CN109113990B

CN109113990B - Scroll compressor having a plurality of scroll members

Info

Publication number: CN109113990B
Application number: CN201810654524.0A
Authority: CN
Inventors: 柳濑裕一; 近野雅嗣; 中村聪; 太田原优; 幸野雄
Original assignee: Hitachi Johnson Controls Air Conditioning Inc
Current assignee: Hitachi Johnson Controls Air Conditioning Inc
Priority date: 2017-06-22
Filing date: 2018-06-22
Publication date: 2020-03-06
Anticipated expiration: 2038-06-22
Also published as: JP2019007382A; CN109113990A; JP6862294B2

Abstract

The invention provides a scroll compressor, which restrains abrasion of an inner rotor and a pump cover of an oil supply pump and realizes improvement of reliability of the scroll compressor. The scroll compressor is provided with a sub bearing which is provided in a sub bearing housing and rotatably supports a sub shaft portion of a rotary shaft. Further, the apparatus comprises: an oil supply pump mounted on the sub-bearing housing and having a pump housing, and an inner rotor and an outer rotor provided in the pump housing; a plurality of stay bolts that attach a pump housing of the oil supply pump to the sub-bearing housing while maintaining an axial gap and a radial gap; and an elastic support member provided between the sub-bearing housing and the pump housing so as to surround the plurality of support bolts.

Description

Scroll compressor having a plurality of scroll members

Technical Field

The present invention relates to a scroll compressor equipped with an oil feed pump, and more particularly to a scroll compressor that handles HFC refrigerants, natural refrigerants such as air and carbon dioxide, and other compressible gases, and that suppresses wear of an inner rotor, a pump cover, and the like constituting the oil feed pump.

Background

Scroll compressors are widely used in various fields as compressors for refrigerating and air-conditioning apparatuses. Further, the efficiency of the compressor is rapidly increased by energy saving restriction for preventing global warming. On the other hand, even when the scroll compressor is operated under very severe conditions, it is necessary that the sliding portion is not damaged fatally. In recent years, in order to reduce the cost, the development of a scroll compressor having a small size and a high speed and a sliding bearing for a main bearing and a sub bearing is also urgent.

As described in japanese patent application laid-open No. 2015-203337 (patent document 1), in a scroll compressor, an oil supply pump is provided for supplying oil to a main bearing and a sub-bearing which are configured by rolling bearings. The oil (lubricant oil) discharged from the oil supply pump is partially supplied to the sub-bearing through an oil passage formed in the rotary shaft. Most of the remaining oil is transported from the upper end of the crank portion of the rotating shaft into the orbiting boss portion of the orbiting scroll through the oil passage, and after lubricating the orbiting bearing of the orbiting scroll from there, is supplied to the main bearing formed of a rolling bearing. In this way, the configuration of patent document 1 uses a serial oil supply system.

However, in the scroll compressor, when the main bearing and the sub bearing are formed of rolling bearings, if a sufficient amount of lubricating oil cannot be reliably supplied to each bearing portion, there is a great problem that reliability of these bearing portions cannot be ensured. In order to solve this problem, a distributed oil supply system is required in which oil is directly supplied from an oil passage provided in the center of the rotating shaft to each bearing portion.

In the case of the distributed oil supply system, the amount of oil supplied from the oil supply pump must be increased as compared with the case of the serial oil supply system, and if the volume (maximum discharge volume) of the oil supply pump is not set to be twice or more, the necessary amount of oil cannot be supplied to each bearing portion. If the volume of the fuel feed pump is increased to increase the fuel feed amount, the pressure difference between the suction-side pressure and the discharge-side pressure of the fuel feed pump increases.

The fuel feed pump is composed of an inner rotor, an outer rotor, a pump cover, and a pump housing for housing these components, and is fixed to a housing fixed to a lower frame (sub-frame) by a fastening member such as a bolt. Further, gaps are provided between the inner rotor and the outer rotor and the pump cover in consideration of dimensional tolerances of the components due to manufacturing tolerances of the components constituting the compressor, assembly tolerances at the time of assembly, and inclination and vibration of the rotating shaft generated at the time of operation.

Documents of the prior art

Patent document 1: japanese laid-open patent publication No. 2015-203337

In patent document 1, if the clearance is increased, oil leakage increases, and the oil supply efficiency is reduced. Further, if the gap is reduced in order to improve the oil supply efficiency, the inner rotor and the outer rotor are inclined to strongly contact the pump cover during operation in order to provide the gap, and there is a problem that abrasion occurs to deteriorate reliability.

Further, patent document 1 describes that the pump cover is supported by an elastic body via a cover pressing member so as to be movable in the axial direction of the rotary shaft.

With this configuration, the axial gap between the inner rotor and the outer rotor and the pump cover can be eliminated, and therefore the oil supply efficiency (volume efficiency) can be improved. However, with such a configuration, the pump cover, the inner rotor, and the outer rotor always contact the pump cover regardless of the rotation speed. Therefore, when the pressure difference between the suction-side pressure and the discharge-side pressure of the fuel feed pump increases as the volume of the fuel feed pump increases, abnormal wear occurs in the pump cover, the inner rotor, and the outer rotor, and there is still a problem that the reliability is lowered. The cover pressing member is required to support the pump cover by the elastic body, and this is an expensive problem in terms of cost.

Disclosure of Invention

The invention aims to provide a scroll compressor which can inhibit abrasion of an inner rotor and a pump cover of an oil supply pump and improve reliability.

In order to achieve the above object, the present invention is a scroll compressor including: a closed container; a main frame and a sub-frame mounted on the closed container; a fixed scroll having an end plate and a scroll-shaped overlapping portion provided upright on the end plate, and mounted on the main frame; an orbiting scroll having an end plate and a spiral overlapping portion vertically provided on the end plate, and meshing with the fixed scroll to form a compression chamber; a rotating shaft having an eccentric pin portion for rotating the orbiting scroll; a rotary boss portion provided on a back surface side of the end plate of the orbiting scroll and having a rotary bearing into which the eccentric pin portion is inserted; a main bearing provided on the main frame and rotatably supporting a main shaft portion of the rotating shaft; and a sub-bearing provided in a sub-bearing housing attached to the sub-frame and rotatably supporting a sub-shaft portion of the rotating shaft, the sub-bearing including: an oil supply pump mounted on the auxiliary bearing housing and having a pump housing, and an inner rotor and an outer rotor provided in the pump housing; a plurality of stay bolts that attach a pump housing of the oil feed pump to the sub-bearing housing while maintaining an axial gap and a radial gap; and an elastic support member provided between the sub-bearing housing and the pump housing so as to surround the plurality of support bolts.

Another aspect of the present invention is summarized as a scroll compressor including: a closed container; a main frame and a sub-frame mounted on the closed container; a fixed scroll having an end plate and a scroll-shaped overlapping portion provided upright on the end plate, and mounted on the main frame; an orbiting scroll having an end plate and a spiral overlapping portion vertically provided on the end plate, and meshing with the fixed scroll to form a compression chamber; a rotating shaft having an eccentric pin portion for rotating the orbiting scroll; a rotary wheel hub provided on the back side of the end plate of the rotary scroll and having a rotary bearing into which the eccentric pin portion is inserted; a main bearing provided on the main frame and rotatably supporting a main shaft portion of the rotating shaft; and a sub-bearing provided in a housing of the sub-bearing attached to the sub-frame and rotatably supporting a sub-shaft portion of the rotating shaft, the sub-bearing including: an oil supply pump mounted on the auxiliary bearing housing and having a pump housing, and an inner rotor and an outer rotor provided in the pump housing; a plurality of stay bolts that attach a pump housing of the oil feed pump to the sub-bearing housing while maintaining an axial gap and a radial gap; and an elastic support member provided between the sub-bearing housing and the pump housing on an inner peripheral side of the plurality of support bolts in a circumferential direction.

The effects of the present invention are as follows.

According to the present invention, there is an effect that a scroll compressor in which abrasion of an inner rotor and a pump cover constituting a fuel feed pump is suppressed and reliability is improved can be obtained.

Drawings

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

Fig. 2 is an enlarged cross-sectional view of a main portion in the vicinity of the fuel feed pump shown in fig. 1.

Fig. 3 is an enlarged sectional view of a main portion in the vicinity of the stay bolt shown in fig. 2.

Fig. 4 is a diagram illustrating a second embodiment of the scroll compressor according to the present invention, and corresponds to fig. 3.

Fig. 5 is a view illustrating a third embodiment of the scroll compressor according to the present invention, and corresponds to fig. 3.

Fig. 6 is a diagram illustrating a fourth embodiment of the scroll compressor according to the present invention, and corresponds to fig. 2.

Fig. 7 is a plan view of the oil supply pump shown in fig. 6.

Fig. 8 is a diagram illustrating a fifth embodiment of the scroll compressor according to the present invention, and corresponds to fig. 2.

Fig. 9 is a diagram illustrating a sixth embodiment of the scroll compressor according to the present invention, and corresponds to fig. 2.

Fig. 10 is a longitudinal sectional view showing a conventional scroll compressor.

Fig. 11 is a diagram illustrating the operation principle of the fuel feed pump.

Fig. 12 is a graph showing a relationship between the rotation frequency of the fuel feed pump and the discharge pressure ratio.

In the figure: 1-scroll compressor, 2-compression mechanism section, 3-drive section, 21, 22-bolt, 100-sealed container, 101-rotating shaft, 101 a-main shaft section, 101 b-sub shaft section, 101 c-eccentric pin section, 101 d-sliding bearing, 102-oil passage (oil supply path), 102a, 102 b-branched oil passage, 103-rotary bearing, 104-main bearing, 105-sub bearing, 106-oil supply pump, 106 a-inner rotor, 106 aa-hole, 106 b-outer rotor, 106 c-suction port, 106 d-discharge port, 106 e-pump housing, 106 f-pump housing, 106 g-through hole, 106 h-oil discharge groove (oil discharge path), 107-motor, 107 a-rotor, 107 b-stator, 110-fixed scroll, 110 a-scroll overlapping section, 110 b-end plate, 110 c-discharge port, 120-rotary scroll, 120 a-scroll overlapping section, 120 b-end plate, 120 c-rotary boss portion, 120 d-rotary boss portion end face, 130-compression chamber, 131-oil reservoir portion, 133-sub bearing housing, 133a, 133b, 133c, 133 d-groove, 134-cross joint, 136-discharge space, 137-sub frame (lower frame), 138-support bolt, 138 a-large diameter portion, 140-suction pipe, 150-discharge pipe, 160-frame (main frame), 161-annular groove, 170-groove, 172-seal member, 180-back pressure chamber, 181-high pressure chamber, 184-oil discharge pipe, 190-elastic support member, 191 a-resin ring, 192a, 192 b-wave plate gasket, 193 a-O ring, 194-compression coil spring, 204-sliding bearing.

Detailed Description

Hereinafter, a scroll compressor according to an embodiment of the present invention will be described with reference to the drawings. In the drawings, the same reference numerals denote the same or equivalent parts.

[ EXAMPLES one ]

A first embodiment of a scroll compressor according to the present invention will be described with reference to fig. 1 to 3. Fig. 1 is a longitudinal sectional view showing a scroll compressor according to a first embodiment of the present invention, fig. 2 is an enlarged sectional view of a main portion in the vicinity of an oil feed pump shown in fig. 1, and fig. 3 is an enlarged sectional view of a main portion in the vicinity of a support bolt shown in fig. 2.

First, the overall structure of the scroll compressor according to the first embodiment will be described with reference to fig. 1.

The scroll compressor 1 is configured to house the compression mechanism 2, the drive unit 3, and the like in the hermetic container 100.

The compression mechanism 2 includes a fixed scroll 110, an orbiting scroll 120, a frame (main frame) 160, and the like.

The fixed scroll 110 includes an end plate 110b and a scroll-shaped overlapping portion 110a vertically erected on the end plate 110b, and a discharge port 110c is formed in a central portion of the overlapping portion of the end plate 110 b. The outer peripheral portion of the end plate 110b is fixed to the frame 160 by a plurality of bolts 21.

The orbiting scroll 120 includes an end plate 120b and a scroll-shaped overlapping portion 120a vertically erected on the end plate 120b, a swivel boss portion 120c is formed on the back surface side of the end plate 120b, and a swivel bearing 103 is provided on the inner peripheral surface of the swivel boss portion 120 c. Further, 120d is an end surface (a rotary boss end surface) of the rotary boss portion 120 c.

The fixed scroll 110 and the orbiting scroll 120 are engaged with each other to form a compression chamber 130, and the compression chamber 130 is rotated by the orbiting scroll 120 to reduce its volume and perform a compression operation. In the compression operation, working fluid such as refrigerant gas is sucked into the compression chamber 130 through the suction pipe 140 in accordance with the rotational movement of the orbiting scroll 120, and the sucked working fluid is discharged from the discharge port 110c formed in the fixed scroll 110 to the discharge space 136 in the closed casing 100 through a compression stroke.

Then, the compressed refrigerant gas flows toward the driving unit 3 in the closed casing 100 through a passage (not shown) formed in the outer peripheral surfaces of the fixed scroll 120 and the frame 160, and is discharged from there to a refrigeration cycle or the like outside the closed casing 100 through a discharge pipe 150. Therefore, the space in the closed casing 100 is maintained at the discharge pressure.

The drive unit 3 for rotating the orbiting scroll 120 includes a motor 107 including a rotor 107a and a stator 107b, a rotary shaft 101, and the like. Further, the orbiting scroll 120 performs a rotational motion by preventing self-rotation by the oldham joint 134 which is a main component of the self-rotation preventing mechanism.

The oldham joint 134 is provided in a back pressure chamber 180 formed between the orbiting scroll 120 and the frame 160. Two sets of keys orthogonal to the oldham coupling 134 are formed, one set of keys slides in key grooves formed in the frame 160, and the remaining set slides in key grooves formed on the rear surface of the orbiting scroll 120.

The rotary shaft 101 includes a main shaft 101a, an auxiliary shaft 101b, and an eccentric pin 101c, the main shaft 101a being rotatably supported by a main bearing 104 provided in the frame 160, and the auxiliary shaft 101b being rotatably supported by an auxiliary bearing 105 provided in an auxiliary bearing housing 133.

The sub-bearing housing 133 is attached to a sub-frame (lower frame) 137, which is fixed to the lower portion of the hermetic container 100 by a crease welding, by a plurality of bolts 22. Further, an oil reservoir 131 is formed in the bottom portion of the sealed container 100, the main bearing 104 is disposed on the compression mechanism 2 side of the electric motor 107, and the sub-bearing 105 is disposed on the oil reservoir 131 side.

The eccentric pin portion 101c of the rotary shaft 101 is inserted into the rotary bearing 103 provided in the rotary boss portion 120c of the orbiting scroll 120. Therefore, the eccentric pin portion 101c of the rotary shaft 101 is engaged with the rotary bearing 103 so as to be movable in the direction of the rotary shaft and rotatable.

In the present embodiment, slide bearings are used for the main bearing 104, the sub bearing 105, and the rotary bearing 103, respectively. The oil supply to the rotary bearing 103, the main bearing 104, and the sub-bearing 105 is performed through an oil passage (oil supply path) 102 formed in the rotary shaft 101 and an oil supply pump 106 provided on the lower end side of the rotary shaft 101.

That is, a path for sucking the oil (lubricant oil) stored in the oil reservoir 131 in the lower space of the closed casing 100 by the oil supply pump 106 and supplying the oil to the rotary bearing 103 through the oil passage, a path for supplying the oil to the sub-bearing 105 through the branch oil passage 102a branched from the oil passage 102, and a path for supplying the oil to the main bearing 104 through the branch oil passage 102b branched from the oil passage 102 are formed.

The back pressure chamber 180 formed on the back surface side of the orbiting scroll 120 is a space surrounded by the fixed scroll 110, the orbiting scroll 120, and the frame 160. Further, the inside of the rotary boss portion 120c is a high-pressure chamber 181 for guiding oil of a substantially discharge pressure. The back pressure chamber 180 and the high pressure chamber 181 are separated from each other by a seal mechanism.

The sealing mechanism includes an annular groove 161 which is formed as an end surface portion of the frame 160 facing an end surface 120d of the rotary boss portion 120c provided on the rear surface of the orbiting scroll 120, and a sealing member 172 which is disposed in the annular groove 161. The rotary boss end surface 120d is a seal surface that contacts the seal member 172. Further, in order to lubricate the sliding portions such as the oldham's joint 134 disposed in the back pressure chamber 180, the sealing mechanism further includes a slit-shaped or circular hole-shaped groove 170, and the groove 170 is formed in the rotary boss portion end surface 120d, and the high pressure chamber 181 and the back pressure chamber 180 are continuously or intermittently communicated with each other across the sealing member 172 or along with the rotary motion of the rotary scroll 120.

Therefore, the high-pressure oil discharged from the slewing bearing 103 and the main bearing 104 is sealed by the seal member 172, and the high-pressure chamber 181 is a pressure space of approximately the discharge pressure in order to suppress the outflow to the back-pressure chamber 180 side. That is, although the oil at the discharge pressure of the sealed container 100 is increased in pressure by the pumping action of the oil supply pump 106 and is reduced in pressure when passing through the clearance portion such as the rotary bearing 103 and the main bearing 104, the high-pressure chamber 181 is at the discharge pressure of the oil.

Reference numeral 204 denotes a slide bearing provided in the frame 160 and supporting the flange portion 101d of the

rotary shaft

101, 184 denotes an oil drain pipe for guiding oil discharged from the rotary bearing 103 and the main bearing 104 to the

oil reservoir portion

131, and 138 denotes a support bolt for supporting the oil supply pump 106 to the sub-bearing housing 133.

Here, the structure of a conventional scroll compressor will be described with reference to fig. 10. Fig. 10 is a longitudinal sectional view showing a conventional scroll compressor, and the same portions as those of the scroll compressor according to the first embodiment of the present invention shown in fig. 1 are omitted from description, and the different portions will be mainly described. In addition, the same or corresponding portions as those in fig. 1 are denoted by the same reference numerals.

In the conventional scroll compressor shown in fig. 10, rolling bearings are used as the main bearing 104 and the sub bearing 105. The oil discharged from the oil supply pump 106 is supplied to the rotary bearing 103 through the oil passage 102 of the rotary shaft 101. Further, a part of the oil discharged from the slewing bearing 103 is supplied to the back pressure chamber 180 through the seal member 172, and most of the remaining oil is supplied to the main bearing 104 formed of a rolling bearing in a tandem oil supply system.

Further, a part of the oil flowing through the oil passage 102 through the branch oil passage 102a is supplied to the sub-bearing 105 formed of a rolling bearing.

In contrast, in the present embodiment shown in fig. 1, since a sliding bearing is used not only for the rotary bearing 103 but also for the main bearing 104 and the sub-bearing 105, bearing reliability cannot be ensured unless a sufficient amount of oil is reliably supplied to each of the bearings 103 to 105. Therefore, as described in the present embodiment, the oil is distributed from the oil passage 102 to the bearings 103 to 105 in parallel. In the case of this distributed oil supply method, the supply amount needs to be increased compared to the serial oil supply method, and therefore, if the volume of the oil supply pump 106 is not set to be twice or more as large as that of the conventional oil supply pump shown in fig. 10, the necessary amount of oil supply to the bearings 103 to 105 cannot be secured.

As described above, with reference to fig. 11 and 12, a case will be described in which the volume of the oil feed pump 106 needs to be increased in association with the reduction in size and speed of the scroll compressor for the purpose of cost reduction, and the increase in the pressure difference between the discharge pressure and the suction pressure of the oil feed pump 106 is accompanied by the increase in the sliding bearing of each bearing. Fig. 11 is a diagram illustrating the operation principle of the fuel feed pump, and fig. 12 is a graph illustrating the relationship between the rotational frequency of the fuel feed pump and the discharge pressure ratio.

As shown in fig. 11, an internal gear pump, which is generally called a pendulum pump, is used as the oil feed pump 106. As shown in fig. 11, the trochoid pump has a tooth profile in the form of an internal gear including an inner rotor 106a formed by a trochoid curve and an outer rotor 106b meshed with and driven by the inner rotor. The inner rotor 106a has a hole 106aa formed in the center thereof, and engages with a lower end of the rotating shaft 101 (see fig. 1) inserted into the hole 106aa, and when the rotating shaft 101 rotates, the inner rotor 106a is also 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). In the relationship of the number of teeth, the inner rotor 106a and the outer rotor 106b mesh with each other, and the volume of the space formed therebetween gradually increases and then gradually decreases together with the rotation of the inner rotor 106 a. During the volume expansion, oil is sucked from suction port 106c, and during the volume reduction, oil is discharged from discharge port 106d and supplied to oil passage 102 of rotary shaft 101.

A part of the oil supplied to the oil passage 102 is supplied from the branch oil passage 102a to the sub-bearing 105, and then flows out to an inner space between the sub-bearing housing 133 and the rotary shaft 101, and is discharged to the oil reservoir 131 through an axial gap formed between the sub-bearing housing 133 and the oil supply pump 106.

Fig. 12 shows a relationship between a pump rotational frequency and a pump discharge pressure ratio of the fuel feed pump a having a reference capacity and the fuel feed pump B having a capacity 2.5 times as large as the capacity of the fuel feed pump a. That is, the discharge pressure ratio when the rotational frequency of the fuel feed pump a is 100Hz is set to 1, and the discharge pressure ratio of each rotational frequency of the fuel feed pump a is shown by a curve a. Curve B represents the discharge pressure ratio of the fuel feed pump B at each rotational frequency, which has a capacity 2.5 times the capacity of the fuel feed pump a.

As shown in fig. 12, as the rotation frequency of the supply pump is decreased, the discharge pressure ratio is decreased. In addition, although the discharge pressure ratio of the fuel feed pump B in which the capacity is increased by 2.5 times is 2.5 at the rotation frequency of 100Hz, and the discharge pressure ratio decreases as the rotation frequency decreases, it can be seen that the discharge pressure ratio of the fuel feed pump B increases by about 2.5 times if the discharge pressure ratio of the fuel feed pump a is the same rotation frequency.

The oil supply pump a is an oil supply pump for the existing scroll compressor in which the main bearing and the sub bearing adopt rolling bearings and the oil supply pump B is an oil supply pump for the scroll compressor in the first embodiment in which the main bearing and the sub bearing adopt sliding bearings and the oil supply pump B distributes the oil supply method. In the fuel feed pump according to the first embodiment, the main bearing and the sub bearing are sliding bearings, and in order to supply a sufficient amount of oil to each sliding bearing as the distributed oil supply method, the volume of the fuel feed pump needs to be about 2.5 times that of the conventional fuel feed pump.

Therefore, in the fuel feed pump of the present embodiment, the discharge pressure of the fuel feed pump becomes higher by about 2.5 times as compared with the fuel feed pump of the conventional scroll compressor, and the pressure difference between the suction-side pressure and the discharge-side pressure of the fuel feed pump increases.

However, if the volume of the fuel feed pump is set to the pressure level of the first embodiment, which is about 2.5 times the volume of the fuel feed pump, the pressure difference between the suction-side pressure and the discharge-side pressure of the fuel feed pump increases, and accordingly, the vibration of the fuel feed pump increases, and in particular, abnormal wear of the pump cover and the inner rotor occurs.

Next, the structure of the fuel pump unit according to the present embodiment, which can avoid abnormal wear of the pump cover, the inner rotor, and the like of the fuel pump, will be described with reference to fig. 1, 2, and 3.

As shown in fig. 1, the sub-bearing 105 formed of a slide bearing is inserted into the inner peripheral surface of the sub-bearing housing 133. Further, the oil supply pump 106 is attached to a lower end portion of the sub-bearing housing 133 via a support bolt 138.

The structure of the oil feed pump 106 will be described in detail with reference to fig. 2 and 3.

As described with reference to fig. 11, the oil feed pump 106 mounted on the sub-bearing housing 133 uses an internal gear type gear pump called a trochoid pump. The trochanter pump is composed of an inner rotor 106a and an outer rotor 106b that is engaged with and driven by the inner rotor 106a, and the inner rotor 106a has a hole 106aa formed in the center thereof as shown in fig. 2, and the lower end of the rotary shaft 101 is inserted into the hole 106aa and engaged therewith. When the rotary shaft 101 rotates, the inner rotor 106a is rotationally driven, and the outer rotor 106b also rotates with the rotation of the inner rotor 106 a.

The number of teeth of the inner rotor 106a is Z (e.g., 8), and the number of teeth of the outer rotor 106b is Z +1 (e.g., 9). The volume of the space formed between the inner rotor 106a and the outer rotor 106b is increased and decreased together with the rotation of the inner rotor 106a, and the oil in the oil reservoir 131 (see fig. 1) is sucked from the suction port 106c, and the oil is discharged from the discharge port 106d and supplied to the oil passage 102 of the rotary shaft 101.

The inner rotor 106a and the outer rotor 106b are housed in a pump housing 106 e. The pump casing 106e is rotatably supported. The upper end surface sides of the

rotors

106a and 106b are covered with a pump cover 106f fixed to the pump housing with a small gap therebetween. The pump cover 106f has a function of maintaining airtightness between the suction chamber (suction port 106c) and the discharge chamber (discharge port 106 d).

The pump housing 106e is attached to the sub-bearing housing 133 by a plurality of stay bolts 138 while maintaining the axial gap s1 and the radial gap s2, and the pump housing 106e is displaceable relative to the sub-bearing housing 133 within the range of the axial gap s1 and the radial gap s 2. Therefore, even if the inner rotor 106a tilts due to vibration of the rotary shaft 101, imbalance of pressure acting on the inner rotor itself, or the like, the pump housing 106e can tilt following the tilt of the inner rotor 106a by the axial gap s1 and the radial gap s 2.

That is, as shown in fig. 3, the through hole 106g formed in the pump housing 106e into which the stay bolt 138 is inserted is made larger in diameter than the outer diameter of the large-diameter portion (root portion) 138a of the stay bolt 138, and the radial gap s2 is secured. Further, the axial length a of the large diameter portion 138a of the stay bolt 138 is formed longer than the axial length b of the through hole 106g provided in the pump housing 106e, thereby securing the axial gap s 1.

In the first embodiment, an elastic support member 190 is provided between the sub-bearing housing 133 and the pump housing 106e so as to surround the support bolt 138 with respect to each of the plurality of support bolts 138. In the present embodiment, as shown in fig. 3, the elastic support member 190 is composed of an annular resin ring 191 and an annular corrugated plate washer 192 so as to surround the support bolt 138.

The resin ring 191 and the wave plate gasket 192 are provided in an annular recess 133a formed in a lower end surface of the sub-bearing housing 133, and the oil feed pump 106 is elastically supported by the elastic support member 190 by the pump housing 106e being pressed downward by the wave plate gasket 192 through the resin ring 191.

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

As described above, in the present embodiment, the pump housing 106e of the oil supply pump 106 is attached to the sub-bearing housing 133 while maintaining the axial gap s1 and the radial gap s2, and the elastic support member 190 including the resin ring 191 and the wave plate gasket 192 is provided between the sub-bearing housing 133 and the pump housing 106e of the oil supply pump 106.

Therefore, even if the pressure difference between the suction-side pressure and the discharge-side pressure increases with an increase in the volume and a high speed of the fuel feed pump 106, and the inclination of the inner rotor 106a due to the pressure imbalance in the circumferential direction of the rotor and the inclination of the inner rotor 106a due to the vibration of the rotary shaft 101 increase, the inclination of the pump housing 106e absorbs the inclination of the inner rotor 106 a. Further, the vibration of the fuel feed pump 106 caused by the increase in the pressure difference accompanying the increase in the capacity of the fuel feed pump 106 and the vibration caused by the high-speed rotation of the rotary shaft can be absorbed by the elastic support member 190.

This can suppress strong contact between the pump cover 106f, the inner rotor 106a, and the outer rotor 106b constituting the oil feed pump 106, and can reduce wear of the pump cover 106f, the inner rotor 106a, and the like, thereby improving the reliability of the scroll compressor.

Further, since the cover retainer of the conventional scroll compressor described in patent document 1 is not required, a scroll compressor with a reduced cost can be obtained.

As a material of the resin ring 191, super engineering plastic having heat resistance of 150 ℃ or higher, such as Polytetrafluoroethylene (PTFE), polyphenylene sulfide (PPS), or polyether ether ketone (PEEK), can be used.

In addition, in the first embodiment, the annular recess 133a is provided on the side of the sub-bearing housing 133, but instead, the recess 133a for accommodating the resin ring 191 and the wave plate gasket 192 may be formed on the upper end surface of the pump housing 106 e.

[ example two ]

A second embodiment of the scroll compressor according to the present invention will be described with reference to fig. 4. Fig. 4 is a view for explaining a second embodiment, which corresponds to fig. 3, and is an enlarged sectional view of a main portion in the vicinity of the stay bolt 138. In the description of the second embodiment, the same portions as those of the first embodiment are not described, and the different portions will be mainly described.

In the first embodiment, the elastic support member 190 is formed of the resin ring 191 and the wave plate gasket 192, and the oil feed pump 106 is elastically supported by the sub-bearing housing 133, but in the second embodiment, the elastic support member 190 is formed of an annular O-ring 193 made of nitrile rubber, and the O-ring 193 is disposed between the pump housing 106a of the oil feed pump 106 and the sub-bearing housing 133, and elastically supports the oil feed pump 106.

Specifically, in the second embodiment, the annular concave groove 133a is formed on the lower end surface of the sub-bearing housing 133 so as to surround the plurality of stay bolts 138, and the annular O-ring 193 is disposed in the annular concave groove 133 a. Thereby, the pump housing 106e is pressed downward by the O-ring 193, and the oil supply pump 106 is elastically supported by the O-ring 193.

In the present embodiment, the pump housing 106e of the oil feed pump 106 is attached to the sub-bearing housing 133 while maintaining the axial gap s1 and the radial gap s 2. The other structure is the same as the first embodiment.

In the second embodiment, as in the first embodiment, even if the inclination of the inner rotor 106a increases due to pressure imbalance or vibration of the rotary shaft 101 generated in the fuel feed pump 106, the pump housing 106e can be inclined, and the inclination of the inner rotor 106a can be absorbed. Further, the O-ring 193 can absorb vibration of the fuel feed pump 106 caused by an increase in the pressure difference accompanying an increase in the capacity of the fuel feed pump 106 and vibration caused by high-speed rotation of the rotary shaft.

This can suppress strong contact between the pump cover 106f, the inner rotor 106a, and the outer rotor 106b constituting the oil feed pump 106, reduce wear of the pump cover 106f, the inner rotor 106a, and the like, and improve reliability of the scroll compressor, and the like, thereby obtaining the same effects as those of the first embodiment.

In addition, according to the second embodiment, since the elastic support member 190 can be constituted only by the O-ring 193, there is an effect that the structure is simple and the manufacturing can be made cheaper than the first embodiment.

Further, although the example in which the annular recess 133a is provided on the sub-bearing housing 133 side has been described, the recess 133a for accommodating the O-ring 193 may be formed on the upper end surface of the pump housing 106e instead in the second embodiment.

[ EXAMPLE III ]

A third embodiment of the scroll compressor according to the present invention will be described with reference to fig. 5. Fig. 5 is a view for explaining the third embodiment, which corresponds to fig. 3, and is an enlarged sectional view of a main portion in the vicinity of the stay bolt 138. In the description of the third embodiment, the same portions as those of the first embodiment described above are omitted, and the description will be given centering on different portions.

In the third embodiment, the elastic support member 190 is constituted by a compression coil spring 194, and the compression coil spring 194 is disposed between the pump housing 106e of the oil feed pump 106 and the sub-bearing housing 133, thereby elastically supporting the oil feed pump 106.

Specifically, in the third embodiment, a slightly deep annular recess 133b is formed on the lower end surface of the sub-bearing housing 133 so as to surround the periphery of each of the plurality of stay bolts 138, and an annular recess 133c is also formed in a portion of the pump housing 106e of the fuel feed pump 106 that faces the recess 133 b. Further, the compression coil spring 194 is disposed so as to straddle the

concave grooves

133b and 133 c. Therefore, the stay bolt 138 is disposed inside the compression coil spring 194.

Thereby, the pump housing 106e is pressed downward by the compression coil spring 194, and the oil feed pump 106 is elastically supported by the compression coil spring 194.

In the present embodiment, the pump housing 106e of the oil feed pump 106 is attached to the sub-bearing housing 133 while maintaining the axial gap s1 and the radial gap s 2. The other structures are the same as those of the first and second embodiments.

In the third embodiment, as in the first embodiment, even if the inclination of the inner rotor 106a increases due to pressure imbalance or vibration of the rotary shaft 101 generated in the fuel feed pump 106, the pump housing 106e can be inclined, and the inclination of the inner rotor 106a can be absorbed. Further, the vibration of the fuel feed pump 106 caused by the increase in the pressure difference accompanying the increase in the capacity of the fuel feed pump 106 and the vibration caused by the high-speed rotation of the rotary shaft can be absorbed by the compression coil spring 194.

This can suppress strong contact between the pump cover 106f, the inner rotor 106a, and the outer rotor 106b constituting the oil feed pump 106, reduce wear of the pump cover 106f, the inner rotor 106a, and the like, improve reliability of the scroll compressor, and the like, and can obtain the same effects as those of the first embodiment.

In addition, in the third embodiment, since the elastic support member 190 can be constituted only by the compression coil spring 194, there is an effect that the structure is simple and the manufacturing can be made cheaper than the first embodiment.

In the third embodiment, the annular concave groove 133c is also formed in the upper end surface of the pump housing 106e, but the concave groove 133c is not necessarily required as long as the lower end of the compression coil spring 194 is formed as a flat surface.

[ EXAMPLE IV ]

A fourth embodiment of the scroll compressor according to the present invention will be described with reference to fig. 6 and 7. Fig. 6 is a view illustrating a fourth embodiment of the present invention, which corresponds to fig. 2, and fig. 7 is a plan view of the fuel feed pump shown in fig. 6. In the description of the fourth embodiment, the same portions as those of the first embodiment are not described, and the different portions will be mainly described.

In the first to third embodiments, the description has been given of an example in which the elastic support member 190 is provided between the sub-bearing housing 133 and the pump housing 106e so as to surround the support bolt 138 with respect to each of the plurality of support bolts 138. In contrast, in the fourth embodiment, an elastic support member 190 is provided in the circumferential direction between the sub-bearing housing 133 and the pump housing 106e on the inner circumferential side of the plurality of support bolts 138.

That is, in the fourth embodiment, the elastic support member 190 is configured by an annular resin ring or an annular corrugated plate gasket, which is similar to the first embodiment. However, in the present embodiment, an elastic support member is not provided so as to surround the support bolt 138, but an annular elastic support member 190 having a large size in the circumferential direction, that is, an annular resin ring 191a and a corrugated plate gasket 192a are provided between the sub-bearing housing 133 and the pump housing 106e so as to connect the inner circumferential sides of the plurality of support bolts 138, that is, so as to surround the periphery of the rotary shaft 101.

The resin ring 101a and the wave plate gasket 192a are disposed in an annular recess 133d formed in a lower end surface of the sub-bearing housing 133 so as to connect inner circumferential sides of the plurality of support bolts, and the pump housing 106e is pressed downward by the wave plate gasket 192a via the resin ring 191a, thereby elastically supporting the oil feed pump 106 by the elastic support member 190.

In the present embodiment, the pump housing 106e of the oil feed pump 106 is attached to the sub-bearing housing 133 while maintaining the axial gap s1 and the radial gap s 2.

In the fourth embodiment, the elastic support member 190, that is, the annular resin ring 191a and the wave plate gasket 192a are provided annularly between the sub-bearing housing 133 and the pump housing 106e on the inner peripheral side of the support bolt 138, so that the space inside the elastic support member 190 (the inner space of the sub-bearing housing) and the space outside the elastic support member 190 (the outer space of the sub-bearing housing) are sealed. Therefore, the discharge path of the oil that lubricates the sub-bearing 105 (see fig. 1) and is discharged into the sub-bearing housing 133 is blocked, and the oil cannot be discharged to the oil reservoir 131 (see fig. 1) side.

Therefore, in the fourth embodiment, as shown in fig. 6 and 7, a plurality of oil discharge grooves (oil discharge paths) 106h communicating the internal space and the external space of the sub-bearing housing 133 are provided to secure the oil discharge paths. The other structure is the same as the first embodiment.

In the fourth embodiment, similarly to the first embodiment, even if the inclination of the inner rotor 106a increases due to pressure imbalance or vibration of the rotary shaft 101 generated in the fuel feed pump 106, the pump housing 106e can be inclined, and the inclination of the inner rotor 106a can be absorbed. Further, the vibration of the fuel feed pump 106 due to the increase in the pressure difference accompanying the increase in the capacity of the fuel feed pump 106 and the vibration due to the high-speed rotation of the rotating shaft can be absorbed by the elastic support member 190, i.e., the resin ring 191a and the wave plate gasket 192 a.

Further, according to the fourth embodiment, since the annular elastic support member 190 is provided between the sub-bearing housing 133 and the pump housing 106e on the inner peripheral side of the plurality of support bolts 138, the number of components can be reduced and the cost can be reduced compared to the first to third embodiments by using one elastic support member 190.

Further, although the example in which the annular recess 133d is provided on the side of the sub-bearing housing 133 has been described, the recess 133d for accommodating the resin ring 191a and the wave plate gasket 192a may be formed instead in the upper end surface of the pump housing 106 e.

As the material of the resin ring 191a, super engineering plastics having heat resistance of 150 ℃ or higher, such as Polytetrafluoroethylene (PTFE), polyphenylene sulfide (PPS), or polyether ether ketone (PEEK), may be used as in the first embodiment.

In the description of the fourth embodiment, the recessed groove 133d is formed so that the inner peripheral sides of the plurality of stay bolts 138 are annularly continuous, and the annular elastic support member 190 is disposed in the recessed groove 133d, but the present invention is not limited to this embodiment. For example, substantially the same effect can be obtained even in a configuration in which a concave groove is formed intermittently in the circumferential direction on the inner peripheral side of the plurality of support bolts 138, and an elastic support member made of an arc-shaped or linear resin plate material, a wave plate washer, a coil spring, or the like is provided in the concave groove to elastically support the pump housing.

[ EXAMPLE V ]

A fifth embodiment of the scroll compressor according to the present invention will be described with reference to fig. 8. Fig. 8 is a diagram illustrating a fifth embodiment, and corresponds to fig. 2 or 6. In the description of the fifth embodiment, the same portions as those of the first embodiment are not described, and different portions will be mainly described.

In the fifth embodiment, as in the fourth embodiment, an elastic support member 190 is provided in the circumferential direction between the sub-bearing housing 133 and the pump housing 106e on the inner circumferential side of the plurality of support bolts 138.

That is, in the fifth embodiment, the elastic support member 190 is not provided so as to surround the support bolt 138, but a large annular elastic support member 190 is provided in the circumferential direction between the sub-bearing housing 133 and the pump housing 106e so as to connect the inner circumferential sides of the plurality of support bolts 138, that is, so as to surround the periphery of the rotary shaft 101.

In addition, in the fourth embodiment, the elastic support member 190 is constituted by the resin ring 191a and the wave plate gasket 192a, and the fuel feed pump 106 is elastically supported by the sub-bearing housing 133, but in the fifth embodiment, the elastic support member 190 is constituted by the annular O ring 193a made of nitrile rubber, and the O ring 193a is disposed between the pump housing 106e of the fuel feed pump 106 and the sub-bearing housing 133, and the fuel feed pump 106 is elastically supported.

Specifically, in the fifth embodiment, an annular elastic support member 190, i.e., an annular O-ring 193a, which is large in the circumferential direction, is provided between the sub-bearing housing 133 and the pump housing 106e so as to connect the inner peripheral sides of the plurality of support bolts 138, i.e., so as to surround the periphery of the rotary shaft 101, on the lower end surface of the sub-bearing housing 133.

The O-ring 193a is disposed in an annular recess 133d formed in a lower end surface of the sub-bearing housing 133 so as to connect inner circumferential sides of the plurality of support bolts 138, and the pump housing 106e is pressed downward by the O-ring 193a, whereby the oil feed pump 106 is elastically supported by the elastic support member 190.

In the present embodiment, the pump housing 106e of the oil feed pump 106 is also attached to the sub-bearing housing 133 while maintaining the axial gap s1 and the radial gap s 2. The other structures are the same as those of the first and fourth embodiments.

In the fifth embodiment, as in the first and fourth embodiments, even if the inclination of the inner rotor 106a increases due to pressure imbalance generated in the fuel feed pump 106 and vibration of the rotary shaft 101, the pump housing 106e can be inclined, and the inclination of the inner rotor 106a can be absorbed. Further, the O-ring 193a absorbs vibration of the fuel feed pump 106 caused by an increase in the pressure difference accompanying an increase in the capacity of the fuel feed pump 106 and vibration caused by high-speed rotation of the rotary shaft.

Accordingly, strong contact of the pump cover 106f, the inner rotor 106a, and the outer rotor 106b constituting the oil feed pump 106 can be suppressed, and abrasion of the pump cover 106f, the inner rotor 106a, and the like can be reduced, whereby 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 constituted only by the O-ring 193a, there is also an effect that the structure is simple and the manufacturing can be made cheaper than the fourth embodiment.

Further, although the example in which the annular recess 133d is provided on the side of the sub-bearing housing 133 has been described, the recess 133d for accommodating the O-ring 193a may be formed instead of the annular recess 133d on the upper end surface of the pump housing 106e in the fifth embodiment.

[ EXAMPLE six ]

A sixth embodiment of the scroll compressor according to the present invention will be described with reference to fig. 9. Fig. 9 is a diagram for explaining the sixth embodiment, and corresponds to fig. 2 or 6. In the description of the sixth embodiment, the same portions as those of the first embodiment are not described, and the different portions will be mainly described.

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

That is, in the sixth embodiment, an elastic support member is not provided so as to surround the support bolt 138, but an annular elastic support member having a large size in the circumferential direction is provided between the sub-bearing housing 133 and the pump housing 106e so as to connect the inner circumferential sides of the plurality of support bolts 138.

In addition, in the fourth embodiment, the elastic support member 190 is constituted by the resin ring 191a and the wave plate gasket 192a, and the oil feed pump 106 is elastically supported by the sub-bearing housing 133, but in the sixth embodiment, the elastic support member 190 is constituted by only the annular wave plate gasket 192b, and the wave plate gasket 192b is disposed between the pump housing 106e of the oil feed pump 106 and the sub-bearing housing 133, and the oil feed pump 106 is elastically supported.

The wave plate gasket 192b is disposed in an annular recess 133d formed in a lower end surface of the sub-bearing housing 133 so as to connect inner circumferential sides of the plurality of support bolts 138, and the pump housing 106e is pressed downward by the wave plate gasket 192b, whereby the oil feed pump 106 is elastically supported by the wave plate gasket 192b serving as the elastic support member 190.

In the sixth embodiment, since the elastic support member 190 is constituted only by the annular wave plate gasket 192b, there is a possibility that a portion of the pump casing 106e that is in contact with the wave plate gasket 192b is worn. In order to suppress this wear, the end of the wave plate gasket 192b on the side of the pump casing 106e may be formed as a flat surface.

In the present embodiment, the pump housing 106e of the oil feed pump 106 is attached to the sub-bearing housing 133 while maintaining the axial gap s1 and the radial gap s 2. The other structures are the same as those of the first and fourth embodiments.

In the sixth embodiment, as in the first and fourth embodiments, even if the inclination of the inner rotor 106a increases due to pressure imbalance generated in the fuel feed pump 106 and vibration of the rotary shaft 101, the pump housing 106e can be inclined, and the inclination of the inner rotor 106a can be absorbed. Further, the vibration of the fuel feed pump 106 due to the increase in the pressure difference accompanying the increase in the capacity of the fuel feed pump 106 and the vibration due to the high-speed rotation of the rotating shaft can be absorbed by the wave plate gasket 192 b.

Further, according to the sixth embodiment, since the elastic support member 190 is constituted only by the wave plate spacer 192b, it can be manufactured more inexpensively than the fourth embodiment.

Instead of providing the annular recess 133d on the sub-bearing housing 133 side, the recess 133d for accommodating the wave plate gasket 192b may be formed on the upper end surface of the pump housing 106 a.

The present invention is not limited to the above-described embodiments, and includes various modifications. Further, a part of the structure of one embodiment may be replaced with the structure of another embodiment, and the structure of another embodiment may be added to the structure of one embodiment.

The above-described embodiments are described in detail to explain the present invention easily and clearly, and are not limited to having all the structures described.

Claims

1. A scroll compressor is provided with: a closed container; a main frame and a sub-frame mounted on the closed container; a fixed scroll having an end plate and a scroll-shaped overlapping portion provided upright on the end plate, and mounted on the main frame; an orbiting scroll having an end plate and a spiral overlapping portion vertically provided on the end plate, and meshing with the fixed scroll to form a compression chamber; a rotating shaft which rotates the rotating scroll and has an eccentric pin portion; a rotary boss portion provided on a back surface side of the end plate of the orbiting scroll and having a rotary bearing into which the eccentric pin portion is inserted; a main bearing provided in the main frame and rotatably supporting a main shaft portion of the rotating shaft; and a sub-bearing provided in a sub-bearing housing attached to the sub-frame and rotatably supporting a sub-shaft portion of the rotary shaft, the scroll compressor being characterized in that,

the disclosed device is provided with:

an oil supply pump mounted on the sub-bearing housing and having a pump housing, and an inner rotor and an outer rotor provided in the pump housing;

a plurality of stay bolts that are attached to the pump housing of the oil feed pump while maintaining an axial gap and a radial gap with respect to the sub-bearing housing; and

and an elastic support member provided between the sub-bearing housing and the pump housing so as to surround the plurality of support bolts.

2. The scroll compressor of claim 1,

the elastic support member is formed of a compression coil spring, the support bolt is disposed inside the compression coil spring, and the oil feed pump is elastically supported by the compression coil spring.

3. The scroll compressor of claim 2,

the compression coil spring is inserted and disposed across a groove formed in an end surface of the sub-bearing housing and a groove formed in an end surface of the pump housing at a position facing the groove.

4. A scroll compressor is provided with: a closed container; a main frame and a sub-frame mounted on the closed container; a fixed scroll having an end plate and a scroll-shaped overlapping portion provided upright on the end plate, and mounted on the main frame; an orbiting scroll having an end plate and a spiral overlapping portion vertically provided on the end plate, and meshing with the fixed scroll to form a compression chamber; a rotating shaft which rotates the rotating scroll and has an eccentric pin portion; a rotary boss portion provided on a back surface side of the end plate of the orbiting scroll and having a rotary bearing into which the eccentric pin portion is inserted; a main bearing provided in the main frame and rotatably supporting a main shaft portion of the rotating shaft; and a sub-bearing provided in a sub-bearing housing attached to the sub-frame and rotatably supporting a sub-shaft portion of the rotary shaft, the scroll compressor being characterized in that,

the disclosed device is provided with:

and an elastic support member provided between the sub-bearing housing and the pump housing on an inner circumferential side of the plurality of support bolts in a circumferential direction.

5. The scroll compressor of claim 1 or 4,

the elastic support member is composed of a resin ring and a wave plate gasket, and elastically supports the oil supply pump.

6. The scroll compressor of claim 5,

the resin ring is made of PTFE, which is polytetrafluoroethylene, PPS, which is polyphenylene sulfide, or PEEK, which is polyether ether ketone.

7. The scroll compressor of claim 1 or 4,

the elastic support member is formed of an annular O-ring made of nitrile rubber, and elastically supports the oil supply pump.

8. The scroll compressor of claim 4,

the elastic support member is formed of an annular wave plate gasket that is inserted into an annular groove formed in an end surface of the sub-bearing housing or an end surface of the pump housing and elastically supports the oil supply pump.

9. The scroll compressor of claim 4,

an oil discharge path is provided to communicate the inner space and the outer space of the sub-bearing housing.

10. The scroll compressor of claim 9,

the oil discharge path is an oil discharge groove provided in an end surface of the pump housing on the side of the sub-bearing housing.