JP2018112130A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To inhibit control failure and lubrication failure caused by clogging of a filter for capturing contaminations mixed into a lubrication oil in a compressor which compresses a working fluid.SOLUTION: A compressor includes: a compression mechanism which compresses a working fluid; and a first filter 260, a second filter 262, and a third filter 264 which are disposed at a passage L3 of a lubrication oil for lubricating the compression mechanism at intervals with their filter surfaces intersecting with a direction in which the passage L3 extends. The first filter 260, the second filter 262, and the third filter 264 respectively form spaces with an inner wall of the passage L3, and areas of the filters increase from the upstream to the downstream in a lubrication oil flow direction.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a compressor that compresses a working fluid such as a refrigerant.

  In the compressor, when the mist of lubricating oil is mixed into the gaseous refrigerant (gas refrigerant) compressed by the compression mechanism, it may be introduced into a condenser or the like of the refrigerant circuit and the efficiency may be reduced. For this reason, the compressor is provided with an oil separator that separates the lubricating oil from the gaseous refrigerant discharged from the compression mechanism. The lubricating oil separated by the oil separator is used as a back pressure that presses the orbiting scroll against the fixed scroll in a scroll compressor, for example. In order to adjust the back pressure, a back pressure control valve that operates according to a differential pressure between the suction pressure and the discharge pressure is used.

  Incidentally, contamination (foreign matter) such as sludge is mixed in the lubricating oil of the compressor. When contamination is introduced into the back pressure control valve, for example, the valve body cannot move smoothly, and the back pressure cannot be adjusted appropriately. For this reason, as described in Japanese Patent Application Laid-Open No. 2003-343433 (Patent Document 1), by attaching a filter to the back pressure control valve, contamination is captured and occurrence of malfunction is suppressed.

JP 2003-343433 A

  However, since the filter of the back pressure control valve has a small contamination capturing area, if the compressor is used for many years, the entire surface of the filter is covered with the contamination and the lubricating oil does not flow. There is a risk of poor lubrication of moving parts. Note that a problem due to contamination mixed in the lubricating oil may occur not only in the back pressure control valve but also in an orifice disposed in the lubricating oil flow path.

  Then, an object of this invention is to provide the compressor which can suppress the control failure, lubrication failure, etc. by filter clogging.

  For this reason, the compressor is disposed with a space between the compression mechanism that compresses the working fluid and the flow path of the lubricating oil that lubricates the compression mechanism, with the filter surfaces intersecting in the direction in which the flow path extends. A plurality of filters. And a some filter has a clearance gap between the inner walls of a flow path, and an area increases as it goes to the downstream from the upstream of the distribution direction of lubricating oil.

  According to the present invention, control failure and lubrication failure due to filter clogging can be suppressed.

It is sectional drawing which shows an example of a scroll compressor. It is explanatory drawing of the separation method of the lubricating oil by an oil separator. It is a block diagram explaining the flow of a gaseous refrigerant. It is explanatory drawing of 1st Example which has arrange | positioned the several filter in the flow path of lubricating oil. It is explanatory drawing which shows an example of the arrangement method of a some filter. It is explanatory drawing of the effect | action and effect by 1st Example. It is explanatory drawing which shows the other example of the arrangement method of a some filter. It is explanatory drawing of 2nd Example which has arrange | positioned the several filter in the flow path of lubricating oil. It is explanatory drawing of the effect | action and effect by 2nd Example.

Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 shows an example of a scroll compressor. A scroll compressor is an example of a compressor.

  The scroll compressor 100 includes a scroll unit 120, a housing 140 having a gas refrigerant suction chamber H1 and a discharge chamber H2, an electric motor 160 that drives the scroll unit 120, and an inverter 180 that controls the electric motor 160. ing. The scroll unit 120 may be driven by, for example, engine output instead of the electric motor 160. Further, the inverter 180 may not be incorporated in the scroll compressor 100.

  The scroll unit 120 includes a fixed scroll 122 and a turning scroll 124 that are meshed with each other. The fixed scroll 122 includes a disc-shaped bottom plate 122A and an involute-shaped (spiral shape) wrap 122B standing from one surface of the bottom plate 122A. Similar to the fixed scroll 122, the orbiting scroll 124 includes a disc-shaped bottom plate 124A and an involute-shaped wrap 124B standing from one surface of the bottom plate 124A.

  The fixed scroll 122 and the orbiting scroll 124 are arranged so as to mesh the wraps 122B and 124B. Specifically, the front end portion 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 front end portion of the wrap 124B of the orbiting scroll 124 is in contact with one surface of the bottom plate 122A of the fixed scroll 122. Is arranged. A tip seal (not shown) is attached to the tip of the wraps 122B and 124B.

  Further, the fixed scroll 122 and the orbiting scroll 124 are arranged such that the side walls of the wraps 122B and 124B are in partial contact with each other in a state where the circumferential angles of the wraps 122B and 124B are shifted from each other. Therefore, a crescent-shaped sealed space that functions as the compression chamber H3 is formed between the wrap 122B of the fixed scroll 122 and the wrap 124B of the orbiting scroll 124.

  The orbiting scroll 124 is disposed so as to be able to revolve around the axis of the fixed scroll 122 via a crank mechanism 240 described later in a state in which the rotation is prevented. Therefore, the scroll unit 120 moves the compression chamber H3 defined by the wrap 122B of the fixed scroll 122 and the wrap 124B of the orbiting scroll 124 to the center, and gradually reduces the volume thereof. As a result, the scroll unit 120 compresses the gaseous refrigerant sucked into the compression chamber H3 from the outer ends of the wraps 122B and 124B.

  The housing 140 includes a front housing 142 that houses the electric motor 160 and the inverter 180, a center housing 144 that houses the scroll unit 120, a rear housing 146, and an inverter cover 148. The front housing 142, the center housing 144, the rear housing 146, and the inverter cover 148 are integrally fastened by, for example, a fastener (not shown) including a bolt and a washer, so that the housing of the scroll compressor 100 is obtained. 140 is configured.

  The front housing 142 includes a substantially cylindrical peripheral wall portion 142A and a partition wall portion 142B. The internal space of the front housing 142 is partitioned into a space for housing the electric motor 160 and a space for housing the inverter 180 by the partition wall 142B. The opening on one end side of the peripheral wall portion 142 </ b> A is closed by the inverter cover 148. Further, the opening on the other end side of the peripheral wall portion 142 </ b> A is closed by the center housing 144. The partition wall 142B has a substantially cylindrical support 142B1 that rotatably supports one end of a drive shaft 166, which will be described later, at the center in the radial direction, and protrudes toward the other end of the peripheral wall 142A. Has been.

  Further, a gas refrigerant suction chamber H <b> 1 is defined by the peripheral wall 142 </ b> A and the partition wall 142 </ b> B of the front housing 142 and the center housing 144. Low-pressure and low-temperature gaseous refrigerant is sucked into the suction chamber H1 through a suction port P1 formed in the peripheral wall 142A. In the suction chamber H1, gas refrigerant flows around the electric motor 160 so that the electric motor 160 can be cooled, and the space on one side of the electric motor 160 communicates with the space on the other side. A suction chamber H1 is formed. An appropriate amount of lubricating oil is stored in the suction chamber H1 in order to lubricate sliding portions such as the drive shaft 166 that is rotationally driven. For this reason, in the suction chamber H1, the gaseous refrigerant flows as a mixed fluid with the lubricating oil.

  The center housing 144 has a substantially bottomed cylindrical shape that is open on the side opposite to the fastening side with the front housing 142, and can accommodate the scroll unit 120 therein. The center 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 into which the fixed scroll 122 is fitted is formed on the other end side of the cylindrical portion 144A. Therefore, the opening of the center housing 144 is closed by the fixed scroll 122. Further, the bottom wall portion 144 </ b> B is formed so that a central portion in the radial direction bulges toward the electric motor 160. A through hole for allowing the other end portion of the drive shaft 166 to penetrate is formed in the radial center portion of the bulging portion 144B1 of the bottom wall portion 144B. And the fitting part which the bearing 200 which supports the other end part of the drive shaft 166 freely rotatably is formed in the scroll unit 120 side of the bulging part 144B1.

  An annular thrust plate 210 is disposed between the bottom wall portion 144 </ b> B of the center housing 144 and the bottom plate 124 </ b> A of the orbiting scroll 124. The outer peripheral portion of the bottom wall portion 144 </ b> B receives a thrust force from the orbiting scroll 124 via the thrust plate 210. Sealing members (not shown) are embedded in the bottom wall portion 144B and the portions of the bottom plate 124A that are in contact with the thrust plate 210, respectively.

  Further, a back pressure chamber H4 is formed between the end surface of the bottom plate 124A on the electric motor 160 side and the bottom wall portion 144B, that is, between the end surface of the orbiting scroll 124 opposite to the fixed scroll 122 and the center housing 144. Has been. A gas refrigerant (specifically, a mixed fluid of a gas refrigerant and lubricating oil) is introduced into the center housing 144 from the suction chamber H1 to the space H5 near the outer ends of the wraps 122B and 124B of the scroll unit 120. A refrigerant introduction passage L1 is formed. Since the refrigerant introduction passage L1 communicates the space H5 and the suction chamber H1, the pressure of the space H5 is equal to the pressure of the suction chamber H1 (suction pressure Ps).

  The rear housing 146 is fastened to a fitting portion 144A1 side end portion of the cylindrical portion 144A of the center housing 144 by a fastener. Accordingly, the bottom plate 122A of the fixed scroll 122 is fixed by being sandwiched between the fitting portion 144A1 and the rear housing 146. Further, the rear housing 146 has a substantially bottomed cylindrical shape with an opening on the fastening side (one end side) with the center housing 144, and has a cylindrical portion 146A and a bottom wall portion 146B on the other end side.

  A gas refrigerant discharge chamber H <b> 2 is defined by the cylindrical portion 146 </ b> A and the bottom wall portion 146 </ b> B of the rear housing 146 and the bottom plate 122 </ b> A of the fixed scroll 122. A compressed refrigerant discharge passage (discharge hole) L2 is formed at the center of the bottom plate 122A, and the discharge passage L2 restricts the flow from the discharge chamber H2 to the scroll unit 120, for example, a check valve comprising a reed valve. A valve 220 is attached. Compressed refrigerant compressed in the compression chamber H3 of the scroll unit 120 is discharged into the discharge chamber H2 through the discharge passage L2 and the check valve 220.

  In the rear housing 146, an oil separator 230 for separating the lubricating oil from the gaseous refrigerant in the discharge chamber H2 is disposed. Specifically, the rear end portion of the rear housing 146, that is, the end portion on the side opposite to the center housing 144, has a gas-liquid separation chamber having a circular cross section extending from the outer peripheral wall to the inside. 230A is formed. A stepped inner cylinder 230B having a circular cross section is inserted into the gas-liquid separation chamber 230A so as to be concentric with the gas-liquid separation chamber 230A. The base end portion of the inner cylinder 230B is locked to the step portion 230A1 of the gas-liquid separation chamber 230A, and the distal end portion extends to a position spaced apart from the innermost portion of the gas-liquid separation chamber 230A by a predetermined interval. Here, at least the space of the gas-liquid separation chamber 230A in which the inner cylinder 230B is disposed functions as a separation portion that separates the lubricating oil from the gas refrigerant, and is substantially cylindrical in shape at the innermost portion of the gas-liquid separation chamber 230A. This space functions as a reservoir for temporarily storing the lubricating oil separated by the oil separator 230.

  The opening of the gas-liquid separation chamber 230A in the rear housing 146 is closed by a bolt (not shown) that can press the inner cylinder 230B. The bolt is formed with a through-hole penetrating from the end surface of the head portion to the tip end portion of the shaft portion. A discharge port P2 for connecting piping is formed at the head of the bolt in order to guide the gaseous refrigerant from which the lubricating oil is separated by the oil separator 230 to a condenser (not shown). The gas-liquid separation chamber 230A communicates with the discharge chamber H2 via an introduction port 146C extending in the tangential direction of the inner peripheral surface thereof.

  Therefore, the gaseous refrigerant compressed by the scroll unit 120 is introduced from the introduction port 146C to the oil separator 230 via the discharge chamber H2. As shown in FIG. 2, the gas refrigerant introduced into the oil separator 230 moves downward while swirling in an annular space formed by the inner peripheral surface of the gas-liquid separation chamber 230A and the outer peripheral surface of the inner cylinder 230B. And flow. At this time, the mist of the lubricating oil contained in the gas refrigerant receives a centrifugal force generated when the gas refrigerant swirls and moves outward. When the lubricant mist moves outward, it adheres to the inner peripheral surface of the gas-liquid separation chamber 230A and is dropped onto the bottom using gravity. Then, the lubricating oil separated by the oil separator 230 is guided to a pressure supply passage L3 described later. On the other hand, the gaseous refrigerant from which the lubricating oil has been separated enters the internal space from the tip of the inner cylinder 230B, and is discharged from a discharge port P2 formed in the head of the bolt using the pressure.

  In FIG. 1, the flow of the gaseous refrigerant before or after mixing the lubricating oil is indicated by a hatched arrow, and the flow of the gaseous refrigerant (mixed fluid) mixed with the lubricating oil is indicated by a black arrow. The flow of lubricating oil separated from the refrigerant is indicated by white arrows.

  The electric motor 160 is composed of, for example, a three-phase AC motor, and includes a rotor 162 and a stator core unit 164 disposed on the radially outer side of the rotor 162. For example, a direct current from an on-vehicle battery (not shown) is converted into an alternating current by the inverter 180 and supplied to the electric motor 160.

  The rotor 162 is rotatably supported on the radially inner side of the stator core unit 164 through a drive shaft 166 that is press-fitted into a shaft hole formed at the center in the radial direction. One end portion of the drive shaft 166 is rotatably supported by the support portion 142B1 of the front housing 142. The other end of the drive shaft 166 passes through a through hole formed in the center housing 144 and is rotatably supported by the bearing 200. When a magnetic field is generated in the stator core unit 164 by power feeding from the inverter 180, a rotational force acts on the rotor 162, and the drive shaft 166 is rotationally driven. The other end of the drive shaft 166 is connected to the orbiting scroll 124 via the crank mechanism 240.

  The crank mechanism 240 is attached in an eccentric state to a substantially cylindrical boss portion 240A that protrudes from the end surface on the back pressure chamber H4 side of the bottom plate 124A of the orbiting scroll 124 and a crank 240B that is provided at the other end portion of the drive shaft 166. And an eccentric bush 240C. The eccentric bush 240C is rotatably supported by the boss portion 240A. Note that a balancer weight 240 </ b> D is attached to the other end portion of the drive shaft 166 to resist centrifugal force during the operation of the orbiting scroll 124. Therefore, the orbiting scroll 124 can revolve around the axis of the fixed scroll 122 via the crank mechanism 240 in a state where the rotation of the orbiting scroll 124 is suppressed. Here, the scroll unit 120, the drive shaft 166, and the crank mechanism 240 are cited as examples of the compression mechanism.

  FIG. 3 is a block diagram for explaining the flow of the gaseous refrigerant in the scroll compressor 100.

  As shown in FIGS. 1 and 3, the low-pressure / low-temperature gas refrigerant from the evaporator is introduced into the suction chamber H1 through the suction port P1, and then the outer end of the scroll unit 120 through the refrigerant introduction passage L1. To the space H5 near the section. The gaseous refrigerant in the space H5 is taken into the compression chamber H3 of the scroll unit 120 and compressed. The compressed refrigerant compressed in the compression chamber H3 is discharged to the discharge chamber H2 through the discharge passage L2 and the check valve 220, and is then guided from the discharge chamber H2 to the oil separator 230 through the introduction port 146C. The gaseous refrigerant from which the lubricating oil is separated by the oil separator 230 is discharged to the condenser through the discharge port P2. In this way, the scroll unit 120 that compresses the gaseous refrigerant flowing in through the suction chamber H1 in the compression chamber H3 and discharges the compressed refrigerant through the discharge chamber H2 is configured.

  Here, as shown in FIG. 1, a back pressure control valve 250 for adjusting the pressure of the back pressure chamber H4 is further incorporated in the rear end portion of the rear housing 146.

  The back pressure control valve 250 operates according to the suction pressure Ps of the suction chamber H1 and the discharge pressure Pd of the discharge chamber H2, and the back pressure Pm of the back pressure chamber H4 is a target back pressure according to the suction pressure Ps and the discharge pressure Pd. This is a known mechanical (autonomous) flow control valve that automatically adjusts the valve opening so as to approach Pc.

  As shown in FIGS. 1 and 3, the scroll compressor 100 includes a pressure supply passage L3 and a pressure release passage L4 in addition to the refrigerant introduction passage L1 and the discharge passage L2.

  The back pressure control valve 250 is disposed in the middle of the pressure supply passage L3 so as to constitute a part of the pressure supply passage L3. Accordingly, the lubricating oil separated by the oil separator 230 is supplied to the back pressure chamber H4 via the pressure supply passage L3 while being appropriately decompressed by the back pressure control valve 250. That is, by adjusting the opening of the pressure supply passage L3 connected to the inlet side (upstream side) of the back pressure chamber H4 with the back pressure control valve 250, the flow rate of the lubricating oil flowing into the back pressure chamber H4 is increased or decreased. Then, the back pressure Pm is adjusted.

  The pressure release passage L4 communicates the back pressure chamber H4 and the suction chamber H1. An orifice OL is arranged in the middle of the pressure release passage L4. The pressure release passage L4 in which the orifice OL is disposed is formed so as to penetrate the drive shaft 166 and extend along the central axis of the drive shaft 166. For example, the orifice OL is disposed at the end of the drive shaft 166 on the suction chamber H1 side. The lubricating oil in the back pressure chamber H4 is returned to the suction chamber H1 while the flow rate is limited by the orifice OL.

  Then, the orbiting scroll 124 is pressed toward the fixed scroll 122 by the back pressure Pm in the back pressure chamber H4. During the compression operation of the scroll unit 120, the resultant force of the back pressure Pm acting on the back pressure chamber H4 side end surface of the bottom plate 124A of the orbiting scroll 124 is smaller than the compression reaction force acting on the compression chamber H3 side end surface of the bottom plate 124A. When the back pressure is insufficient, a gap is generated between the tip of the wrap 124B of the orbiting scroll 124 and the bottom plate 122A of the fixed scroll 122, and the bottom plate 124A of the orbiting scroll 124 and the tip of the wrap 122B of the fixed scroll 122 There may be a gap between them, which may reduce the volumetric efficiency of the compressor. For this reason, the back pressure Pm is adjusted by the back pressure control valve 250 so that the resultant force is greater than the compression reaction force.

  On the other hand, when the resultant force due to the back pressure Pm in the back pressure chamber H4 is too higher than the compression reaction force, that is, when the back pressure is excessive, the frictional force between the fixed scroll 122 and the orbiting scroll 124 becomes large. The machine efficiency is reduced. For this reason, when the back pressure Pm exceeds the target back pressure Pc, the back pressure control valve 250 reduces the back pressure Pm so as to approach the target back pressure Pc so that the back pressure does not become excessive.

  By the way, contamination such as sludge is mixed in the lubricating oil separated by the oil separator 230. When contamination is introduced into the back pressure control valve 250 located downstream of the oil separator 230, for example, the valve body of the back pressure control valve 250 cannot move smoothly, and the back pressure Pm in the back pressure chamber H4 is reduced to the target back pressure. There is a possibility that the pressure Pc cannot be adjusted. When contamination is introduced into the orifice OL located downstream of the oil separator 230, for example, the flow path of the lubricating oil is blocked or narrowed, and the lubricating oil is transferred from the back pressure chamber H4 to the suction chamber H1. It may be difficult to return, and the back pressure Pm in the back pressure chamber H4 may not be adjusted to the target back pressure Pc.

  Therefore, a plurality of filters are disposed in the flow path of the lubricating oil that lubricates the compression mechanism that compresses the gaseous refrigerant, specifically, the pressure supply passage L3 and the pressure release passage L4, thereby mixing in the lubricating oil. Captures contaminated contamination. In the following description, a plurality of filters are disposed in the pressure supply passage L3 for supplying the lubricating oil separated by the oil separator 230 to the back pressure control valve 250. A plurality of filters may be disposed in the pressure supply passage L3 located in the pressure relief passage L4 formed in the drive shaft 166 and the like. However, if a plurality of filters are provided in the pressure supply passage L3 that supplies the lubricating oil separated by the oil separator 230 to the back pressure control valve 250, to a portion where a problem may occur due to contamination. The introduction of contamination is suppressed.

  FIG. 4 shows an example of a plurality of filters disposed in the pressure supply passage L3. That is, in the pressure supply passage L3 positioned between the oil separator 230 and the back pressure control valve 250, the first filter 260, the filter surface is orthogonal to the direction in which the pressure supply passage L3 extends and is spaced at a predetermined interval. A second filter 262 and a third filter 264 are provided. The areas of the first filter 260, the second filter 262, and the third filter 264 increase as they go from upstream to downstream in the flow direction of the lubricating oil. In addition, the first filter 260, the second filter 262, and the third filter 264 have, for example, a cutout in which a part of a circle is cut out so as to have a gap with the inner wall of the pressure supply passage L3. It has a circular shape. Note that the plurality of filters are not limited to the first filter 260, the second filter 262, and the third filter 264, and may be two or more filters. The first filter 260, the second filter 262, and the third filter 264 are not limited to the configuration in which the filter surfaces are orthogonal to the direction in which the pressure supply passage L3 extends, and the filter surfaces are inclined with respect to the direction. And may be arranged so as to intersect.

  As shown in FIG. 5, the first filter 260, the second filter 262, and the third filter 264 are staggered with respect to the pressure supply passage L3, that is, portions facing each other across the axis of the pressure supply passage L3. For example, it is arrange | positioned so that the clearance gap may be located in the upper part and the lower part alternately. Here, the first filter 260, the second filter 262, and the third filter 264 are located between adjacent filters as viewed from the direction along the pressure supply passage L3, that is, the direction indicated by the white arrow in FIG. It is arrange | positioned so that it may have a part to overlap. Accordingly, the first filter 260, the second filter 262, and the third filter 264 are arranged so that no gap appears on the cross section of the pressure supply passage L3 when viewed from the direction indicated by the white arrow in FIG. It is installed.

  In this way, as shown in FIG. 6, a part of the contamination CON mixed in the lubricating oil is captured by the first filter 260 located on the most upstream side. A part of the contamination CON that has not been captured by the first filter 260 is captured by the second filter 262 located downstream of the first filter 260. Then, the remaining contamination CON that has not been captured by the second filter 262 is captured by the third filter 264 located downstream of the second filter 262. At this time, since the first filter 260, the second filter 262, and the third filter 264 are arranged so that no gap appears on the cross section of the pressure supply passage L3, they are mixed into the lubricating oil. The contamination CON is captured by any one of the filters.

  In short, the contamination CON mixed in the lubricating oil is captured stepwise by the first filter 260, the second filter 262, and the third filter 264 having a gap with the inner wall of the pressure supply passage L3. The Therefore, it is possible to capture the contamination CON while securing the flow path of the lubricating oil, and it is possible to reduce the contamination CON introduced into the back pressure control valve 250 and the orifice OL arranged downstream thereof. . Further, since the contamination CON introduced into the back pressure control valve 250 and the orifice OL is reduced, control failure and lubrication failure due to filter clogging are suppressed, and the durability of the scroll compressor 100 can be improved.

  At this time, if the first filter 260 located in the uppermost stream is arranged so that the gap is located in the upper part, the lower region on the upstream surface of the first filter 260 is used as a space for storing the contamination CON. Can be used. For this reason, the absolute amount of contamination CON that can be captured by the first filter 260, the second filter 262, and the third filter 264 increases, and the durability of the scroll compressor 100 can be further improved.

  As shown in FIG. 7, the first filter 260, the second filter 262, and the third filter 264 are arranged so that the angle of the portion where the gap is formed is different from the axis of the pressure supply passage L3. You can also Also in this case, similarly to the arrangement shown in FIG. 5, the first filter 260, the second filter 262, and the third filter 264 are arranged so that no gap appears on the cross section of the pressure supply passage L3. ing. In addition, since the effect | action and effect by this arrangement | positioning are the same as that of the arrangement | positioning shown in FIG. Please refer to the above description if necessary.

  Further, as shown in FIG. 8, a fourth filter 266 that covers the entire surface of the pressure supply passage L <b> 3 in the pressure supply passage L <b> 3 located downstream of the first filter 260, the second filter 262, and the third filter 264. Can also be provided. Here, the 4th filter 266 is mentioned as an example of another filter.

  At this time, the fourth filter 266 can have a coarser eye than the first filter 260, the second filter 262, and the third filter 264. If the eyes of the fourth filter 266 are roughened, an increase in lubricating oil flow resistance in the pressure supply passage L3 can be suppressed. Note that most of the contamination CON mixed in the lubricating oil is captured by the first filter 260, the second filter 262, and the third filter 264, so the eyes of the fourth filter 266 are roughened. There is no problem.

  In this way, as shown in FIG. 9, even if there is a contamination CON that could not be captured by the first filter 260, the second filter 262, and the third filter 264, the first filter 260 is located downstream of these. 4 filters 266. Therefore, the absolute amount of the contamination CON introduced into the first pressure 260, the second filter 262, the third filter 264, the back pressure control valve 250 located downstream of the fourth filter 266, the orifice OL, and the like. The occurrence of defects due to contamination CON can be suppressed. As in the prior art, even if the back pressure control valve 250 is provided with a filter, the absolute amount of contamination introduced here is reduced, so that it does not clog in a short time.

  In the embodiment described above, the compressor is assumed to be a scroll compressor, but it may be a reciprocating compressor, a swash plate compressor, a rotary piston compressor, a slide vane compressor, or the like. Further, the oil separator is not limited to the centrifugal separation type, and may be a method of separating the lubricating oil from the gaseous refrigerant through a labyrinth passage, for example.

100 scroll compressor (compressor)
120 Scroll unit (compression mechanism)
166 Drive shaft (compression mechanism)
230 Oil separator 240 Crank mechanism (compression mechanism)
260 First filter 262 Second filter 264 Third filter 266 Fourth filter L3 Pressure supply path (lubricant flow path)
L4 Pressure release passage (lubricant flow passage)

Claims (8)

A compression mechanism for compressing the working fluid;
A plurality of filters disposed at intervals while crossing the filter surface in the direction in which the flow path extends with respect to the flow path of the lubricating oil that lubricates the compression mechanism;
With
The plurality of filters have a gap with the inner wall of the flow path, and the area increases from the upstream to the downstream in the flow direction of the lubricating oil.
Compressor. The plurality of filters are arranged to be staggered with respect to the flow path,
The compressor according to claim 1. The plurality of filters are disposed so that the angle of the portion where the gap is formed is different from the axis of the flow path.
The compressor according to claim 1. The plurality of filters have a portion that overlaps between adjacent filters as seen from the direction along the flow path.
The compressor according to any one of claims 1 to 3. Another filter that covers the entire surface of the flow path is disposed downstream of the plurality of filters.
The compressor according to any one of claims 1 to 4. The another filter is coarser than the plurality of filters,
The compressor according to claim 5. The filter located in the uppermost stream among the plurality of filters has a gap between the inner wall of the flow path at the top,
The compressor according to claim 1. An oil separator for separating the lubricating oil from the working fluid discharged from the compression mechanism;
At least the plurality of filters among the plurality of filters and the other filters are disposed in the flow path located downstream of the oil separator,
The compressor according to any one of claims 1 to 7.