurality of support bolts. The scroll compressor according to claim 1 or 2, wherein the elastic support member is composed of a resin ring and a corrugated washer to elastically support the refueling pump. In the scroll compressor according to claim 3, the resin ring is characterized by being composed of either portetrafluoroethylene (PTFE), polyphenylene sulfide (PPS) or boroetheretherketone (PEEK). Scroll compressor. The scroll compressor according to claim 1 or 2, wherein the elastic support member is composed of an annular O-ring made of nitrile rubber and elastically supports the refueling pump. Machine. In the scroll compressor according to claim 1, the elastic support member is composed of a compression coil spring, and the support bolt is arranged inside the compression coil spring to elastically support the refueling pump by the compression coil spring. A scroll compressor featuring. In the scroll compressor according to claim 6, the compression coil spring is inserted and arranged across a groove formed on the end face of the auxiliary bearing housing and a groove formed on the end face of the pump case at a position facing the groove. A scroll compressor characterized by being bearing. In the scroll compressor according to claim 2, the elastic support member is formed of an annular corrugated washer, and the annular corrugated washer is formed on the end face of the auxiliary bearing housing or the end face of the pump case. A scroll compressor characterized in that it is inserted and arranged in an annular groove to elastically support the refueling pump. The scroll compressor according to claim 2, wherein an oil discharge path for communicating the internal space and the external space of the auxiliary bearing housing is provided. The scroll compressor according to claim 9, wherein the oil discharge path is an oil discharge groove provided on an end surface of the pump case on the side of the auxiliary bearing housing.

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