CN116507807A - Scroll type fluid machine - Google Patents
Scroll type fluid machine Download PDFInfo
- Publication number
- CN116507807A CN116507807A CN202180076525.1A CN202180076525A CN116507807A CN 116507807 A CN116507807 A CN 116507807A CN 202180076525 A CN202180076525 A CN 202180076525A CN 116507807 A CN116507807 A CN 116507807A
- Authority
- CN
- China
- Prior art keywords
- scroll
- eccentric
- flow path
- lubricant supply
- back pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 title claims description 23
- 239000000314 lubricant Substances 0.000 claims abstract description 54
- 239000010687 lubricating oil Substances 0.000 claims abstract description 25
- 230000002093 peripheral effect Effects 0.000 claims abstract description 25
- 238000006243 chemical reaction Methods 0.000 claims abstract description 16
- 239000003507 refrigerant Substances 0.000 description 39
- 125000006850 spacer group Chemical group 0.000 description 32
- 230000006835 compression Effects 0.000 description 11
- 238000007906 compression Methods 0.000 description 11
- 239000003921 oil Substances 0.000 description 7
- 238000005192 partition Methods 0.000 description 4
- 238000013459 approach Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/028—Means for improving or restricting lubricant flow
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Lubricating oil is well supplied to a bearing that supports an eccentric bush. A scroll compressor (100) is provided with a fixed scroll (122) fixed to a housing (140), a orbiting scroll (124) which performs orbiting motion with respect to the fixed scroll, and a conversion mechanism (300) which converts the rotational motion of a drive shaft (166) and the orbiting motion of the orbiting scroll into each other. The conversion mechanism includes: an eccentric shaft (260) which is provided on the end surface of the drive shaft and is eccentric with respect to the drive shaft; an eccentric bush (270) having a through hole (271) into which the eccentric shaft is fitted; a bearing (280) is press-fitted into a boss portion (250) formed in the orbiting scroll to support an outer peripheral surface (272) of an eccentric bush, and a lubricant supply passage (350) for supplying lubricant to the bearing is formed in the eccentric bush. The outflow port (356) of the lubricant supply passage is disposed on the outer peripheral surface (272) of the eccentric bush.
Description
Technical Field
The present invention relates to a scroll fluid machine such as a scroll compressor and a scroll expander.
Background
Patent document 1 discloses a scroll compressor as an example of a scroll fluid machine. In the scroll compressor, the drive shaft is coupled to the orbiting scroll through a crank mechanism. The crank mechanism comprises: a boss portion formed on a back pressure chamber side end surface of a bottom plate of the orbiting scroll; and an eccentric bush which is mounted in an eccentric state to a crank pin provided at an end portion of the drive shaft. The eccentric bush is rotatably supported on the inner peripheral surface of the boss portion via a bearing.
Prior art literature
Patent literature
Patent document 1: japanese patent laid-open publication No. 2019-015188
Disclosure of Invention
Technical problem to be solved by the invention
However, since the bearing described above is lubricated by scattering the lubricating oil in the back pressure chamber formed on the back surface side of the orbiting scroll, the supply of the lubricating oil to the bearing may be insufficient.
Accordingly, an object of the present invention is to satisfactorily supply lubricating oil to a bearing that supports an eccentric bush.
Technical proposal adopted for solving the technical problems
According to one aspect of the present invention, a scroll fluid machine includes a rotating main shaft provided to be rotatable in a housing, a fixed scroll fixed to the housing, a orbiting scroll orbiting with respect to the fixed scroll, and a conversion mechanism converting the rotational movement of the rotating main shaft and the orbiting movement of the orbiting scroll to each other. The conversion mechanism includes: the eccentric shaft is arranged on the end face of the rotary main shaft and eccentric relative to the rotary main shaft; an eccentric bushing having a through hole into which the eccentric shaft is inserted; and a bearing that is press-fitted into a boss portion formed in the orbiting scroll to support an outer peripheral surface of the eccentric bush, and a lubricant supply passage for supplying lubricant to the bearing is formed through the eccentric bush. Here, the outflow port of the lubricant supply passage is disposed on the outer peripheral surface of the eccentric bush.
Effects of the invention
According to one aspect of the present invention, the outflow port of the lubricant supply passage is disposed on the outer peripheral surface of the eccentric bush. Thus, since the lubricant can be directly supplied to the bearing from the outflow port of the lubricant supply passage, the lubricant can be favorably supplied to the bearing.
Drawings
Fig. 1 is a longitudinal sectional view of a scroll compressor according to a first embodiment of the present invention.
Fig. 2 is a block diagram illustrating the flow of the gas refrigerant and the lubricating oil according to the first embodiment.
Fig. 3 is an enlarged cross-sectional view of the switching mechanism of the first embodiment. Fig. 4 is a perspective view of the eccentric bushing of the first embodiment.
Fig. 5 is a sectional view of the eccentric bushing of the first embodiment.
Fig. 6 is an enlarged cross-sectional view of a switching mechanism according to a second embodiment of the present invention.
Detailed Description
Hereinafter, embodiments of the present invention will be described with reference to the drawings. Here, a case where the scroll fluid machine according to the present invention is a scroll compressor will be described. However, the invention can also be applied to scroll expanders, needless to say.
Fig. 1 is a longitudinal sectional view of a scroll compressor 100 according to a first embodiment of the present invention.
The scroll compressor 100 is incorporated in, for example, a refrigerant circuit of an air conditioner for a vehicle, compresses a gas refrigerant (fluid) sucked from a low pressure side of the refrigerant circuit, and discharges the gas refrigerant. The scroll compressor 100 includes: a scroll unit 120; a housing 140 that houses the suction chamber H1 and the discharge chamber H2 of the gas refrigerant; an electric motor 160 driving the scroll unit 120; and an inverter 180 that drives and controls the electric motor 160. In addition, for example, the scroll unit 120 may be driven by an engine output instead of the electric motor 160. Further, the inverter 180 may not be incorporated into the scroll compressor 100.
The scroll unit 120 has a fixed scroll 122 and a orbiting scroll 124 engaged with each other. Fixed scroll 122 includes: a disk-shaped bottom plate 122A; and an involute (scroll-shaped) surrounding piece 122B erected from one surface of the bottom plate 122A. The orbiting scroll 124 includes the same as the fixed scroll 122: a disk-shaped bottom plate 124A; and an involute-shaped surrounding piece 124B erected from one surface of the bottom plate 124A. Here, the disk shape may be a disk shape which is distinguishable from the external appearance, or may be formed with, for example, a convex portion, a concave portion, a notch, or the like (the same applies to the shape hereinafter).
Fixed scroll 122 and orbiting scroll 124 are configured such that their surrounds 122B engage surrounds 124B. Specifically, the tip of the wrap 122B of the fixed scroll 122 is in contact with one surface of the bottom plate 124A of the orbiting scroll 124, and the tip of the wrap 124B of the orbiting scroll 124 is disposed in contact with one surface of the bottom plate 122A of the fixed scroll 122. Further, chip seals (not shown) are attached to the front end portions of the surrounding members 122B and 124B, respectively.
In addition, fixed scroll 122 and orbiting scroll 124 are arranged such that the side walls of their surrounding pieces 122B and 124B are partially in contact with each other in a state where the circumferential angles of their surrounding pieces 122B and 124B are offset from each other. Therefore, a crescent-shaped closed space functioning as the compression chamber H3 is formed between the surrounding piece 122B of the fixed scroll 122 and the surrounding piece 124B of the orbiting scroll 124.
The orbiting scroll 124 performs an orbiting motion with respect to the fixed scroll 122. The orbiting scroll 124 is arranged to orbit around the axial center of the fixed scroll 122 via a switching mechanism 300 described later in a state where rotation thereof is prevented. Therefore, the scroll unit 120 moves the compression chamber H3 partitioned by the surrounding piece 122B of the fixed scroll 122 and the surrounding piece 124B of the orbiting scroll 124 to the central portion, and gradually reduces its volume. As a result, the scroll unit 120 compresses the gas refrigerant sucked from the outer ends of the surrounding pieces 122B and 124B into the compression chamber H3.
The housing 140 has: a front case 142, wherein the front case 142 accommodates the electric motor 160 and the inverter 180; an intermediate housing 144, wherein the intermediate housing 144 accommodates the scroll unit 120; a rear housing 146; and an inverter cover 148. The front casing 142, the intermediate casing 144, the rear casing 146, and the inverter cover 148 are fastened together by fasteners (not shown) including bolts and washers, for example, to thereby constitute the casing 140 of the scroll compressor 100.
The front case 142 has a cylindrical peripheral wall portion 142A and a thin plate-like partition wall portion 142B. The inner space of the front case 142 is partitioned by a partition wall portion 142B into a space for housing the electric motor 160 and a space for housing the inverter 180. One end side of the peripheral wall 142A, that is, an opening of a space for accommodating the inverter 180 is closed by the inverter cover 148. The other end side of the peripheral wall 142A, i.e., the opening of the space for accommodating the electric motor 160 is closed by the intermediate housing 144. In the partition wall portion 142B, a cylindrical support portion 142B1 is provided to protrude toward the other end of the peripheral wall portion 142A, and the support portion 142B1 rotatably supports one end portion of a drive shaft 166 described later in a central portion in the radial direction thereof. Here, the drive shaft 166 is an example of the "rotating main shaft" of the present invention, and is rotatably provided in the housing 140.
Further, the suction chamber H1 of the gas refrigerant is partitioned by the peripheral wall portion 142A of the front case 142, the partition wall portion 142B, and the intermediate case 144. The gas refrigerant is introduced into the suction chamber H1 from the low pressure side of the refrigerant circuit through the suction port P1 formed in the peripheral wall portion 142A. In addition, in the suction chamber H1, the gas refrigerant flows around the electric motor 160, and can cool the electric motor 160, and one suction chamber H1 is formed to communicate the space on one side of the electric motor 160 with the space on the other side thereof. An appropriate amount of lubricating oil is stored in the suction chamber H1 for lubricating sliding portions such as the driven and rotated drive shaft 166. Therefore, in the suction chamber H1, the gas refrigerant flows as a mixed fluid with the lubricating oil.
The intermediate housing 144 has a bottomed cylindrical shape having an opening opposite to the fastening side of the front housing 142, and is capable of accommodating the scroll unit 120 therein. The intermediate housing 144 has a cylindrical portion 144A and a bottom wall portion 144B on one end side thereof. The scroll unit 120 is accommodated in a space defined by the cylindrical portion 144A and the bottom wall portion 144B. A fitting portion 144A1 is formed at the other end side of the cylindrical portion 144A, and the fitting portion 144A1 is fitted with the fixed scroll 122. Thus, the opening of the intermediate housing 144 is blocked by the fixed scroll 122. The bottom wall portion 144B is formed such that a radially central portion thereof protrudes toward the electric motor 160. A through hole for passing through the other end portion of the drive shaft 166 is formed in the central portion in the radial direction of the ridge portion 144B1 of the bottom wall portion 144B. Further, an engagement portion for engaging the bearing 200 rotatably supporting the other end portion of the drive shaft 166 is formed on the scroll unit 120 side of the boss portion 144B 1.
A thin annular thrust plate 210 is disposed between the bottom wall portion 144B of the intermediate housing 144 and the bottom plate 124A of the orbiting scroll 124. The outer peripheral portion of the bottom wall portion 144B receives thrust from the orbiting scroll 124 via the thrust plate 210. Sealing members 220 are embedded in the bottom wall portion 144B and the bottom plate 124A at the portions that contact the thrust plate 210.
A back pressure chamber H4 is formed between the end surface of the bottom plate 124A on the side of the electric motor 160 and the bottom wall portion 144B, that is, between the end surface of the orbiting scroll 124 on the opposite side of the fixed scroll 122 and the intermediate housing 144. A refrigerant introduction path L1 is formed in the intermediate housing 144, and the refrigerant introduction path L1 introduces the gas refrigerant from the suction chamber H1 to the space H5 near the outer ends of the surrounding pieces 122B and 124B of the scroll unit 120. Since the refrigerant introduction path L1 communicates the space H5 with the suction chamber H1, the pressure of the space H5 is equal to the pressure (suction pressure Ps) of the suction chamber H1.
The rear case 146 is fastened to one end of the cylindrical portion 144A1 of the intermediate case 144 at the fitting portion 144A1 by a fastener. Accordingly, the bottom plate 122A of the fixed scroll 122 is sandwiched between the fitting portion 144A1 and the rear housing 146 and fixed. That is, fixed scroll 122 is fixed to casing 140. The rear case 146 has a bottomed cylindrical shape with an opening on the side fastened to the intermediate case 144, and has a cylindrical portion 146A and a bottom wall portion 146B at the other end portion of the cylindrical portion 146A.
The discharge chamber H2 of the gas refrigerant is partitioned by the cylindrical portion 146A and the bottom wall portion 146B of the rear housing 146 and the bottom plate 122A of the fixed scroll 122. A discharge passage (discharge hole) L2 for the gas refrigerant is formed in the center of the bottom plate 122A. A check valve 230, for example, a needle valve, which restricts the flow of the gas refrigerant from the discharge chamber H2 to the scroll unit 120, is attached to the discharge passage L2. In the discharge chamber H2, the gas refrigerant compressed in the compression chamber H3 of the scroll unit 120 is discharged through the discharge passage L2 and the check valve 230.
Further, although not shown, an oil separator for separating lubricating oil from the gas refrigerant in the discharge chamber H2 is disposed in the rear case 146. The gas refrigerant from which the lubricating oil has been separated by the oil separator is discharged to the high-pressure side of the refrigerant circuit through a discharge port P2 formed in the bottom wall portion 146B of the rear case 146. On the other hand, the lubricating oil separated by the oil separator is supplied to the back pressure chamber H4 through a back pressure supply passage L3 described later.
The electric motor 160 is constituted by, for example, a three-phase ac motor, and includes a rotor 162 and a stator core unit 164, and the stator core unit 164 is disposed radially outward of the rotor 162. Further, for example, a direct current from a battery (not shown) on the vehicle is converted into an alternating current by the inverter 180, and is supplied to the stator core unit 164 of the electric motor 160.
The rotor 162 is rotatably supported on the radially inner side of the stator core unit 164 via a drive shaft 166 press-fitted into a shaft hole formed at the radial center of the rotor 162. One end of the drive shaft 166 is rotatably supported by the support portion 142B1 of the front case 142 via a slide bearing 240. The other end portion of the driving shaft 166 penetrates through a through hole formed in the intermediate housing 144 and is rotatably supported by a bearing 200. If a magnetic field is generated in the stator core unit 164 by power supply from the inverter 180, a rotational force acts on the rotor 162, and the drive shaft 166 is driven to rotate. The other end of the drive shaft 166 is coupled to the orbiting scroll 124 via a conversion mechanism 300.
The conversion mechanism 300 has a function of converting the rotational movement of the rotating main shaft (in the present embodiment, the drive shaft 166) and the orbiting movement of the orbiting scroll 124 into each other. Details of the switching mechanism 300 will be described later with reference to fig. 3 to 5. In the present embodiment, orbiting scroll 124 can orbit around the axial center of fixed scroll 122 via conversion mechanism 300 in a state where rotation thereof is prevented. A balance weight (balance weight) 290 that overcomes the centrifugal force of the orbiting scroll 124 is attached to the other end portion of the drive shaft 166.
Fig. 2 is a block diagram for explaining the flow of the gas refrigerant and the lubricating oil in the scroll compressor 100.
As shown in fig. 1 and 2, the low-temperature and low-pressure gas refrigerant from the low-pressure side of the refrigerant circuit is introduced into the suction chamber H1 through the suction port P1, and thereafter, is guided to the space H5 near the outer end of the scroll unit 120 through the refrigerant introduction path L1. Next, the gas refrigerant of the space H5 is introduced into the compression chamber H3 of the scroll unit 120 to be compressed. The gas refrigerant compressed in the compression chamber H3 is discharged to the discharge chamber H2 through the discharge passage L2 and the check valve 230, and then is discharged to the high pressure side of the refrigerant circuit through the discharge port P2. In this way, the scroll unit 120 is configured to compress the gas refrigerant flowing in through the suction chamber H1 by the compression chamber H3 and to discharge the gas refrigerant through the discharge chamber H2.
Here, as shown in fig. 1, the scroll compressor 100 further includes a back pressure control valve 400, and the back pressure control valve 400 controls the back pressure Pm of the back pressure chamber H4. The back pressure control valve 400 is a mechanical (autonomous) pressure control valve that operates based on the pressure difference between the discharge pressure Pd of the discharge chamber H2 and the back pressure Pm of the back pressure chamber H4, and automatically adjusts the valve opening degree so that the back pressure Pm of the back pressure chamber H4 approaches the target back pressure Pc. The back pressure control valve 400 is housed in a housing chamber 146C, and the housing chamber 146C is formed in the bottom wall portion 146B of the rear housing 146 so as to extend from the outer peripheral surface of the bottom wall portion 146B in a direction orthogonal to the central axis of the drive shaft 166 of the electric motor 160.
As shown in fig. 1 and 2, the scroll compressor 100 includes a back pressure supply passage L3, a pressure release passage L4, and a suction pressure sensing passage L5 in addition to the refrigerant introduction passage L1 and the discharge passage L2.
The back pressure supply path L3 is formed in the rear case 146 and the intermediate case 144 so as to communicate the discharge chamber H2 with the back pressure chamber H4. Here, the back pressure supply passage L3 in the rear housing 146 passes through the housing chamber 146C in which the back pressure control valve 400 is housed. The lubricating oil separated from the gas refrigerant in the discharge chamber H2 by the oil separator is guided to the back pressure chamber H4 via the back pressure control valve 400 and the back pressure supply passage L3, so that lubrication of each sliding portion is performed, and the back pressure Pm in the back pressure chamber H4 is raised.
The back pressure control valve 400 is disposed midway in the back pressure supply passage L3 to form a part of the back pressure supply passage L3. Accordingly, the lubricating oil separated from the gas refrigerant of the discharge chamber H2 is appropriately depressurized by the back pressure control valve 400, and is supplied to the back pressure chamber H4 via the back pressure supply passage L3 located on the downstream side thereof. That is, the opening of the back pressure supply path L3 connected to the inlet side (upstream side) of the back pressure chamber H4 is adjusted by the back pressure control valve 400, so that the flow rate of the lubricating oil flowing into the back pressure chamber H4 is increased or decreased, thereby adjusting the back pressure Pm.
The pressure release passage L4 is formed so as to penetrate along the axial direction of the drive shaft 166 so that the back pressure chamber H4 communicates with the suction chamber H1. An orifice OL is disposed in the middle of the pressure release passage L4, for example, at the end of the drive shaft 166 on the suction chamber H1 side. Therefore, the flow rate of the lubricating oil in the back pressure chamber H4 is restricted by the orifice OL, and flows back to the suction chamber H1.
The suction pressure sensing path L5 communicates the space H5 near the outer end of the scroll unit 120 with the housing chamber 146C to be able to sense the suction pressure Ps of the suction chamber H1 in the back pressure control valve 400. Specifically, the suction pressure sensing path L5 is formed in the bottom plate 122A of the fixed scroll 122 and the rear housing 146. The suction pressure sensing path L5 indirectly senses the suction pressure Ps of the suction chamber H1 through the space H5, but may directly sense the suction pressure Ps of the suction chamber H1.
Here, the back pressure chamber H4 (a machine chamber provided with an orbiting drive element such as the drive shaft 166) is formed on the back surface side of the orbiting scroll 124 (i.e., the end surface side of the orbiting scroll 124 opposite to the fixed scroll 122). The back pressure chamber H4 generates a back pressure Pm that presses the orbiting scroll 124 toward the fixed scroll 122. Therefore, the orbiting scroll 124 is pressed against the fixed scroll 122 by the back pressure Pm of the back pressure chamber H4. In the compression operation of the scroll unit 120, when the resultant force of the back pressure Pm acting on the end surface of the bottom plate 124A of the orbiting scroll 124 on the back pressure chamber H4 side is too low compared to the compression reaction force acting on the end surface of the bottom plate 124A on the compression chamber H3 side, that is, when the back pressure becomes insufficient, a gap is generated between the front end portion of the wrap 124B of the orbiting scroll 124 and the bottom plate 122A of the fixed scroll 122, and a gap is generated between the bottom plate 124A of the orbiting scroll 124 and the front end portion of the wrap 122B of the fixed scroll 122, so that the volumetric efficiency of the compressor is lowered. The back pressure control valve 400 increases the back pressure Pm to be close to the target back pressure Pc in the case where the back pressure Pm is smaller than the target back pressure Pc, so as to avoid becoming an insufficient back pressure state.
On the other hand, if the resultant force of the back pressure Pm in the back pressure chamber H4 is too high as compared with the compression reaction force, that is, if the back pressure is excessive, the friction force between the fixed scroll 122 and the orbiting scroll 124 increases, and therefore the mechanical efficiency of the compressor decreases. The back pressure control valve 400 lowers the back pressure Pm and approaches the target back pressure Pc in the case where the back pressure Pm is greater than the target back pressure Pc, so as to avoid becoming a back pressure excess state.
Next, the details of the switching mechanism 300 will be described with reference to fig. 3 to 5 in addition to fig. 1. Fig. 3 is an enlarged cross-sectional view of the conversion mechanism 300. Fig. 4 is a perspective view of the eccentric bushing 270. Fig. 5 is a cross-sectional view of eccentric spacer 270.
The conversion mechanism 300 has an eccentric shaft (crank pin) 260, an eccentric spacer 270, and a bearing 280. The eccentric shaft 260 is provided at the other end face of the drive shaft 166, and is eccentric (offset) with respect to the drive shaft 166. The eccentric spacer 270 has a cylindrical shape, and has a through hole 271 into which the eccentric shaft 260 is fitted at a position eccentric from the center line BS thereof. Accordingly, the eccentric bushing 270 is mounted to the eccentric shaft 260 in an eccentric state via the through hole 271.
The bearing 280 is pressed into the cylindrical boss 250 formed to protrude from the back pressure chamber H4 side end surface of the bottom plate 124A of the orbiting scroll 124, and supports the outer peripheral surface 272 of the eccentric spacer 270. In the present embodiment, a slide bearing is used as the bearing 280. Accordingly, the eccentric spacer 270 is rotatably supported on the inner peripheral surface of the boss 250 via the bearing 280. In this way, orbiting scroll 124 can orbit around the axial center of fixed scroll 122 via conversion mechanism 300 in a state where rotation thereof is prevented.
A lubricant supply passage 350 is formed through the eccentric bush 270, and the lubricant supply passage 350 is used to supply lubricant to the bearing 280. The lubricant supply passage 350 includes: an axial flow path portion 351, the axial flow path portion 351 extending along an axial direction of the eccentric spacer 270; and a radial flow path portion 352, the radial flow path portion 352 extending along a radial direction of the eccentric spacer 270.
The axial flow path portion 351 extends substantially parallel to the center axis BS of the eccentric spacer 270 and the center axis RS of the drive shaft 166, and penetrates the eccentric spacer 270. The radial flow path portion 352 diverges from the middle of the axial flow path portion 351 and extends in the radial direction of the eccentric spacer 270 to the outer circumferential surface 272 of the eccentric spacer 270.
A recess 273 extending in the radial direction of the eccentric spacer 270 is formed in an end surface of the eccentric spacer 270 adjacent to the other end surface of the drive shaft 166, and an opening on one end side of the axial flow path portion 351 is located on a bottom surface of the recess 273. The opening can function as the inflow port 355 of the lubricant supply passage 350. That is, the axial flow path portion 351 has an inflow port 355 of the lubricant supply flow path 350.
An opening located at one end side of the radial flow path portion 352 of the outer circumferential surface 272 of the eccentric bush 270 can function as the outflow port 356 of the lubricant supply flow path 350. That is, the radial flow path portion 352 has the outflow port 356 of the lubricant supply flow path 350. The outflow port 356 of the lubricant supply passage 350 faces the inner peripheral surface (support surface) 281 of the bearing 280. The outflow port 356 of the lubricant supply passage 350 is preferably disposed so as to face the axial center portion of the inner peripheral surface 281 of the bearing 280.
As shown in fig. 5, in the present embodiment, when the eccentric spacer 270 is divided into the first region T1 and the second region T2 by the first virtual plane PL1 including the central axis RS of the drive shaft 166, the central axis BS of the eccentric spacer 270, the lubricant supply flow path 350, and the through hole 271 are located within the first region T1. The first virtual plane PL1 is a virtual plane orthogonal to a second virtual plane PL2 including both the center axis RS of the drive shaft 166 and the center axis BS of the eccentric spacer 270.
In the present embodiment, when the distance between the first virtual plane PL1 and the center axis BS of the eccentric spacer 270 is N1 and the distance between the first virtual plane PL1 and the center axis WS of the axial flow path portion 351 is N2, the relationship of N1 < N2 is satisfied. That is, the central axis WS of the axial flow path portion 351 is farther than the central axis BS of the eccentric spacer 270 as viewed from the first virtual plane PL 1. Further, the lubricant supply flow path 350 is farther than the center axis BS of the eccentric spacer 270 as viewed from the first virtual plane PL 1.
In the present embodiment, when the distance between the center axis RS of the drive shaft 166 and the center axis BS of the eccentric spacer 270 is N3 and the distance between the center axis RS of the drive shaft 166 and the center axis WS of the axial flow path portion 351 is N4, the relationship of N3 < N4 is satisfied. That is, the central axis WS of the axial flow path portion 351 is farther than the central axis BS of the eccentric spacer 270 when viewed from the central axis RS of the drive shaft 166. Further, the lubricant supply flow path 350 is farther than the center axis BS of the eccentric spacer 270 when viewed from the center axis RS of the drive shaft 166.
Here, the supply of the lubricating oil to the bearing 280 will be described with reference to fig. 1 and 3 to 5.
A part of the lubricating oil in the back pressure chamber H4 passes through the concave portion 273 of the eccentric bush 270 and enters the axial flow path portion 351 from the inflow port 355. Further, most of the lubricating oil in the axial flow path portion 351 flows into the radial flow path portion 352 by the centrifugal force generated by the rotational movement of the drive shaft 166 with the central axis RS of the drive shaft 166 as the rotational center, and is supplied from the outflow port 356 to the inner peripheral surface 281 of the bearing 280. In order to sufficiently obtain the centrifugal force, the layout of the lubricant supply passage 350 is adopted in the present embodiment.
According to the present embodiment, the scroll compressor 100, which is an example of a scroll fluid machine, includes a drive shaft 166 (a main rotation shaft) rotatably provided in a housing 140, a fixed scroll 122 fixed to the housing 140, an orbiting scroll 124 that performs orbiting motion with respect to the fixed scroll 122, and a conversion mechanism 300 that converts the rotational motion of the drive shaft 166 (the main rotation shaft) and the orbiting motion of the orbiting scroll 124 into each other. The switching mechanism 300 includes: an eccentric shaft 260 provided on an end surface of the drive shaft 166 (rotating main shaft) and eccentric with respect to the drive shaft 166 (rotating main shaft); an eccentric spacer 270, the eccentric spacer 270 having a through hole 271 into which the eccentric shaft 260 is inserted; and a bearing 280, wherein the bearing 280 is pressed into the boss portion 250 formed on the orbiting scroll 124 and supports the outer circumferential surface 272 of the eccentric spacer 270. A lubricant supply passage 350 is formed through the eccentric bush 270, and the lubricant supply passage 350 is used to supply lubricant to the bearing 280. The outflow port 356 of the lubricant supply channel 350 is disposed on the outer circumferential surface 272 of the eccentric bush 270. Accordingly, since the lubricant can be directly supplied from the outflow port 356 of the lubricant supply channel 350 to the bearing 280, the lubricant can be favorably supplied to the bearing 280.
Further, according to the present embodiment, the outflow port 356 of the lubricant supply flow path 350 faces the inner peripheral surface 281 of the bearing 280. This can satisfactorily supply the lubricating oil to the inner peripheral surface 281 of the bearing 280.
Further, according to the present embodiment, the lubricating oil supply passage 350 includes: an axial flow path portion 351, the axial flow path portion 351 extending along an axial direction of the eccentric spacer 270; and a radial flow path portion 352, the radial flow path portion 352 extending along a radial direction of the eccentric spacer 270. The axial flow path portion 351 has an inflow port 355 of the lubricant supply flow path 350. The radial flow path portion 352 has an outflow port 356 of the lubricant supply flow path 350. Thus, the lubricant supply passage 350 can be easily formed.
Further, according to the present embodiment, the lubricant supply passage 350 is farther than the center axis BS of the eccentric spacer 270 as viewed from the center axis RS of the drive shaft 166 (rotating main shaft). Thereby, the lubricating oil can be positively supplied to the bearing 280 by the centrifugal force generated by the rotational movement of the drive shaft 166.
Further, according to the present embodiment, when the eccentric spacer 270 is divided into the first region T1 and the second region T2 by the first imaginary plane PL1 including the central axis RS of the drive shaft 166 (rotation main shaft), the central axis BS of the eccentric spacer 270, the lubricant supply flow path 350, and the through hole 271 are located within the first region T1. The lubricant supply flow path 350 is farther than the center axis BS of the eccentric spacer 270 when viewed from the first virtual plane PL 1. Thereby, the lubricating oil can be positively supplied to the bearing 280 by the centrifugal force generated by the rotational movement of the drive shaft 166.
In addition, according to the present embodiment, the scroll compressor 100, which is an example of a scroll fluid machine, further includes a back pressure chamber H4, and the back pressure chamber H4 is formed on the back surface side of the orbiting scroll 124, and generates a back pressure that presses the orbiting scroll 124 to the fixed scroll 122 side. The inflow port 355 of the lubricant oil supply passage 350 communicates with the back pressure chamber H4. Therefore, the lubricating oil in the back pressure chamber H4 can be smoothly supplied to the bearing 280.
Further, according to the present embodiment, the inflow port 355 of the lubricant supply passage 350 is disposed in the concave portion 273 formed in the end surface of the eccentric bush 270. This allows the lubricant oil from the back pressure chamber H4 to be smoothly guided to the lubricant oil supply passage 350.
Further, according to the present embodiment, a slide bearing is used as the bearing 280. Thus, the eccentric spacers 270 can be rotatably supported by a simple structure.
Next, a second embodiment of the present invention will be described with reference to fig. 6.
Fig. 6 is an enlarged cross-sectional view of the switching mechanism 300 of the present embodiment.
The points different from the first embodiment described above will be described.
A balance weight (balance weight) 290' is provided integrally with the eccentric bush 270. The balance weight 290' is disposed on the opposite side of the through hole 271 so as to sandwich the center axis RS of the drive shaft 166. The same lubricant supply flow path 350 as described above is preferably also formed in the eccentric bush 270 integrally including the balance weight 290'.
In the first and second embodiments described above, the balance weights 290 and 290' may be omitted.
In the first and second embodiments described above, the scroll fluid machine according to the present invention is described as a scroll compressor, but it is needless to say that the present invention can be applied to a scroll expander. In the case of being applied to a scroll expander, the scroll expander is incorporated into a refrigerant circuit of a vapor cycle device for a vehicle, for example, and expands a refrigerant introduced from the refrigerant circuit to generate power (recover power from the refrigerant). In addition, in the case of application to a scroll expander, the aforementioned drive shaft 166 becomes an output shaft. That is, if the scroll fluid machine of the present invention is a scroll compressor, the "rotating main shaft" of the present invention functions as a drive shaft, and if the scroll fluid machine of the present invention is a scroll expander, the "rotating main shaft" of the present invention functions as an output shaft.
While the preferred embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and further modifications and the like can be made based on the technical idea of the present invention.
(symbol description)
100 scroll compressor (scroll fluid machine);
122 fixed vortex plate;
124 orbiting scroll;
140 a housing;
166 drive shaft (rotating spindle);
250 sleeve portion;
260 eccentric shafts;
270 eccentric bushings;
271 through holes;
272 outer peripheral surface;
273 recess;
280 bearings;
290. 290' balance weights;
281 inner circumferential surface;
300 conversion mechanism;
350 a lubricating oil supply passage;
351 an axial flow path portion;
352 radial flow path portion;
355 flow inlet;
356 outlet;
BS, RS, WS central axis;
an H4 back pressure chamber;
PL1 a first imaginary plane;
PL 2a second imaginary plane;
a T1 first region;
t2 second region.
Claims (9)
1. A scroll fluid machine comprising a housing, a rotating main shaft rotatably provided in the housing, a fixed scroll fixed to the housing, a orbiting scroll orbiting with respect to the fixed scroll, and a conversion mechanism for converting the rotational movement of the rotating main shaft and the orbiting movement of the orbiting scroll into each other,
the conversion mechanism includes:
the eccentric shaft is arranged on the end face of the rotary main shaft and eccentric relative to the rotary main shaft;
an eccentric bushing having a through hole into which the eccentric shaft is inserted; and
a bearing press-fitted into a boss portion formed in the orbiting scroll to support an outer peripheral surface of the eccentric bush,
a lubricant supply passage for supplying lubricant to the bearing is formed through the eccentric bush,
the outflow port of the lubricant supply passage is disposed on the outer peripheral surface of the eccentric bush.
2. The scroll fluid machine according to claim 1, wherein,
the outflow port of the lubricant supply passage faces the inner peripheral surface of the bearing.
3. A scroll fluid machine according to claim 1 or 2, wherein,
the lubricating oil supply flow path includes an axial flow path portion extending in an axial direction of the eccentric bush and a radial flow path portion extending in a radial direction of the eccentric bush,
the axial flow path portion has an inflow port of the lubricant supply flow path,
the radial flow path portion has an outflow port of the lubricant supply flow path.
4. A scroll fluid machine according to any one of claims 1 to 3, wherein,
the lubricant supply passage is farther than the center axis of the eccentric bush when viewed from the center axis of the rotating main shaft.
5. The scroll fluid machine according to any one of claims 1 to 4, wherein,
when the eccentric bushing is divided into a first region and a second region by an imaginary plane including a central axis of the rotating main shaft, the central axis of the eccentric bushing, the lubricant supply flow path, and the through hole are located in the first region.
6. The scroll fluid machine according to claim 5, wherein,
the lubricant supply flow path is farther than a central axis of the eccentric bush when viewed from the virtual plane.
7. The scroll fluid machine according to any one of claims 1 to 6, wherein,
and a back pressure chamber formed on the back surface side of the orbiting scroll and generating a back pressure for pressing the orbiting scroll to the fixed scroll side,
an inflow port of the lubricant supply passage communicates with the back pressure chamber.
8. The scroll fluid machine according to any one of claims 1 to 7, wherein,
an inlet of the lubricant supply passage is disposed in a recess formed in an end surface of the eccentric bush.
9. The scroll fluid machine according to any one of claims 1 to 8, wherein,
a sliding bearing is used as the bearing.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2020-194280 | 2020-11-24 | ||
| JP2020194280A JP2022083044A (en) | 2020-11-24 | 2020-11-24 | Scroll fluid machine |
| PCT/JP2021/038214 WO2022113558A1 (en) | 2020-11-24 | 2021-10-15 | Scroll fluid machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116507807A true CN116507807A (en) | 2023-07-28 |
Family
ID=81754245
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202180076525.1A Pending CN116507807A (en) | 2020-11-24 | 2021-10-15 | Scroll type fluid machine |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20240011487A1 (en) |
| JP (1) | JP2022083044A (en) |
| CN (1) | CN116507807A (en) |
| DE (1) | DE112021004837T5 (en) |
| WO (1) | WO2022113558A1 (en) |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4997349A (en) * | 1989-10-05 | 1991-03-05 | Tecumseh Products Company | Lubrication system for the crank mechanism of a scroll compressor |
| JP2815527B2 (en) * | 1993-07-23 | 1998-10-27 | サンデン株式会社 | Scroll compressor |
| JPH094577A (en) * | 1995-06-19 | 1997-01-07 | Sanden Corp | Scroll compressor |
| JPH11182461A (en) * | 1997-12-15 | 1999-07-06 | Sanden Corp | Scroll compressor |
| US6146118A (en) * | 1998-06-22 | 2000-11-14 | Tecumseh Products Company | Oldham coupling for a scroll compressor |
| JP4459552B2 (en) * | 2003-06-06 | 2010-04-28 | サンデン株式会社 | Scroll type fluid machinery |
| JP5315933B2 (en) * | 2008-06-05 | 2013-10-16 | 株式会社豊田自動織機 | Electric scroll compressor |
| JP2012062854A (en) * | 2010-09-17 | 2012-03-29 | Keihin Corp | Scroll compressor |
| JP6037174B2 (en) * | 2011-05-30 | 2016-11-30 | サンデンホールディングス株式会社 | Scroll compressor |
| JP5565429B2 (en) * | 2012-03-29 | 2014-08-06 | 株式会社豊田自動織機 | Scroll compressor |
| JP2014202162A (en) * | 2013-04-08 | 2014-10-27 | サンデン株式会社 | Scroll type fluid machine |
| JP2019015188A (en) | 2017-07-04 | 2019-01-31 | サンデン・オートモーティブコンポーネント株式会社 | Scroll type compressor |
| JP7056820B2 (en) * | 2018-06-29 | 2022-04-19 | サンデン・オートモーティブコンポーネント株式会社 | Scroll compressor |
-
2020
- 2020-11-24 JP JP2020194280A patent/JP2022083044A/en active Pending
-
2021
- 2021-10-15 WO PCT/JP2021/038214 patent/WO2022113558A1/en active Application Filing
- 2021-10-15 DE DE112021004837.6T patent/DE112021004837T5/en active Pending
- 2021-10-15 US US18/251,971 patent/US20240011487A1/en active Pending
- 2021-10-15 CN CN202180076525.1A patent/CN116507807A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| JP2022083044A (en) | 2022-06-03 |
| WO2022113558A1 (en) | 2022-06-02 |
| US20240011487A1 (en) | 2024-01-11 |
| DE112021004837T5 (en) | 2023-07-06 |
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