JP4522180B2 - Variable capacity gas compressor - Google Patents

Description

  The present invention relates to, for example, a gas compressor used for compressing refrigerant gas in a cooling device, and more particularly, to a variable capacity gas compressor capable of changing the discharge capacity of compressed refrigerant gas.

  For example, in a gas compressor used for a cooling device, a compression mechanism having a cylinder chamber for compressing a refrigerant gas sucks the refrigerant gas from the suction chamber, compresses the sucked refrigerant gas, and discharges the compressed refrigerant gas. To discharge. In the cooling device, as is well known in the art, air is cooled using compressed refrigerant gas discharged from the discharge chamber of the gas compressor. In the gas compressor, in order for the cooling device to cool the air more efficiently, for example, it is required to change the discharge capacity of the compressed refrigerant gas in order to prevent overcooling by the cooling unit of the cooling device. It has been.

  For this reason, a variable capacity gas compressor has been proposed that can change the volume of the compressed refrigerant gas discharged from the cylinder chamber to the discharge chamber. The variable capacity gas compressor has a communication passage allowing leakage of refrigerant gas from the cylinder chamber to the suction chamber, and an intermittent passage for switching the discharge capacity of the compressed refrigerant gas. The valve device is provided. In the cylinder chamber, a refrigerant gas having a normal capacity is compressed when the communication path is closed by the valve device, and when the communication path is open, the refrigerant starts from a position where the communication path is not provided. As gas compression begins, the volume of refrigerant gas compressed decreases.

In the variable capacity type gas compressor, when the refrigerant gas is mixed into the refrigerant gas compressed by the compression mechanism that operates under supply of lubricating oil and is discharged into the discharge chamber as a valve device that intermittently connects the communication path In addition, there is a type that uses a valve device that operates to interrupt the communication path by introducing the pressure of the lubricating oil separated from the refrigerant gas and stored in the discharge chamber. Such a valve device has a valve body and a valve case for movably holding the valve body, and the rear of the valve body to urge the valve body toward the closed position of the valve body. There is one in which lubricating oil is supplied to a space defined by an end and the valve case, and the space functions as a pressure space (see, for example, Patent Document 1). One end of the compression mechanism and the pressure space can be connected to the discharge chamber in order to take in lubricating oil from the discharge chamber, and a part of the taken-in lubricating oil can be supplied to the compression mechanism and the remainder to the pressure space. The oil is supplied from the discharge chamber through an oil supply path.
Japanese Utility Model Publication No. 57-123991 (page 1-14, Fig. 2)

  However, in the lubricating oil stored in the discharge chamber, for example, foreign matters made of metal powder generated by piping construction for using the variable capacity gas compressor for the cooling device and remaining in the cooling device. May be mixed. If the foreign matter enters, for example, between the valve body of the valve device and the valve case, the valve device may cause a malfunction due to the movement of the valve body being hindered.

  For this reason, for example, it is considered to provide a filter for preventing foreign matter from entering the valve device at a connection point to the discharge chamber, which is an intake port for lubricating oil in the discharge chamber in the oil supply path. It is done. However, the connection point to the discharge chamber in the oil supply path is a shared part of the oil supply path that supplies the compression mechanism and the valve device with the lubricating oil in the discharge chamber, so that the filter is caused by foreign matter. If clogging occurs and the lubricating oil cannot pass through the filter, the lubricating oil cannot be supplied to the compression mechanism. If the lubricating oil is not supplied to the compression mechanism, seizure occurs at the frictional part of the compression mechanism, and the compression mechanism may not be able to operate smoothly.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a variable capacity gas compressor that can prevent foreign matter from entering a valve device that can switch the discharge capacity without disturbing the supply of lubricating oil to the compression mechanism. There is to do.

In order to solve the above-described problem, the variable capacity gas compressor according to claim 1 has a cylinder chamber for compressing the gas, sucks the gas through the suction chamber, and supplies the compressed gas to the discharge chamber. A compression mechanism that operates under the supply of lubricating oil to discharge, a communication path that allows gas to leak from the cylinder chamber to the suction chamber, and the communication path can be intermittent to switch the discharge capacity of the compressed gas. A variable displacement gas compressor comprising a valve device that introduces the pressure of the lubricating oil separated from the compressed gas and stored in the discharge chamber, wherein the lubricating oil is supplied from the discharge chamber to the compression mechanism. A first oil supply passage for supplying, a second oil supply passage for supplying lubricating oil from the discharge chamber to the valve device independently of the first oil supply passage, and a lubricant in the lubricating oil in the discharge chamber. foreign matter through the second oil supply passage to penetrate the valve device It passes through the second oil supply passage from said discharge chamber without positioned in the path of the lubricating oil leading to the compression mechanism through the first oil supply passage from the discharge chamber in order to prevent the said valve device and a filter provided in the lubricating oil passage extending between the first oil supply passage is characterized Rukoto than said second oil supply passage in communication with the discharge chamber below.

  The variable capacity gas compressor according to claim 2 is the variable capacity gas compressor according to claim 1, wherein the filter is provided in the second oil supply path.

  A variable capacity gas compressor according to a third aspect of the present invention is the variable capacity gas compressor according to the first aspect, wherein the filter is provided in the discharge chamber.

  The variable capacity gas compressor according to claim 4 is the variable capacity gas compressor according to any one of claims 1 to 3, wherein the valve device lubricates the discharge chamber to close the communication passage. A first on-off valve mechanism having a pressure space to which oil is supplied via the second oil supply path, and a discharge allowing leakage of lubricating oil in the pressure space to the suction chamber to open the communication path It has a passage and a second on-off valve mechanism for opening and closing the discharge passage in order to connect and disconnect the communication passage.

  In the variable capacity gas compressor according to claim 1, the foreign matter in the lubricating oil accumulated in the discharge chamber passes through the second oil supply path for supplying the lubricating oil in the discharge chamber to the valve device. Since the intrusion into the valve device is prevented by the filter, it is possible to prevent malfunction of the valve device due to the entry of foreign matter into the valve device. In addition, since the first oil supply path for supplying lubricating oil to the compression mechanism is provided independently from the second oil supply path, the compression is performed regardless of clogging by foreign matter in the filter. Lubricating oil can be supplied to the mechanism. In the variable capacity type gas compressor, the filter suppresses the malfunction of the valve device due to foreign matter in the lubricating oil, and the compression is performed even if the filter is clogged by foreign matter and the valve device does not operate. The supply of lubricating oil to the mechanism does not become insufficient, and seizure at the friction point of the compression mechanism can be prevented.

  Further, in the capacity variable type gas compressor according to claim 3, since the filter is provided in the discharge chamber, the filter is provided in comparison with the filter provided in the second oil supply path. It can be formed large. If the filter is formed large, the area of the filtration surface of the filter becomes large. Therefore, even if the filter is clogged with foreign matter contained in the lubricant, the lubricant can pass through the filter. The probability that the passage of the lubricating oil from the discharge chamber to the second oil supply path by the filter, which is clogged by foreign matter contained in the lubricating oil, may be reduced.

  According to the capacity variable type gas compressor according to the present invention, the first oil supply path for supplying the lubricating oil in the discharge chamber to the compression mechanism, and the lubricating oil in the discharge chamber for supplying to the valve device. The second oil supply path is provided independently of each other, and the filter prevents foreign matter from entering the valve device through the second oil supply path. Intrusion of foreign matter into the valve device can be prevented without hindering the supply of. For this reason, in the said valve apparatus, it is prevented that a malfunctioning occurs by the penetration | invasion of a foreign material. In addition, since the lubricating oil in the discharge chamber is supplied to the compression mechanism through the first oil supply path that is independent of the second oil supply path, lubrication is performed regardless of clogging by foreign matter in the filter. Oil is supplied and seizure is prevented from occurring in the compression mechanism due to insufficient supply of lubricating oil.

  The present invention will be described in detail with reference to the embodiment shown in FIGS.

  FIG. 1 shows a cross-sectional view of a variable capacity gas compressor 10 used in a vehicle air conditioner.

  The variable capacity gas compressor 10 is incorporated in, for example, the vehicle air conditioner that performs cooling using the heat of vaporization of the cooling medium, and a condenser, an expansion valve, and an evaporator that are components of the vehicle air conditioner. And the like (not shown) constitute a cooling medium circulation path. The variable capacity gas compressor 10 compresses a gaseous cooling medium, that is, a refrigerant gas taken from the evaporator, and supplies the compressed refrigerant gas to the condenser. The refrigerant gas compressed by the variable capacity gas compressor 10 is liquefied by the condenser and sent to the expansion valve as a high-pressure liquid cooling medium. The high-pressure liquid cooling medium is converted into a low-pressure liquid cooling medium by the expansion valve and sent to the evaporator. The low-pressure liquid cooling medium is vaporized by the evaporator, thereby absorbing heat from the air surrounding the evaporator and cooling the surrounding air.

  The capacity variable type gas compressor 10 is attached to the housing 11 so as to transmit a driving force from a housing 11, a compression mechanism 12 accommodated inside the housing, and a driving source (not shown) to the compression mechanism 12. The transmission mechanism 13 is provided.

  In the illustrated example, the housing 11 includes a housing main body 11a formed of a cylindrical body with one end open, and a front housing member 11b attached so as to cover the open portion 11c of the housing main body.

  The compression mechanism 12 includes a cylinder body 14 that is open at both ends and has a cylindrical shape with an inner wall surface 14 a having an elliptical cross section, a front side block 15 that covers one open end 14 b, and the other opening of the cylinder body 14. And a rear side block 16 covering the end 14c. A cylinder chamber 17 (see FIG. 2) is formed by the cylinder body 14 and the side blocks 15 and 16.

  In the cylinder chamber 17, a rotor 18 having a rotation axis that slidably contacts the inner wall surfaces 15 a and 16 a of both side blocks 15 and 16 and that coincides with the axis of the cylinder body 14 is rotatably arranged. The rotor 18 divides the cylinder chamber 17 into two spaces located symmetrically with respect to the minor axis of the cross section defined by the inner peripheral wall surface 14a of the cylinder body 14 (see FIG. 2). The rotor 18 has a rotation shaft 19 that coincides with the rotation axis of the rotor, and the rotation shaft is supported by a bearing portion 15 b and a bearing portion 16 b formed on both side blocks 15 and 16.

  FIG. 2 shows a cross-sectional view taken along the line II shown in FIG.

  As shown in FIG. 2, the rotor 18 is formed with five slit-like vane grooves 20 at equal intervals in the circumferential direction, and the inner wall surfaces of both side blocks 15 and 16 are formed in the respective vane grooves. A vane 21 in contact with 15a and 16a and fitted in each vane groove 20 is held so as to be able to advance and retreat. Each vane groove 20 is supplied with lubricating oil from a pair of recesses 15c for oil storage formed in the front side block 15 and a pair of recesses 16c (see FIG. 1) formed in the rear side block 16. The two recesses 15c and 16c can communicate with each other.

  Each of the five vanes 21 receives the pressure of the lubricating oil supplied to each vane groove 20 and the centrifugal force acting on each vane 21 by the rotation of the rotor 18, and is attached to the inner peripheral wall surface 14 a of the cylinder body 14. The cylinder chamber 17 is partitioned into five chambers (22) arranged at equal intervals along the circumferential direction on the outer periphery of the rotor 18 by being pressed and abutted against the inner peripheral wall surface. The five chambers (22) each increase or decrease in volume when the rotor 18 rotates under the bias to each vane 21 and the tip of each vane 21 slides on the inner peripheral wall surface 14a of the cylinder body 14. It functions as the compression chamber 22. Each compression chamber 22 increases or decreases in volume in each of the above-mentioned spaces that form a pair in the cylinder chamber 17 described above.

  As shown in FIG. 1, the compression mechanism 12 receives a driving force from a transmission mechanism 13 attached to the front housing member 11b. As is well known in the art, the transmission mechanism 13 includes a pulley 23 and a belt (not shown) around the pulley, and transmits a driving force applied through the pulley to the rotary shaft 19. Then, the rotor 18 is rotated.

  In order to take in the refrigerant gas from the evaporator (not shown) into each compression chamber 22 when the rotor 18 rotates, the front housing member 11b is provided with a suction port (not shown) connected to the evaporator. An annular suction chamber 24 is provided between the front housing member 11 b and the front side block 15 so as to communicate with the suction port and along the outer periphery of the rotary shaft 19 of the rotor 18. The front side block 15 is provided with two suction holes 25 (see FIG. 2) for communicating the suction chamber 24 and the compression chamber 22, and both the suction holes are paired in the cylinder chamber 17. Pairs to accommodate the space.

  The refrigerant gas taken into each compression chamber 22 with the rotation of the rotor 18 is compressed by each compression chamber and becomes a high pressure. In order to discharge the compressed refrigerant gas from each compression chamber 22, a pair of thin portions 14d are formed in a portion of the cylinder body 14 positioned in the short axis direction of the cylinder chamber 17, as shown in FIG. The thin holes are formed with discharge holes 27, respectively. A pair of discharge chambers 26 is defined by the pair of thin portions 14d and the front housing member 11a. Each discharge hole 27 is provided with a discharge valve 28 for controlling the passage of the refrigerant gas from each compression chamber 22 to each discharge chamber 26. The discharge valve opens and closes the discharge hole 27 by the pressure of the refrigerant gas. And a thin plate-like discharge valve body 28a which is bent and deformed, and a valve support 28b which prevents the discharge valve body from being bent more than necessary due to the pressure of the refrigerant gas. The rear side block 16 is provided with a pair of discharge passages 29 corresponding to the discharge chambers 26. Both discharge passages 29 are formed as through holes that penetrate the rear side block 16.

  The high-pressure refrigerant gas compressed in each compression chamber 22 and discharged from both discharge holes 27 to both discharge chambers 26 is attached to the rear side block 16 via both discharge passages 29 and provided with an oil separation portion 30a. , The lubricant contained in the refrigerant gas is separated and stored in the discharge chamber 31. The stored refrigerant gas is supplied to the condenser (not shown) through the discharge port 34. The lubricating oil separated from the refrigerant gas is stored below the discharge chamber 31 in the drawing.

  As is well known in the art, the lubricating oil in the discharge chamber 31 is between the members of the compression mechanism 12 that performs relative motion, for example, the rotating shaft 19 of the rotor 18 and the bearing portions 15b and 16b that support the rotating shaft. In order to facilitate sliding due to their relative motion. As shown in FIG. 1, this lubricating oil has first oil supply passage portions 32a, 32b, 32c formed in the cylinder body 14 and both side blocks 15, 16 due to the high pressure in the discharge chamber 31. The oil is supplied between the members of the compression mechanism 12 through one oil supply path 32. The first oil supply passage 32c formed in the rear side block 16 is open to the discharge chamber 31 at the lower edge of the rear side block 16 (see FIG. 3). A part of the lubricating oil supplied between the members of the compression mechanism 12 goes to the transmission mechanism 13 along the rotation shaft 19. The rotation shaft 19 is provided with a seal mechanism 33 so as to surround the rotation shaft. Therefore, the seal mechanism prevents the lubricating oil from reaching the transmission mechanism 13.

  Further, part of the lubricating oil supplied between the members of the compression mechanism 12 passes between the rotary shaft 19 of the rotor 18 and the bearing portions 15b and 16b that support the rotary shaft, and then the both side blocks 15 and 16. Are supplied to the two recesses 15c and 16c formed respectively. The two recesses 15c and 16c formed in the side blocks 15 and 16 supply oil to the vane grooves 20 as described above.

  Furthermore, in order to change the capacity of the refrigerant gas compressed in each compression chamber 22, one end of the front side block 15 has a circular opening 40 formed on the inner wall surface 15 a of the front side block 15 (see FIG. 2), and a communication passage 41 is provided with the other end connected to the suction chamber 24. As shown in FIG. 2, the communication passage 41 corresponds to each of the above-mentioned spaces that form a pair in the cylinder chamber 17, and is opposed to the elliptical diameter direction defined by the inner peripheral wall surface 14 a of the cylinder body 14. Is formed. In this embodiment, the opening 40 serving as one end of the both communication passages 41 is formed in the inner wall surface 15a of the front side block 15, but the communication passages 41 communicate with the cylinder chamber 17 and the suction chamber 24, respectively. Therefore, it may be provided in any one of the cylinders defining the cylinder chamber 17, that is, both the side blocks 15 and 16 and the cylinder body 14, and the inner wall surface 16 a of the rear side block 16 or the inside of the cylinder body 14 may be provided. It can form in the surrounding wall surface 14a.

  Both openings 40 are provided on the inner wall surface 15 a of the front side block 15 in a region where the vanes 21 slide on the outside of the rotor 18 so that the two communication passages 41 can be connected to the compression chambers 22. When both the communication passages 41 are opened, the refrigerant gas in each compression chamber 22 flows out to the suction chamber 24 through each communication passage 41, so that the sliding vane 21 passes through the opening 40 in each compression chamber 22. The refrigerant gas starts to be compressed from the position. Further, when both communication passages 41 are blocked, the maximum volume of the refrigerant gas is compressed in each compression chamber 22. For this reason, by switching between the two communication paths 41 as will be described later, it is possible to switch the refrigerant gas compressed in each compression chamber 22 for each compression stroke so as to change the capacity.

  Both openings 40 can be provided at various positions in the region where each vane 21 slides according to the desired capacity of the refrigerant gas compressed by each compression chamber 22 when both communicating passages 41 are opened. In the present embodiment, the front side blocks are respectively arranged so that the compression of the refrigerant gas by each compression chamber 22 starts from a position where the volume becomes 30% of the maximum volume of the compression chamber 22 whose volume increases or decreases as the rotor 18 rotates. Fifteen inner wall surfaces 15 a are provided so as to make a pair with respect to the rotation axis of the rotor 18.

  As shown in FIG. 1, the both communication passages 41 are provided with opening / closing valve mechanisms 42 that open and close the respective openings 40 from the outside of the cylinder chamber 17. When the refrigerant gas is compressed with the normal discharge capacity, that is, the maximum volume of the compression chamber 22, the variable opening type gas compressor 10 closes both the openings 40 of both the communication passages 41 by the both on-off valve mechanisms 42.

  Each of the on-off valve mechanisms 42 has a function as a valve body 43, a valve case 44 that holds the valve body movably, and a valve seat 45 that receives the valve body 43, and the valve case 44 can be fitted therein. In order to achieve this, it has a through hole 46 formed in the front side block 15 so that the diameter increases stepwise.

  Both valve bodies 43 can move in the valve case 44 in a direction approaching the opening, that is, in the forward direction, and in a direction away from the opening, that is, in the rear direction, in order to open and close the opening 40 of the corresponding communication passage 41. Both valve bodies 43 are provided with flange portions 43a that can be engaged with the valve seat 45 at the tip portions thereof.

  A pressure space 47 is defined inside the two valve cases 44 by the rear end face of the valve body 43 and the valve case 44 in order to urge the valve body 43 toward the valve seat 45. Both pressure spaces 47 are supplied with lubricating oil from the discharge chamber 31 via the second oil supply passage 48. The second oil supply passage 48 includes a cylinder oil supply passage portion 49 formed in the cylinder body 14, a front oil supply passage portion 50 formed in the front side block 15, and a rear oil supply formed in the rear side block 16. It has a passage 51 and a case oil supply passage 52 provided in both valve cases 44 to be connected to each pressure space 47.

  The rear oil supply passage 51 is lubricated in the first oil supply passage 32 so that the lubricant in the discharge chamber 31 can be taken into the second oil supply passage 48 independently of the first oil supply passage 32. It is provided in the rear side block 16 independently from the first oil supply passage portion 32c serving as an oil intake (see FIG. 3). The rear oil supply passage 51 passes through the rear side block along the axis of the rotary shaft 19 at the lower part of the rear side block 16. The cylinder oil supply passage portion 49 penetrates the cylinder body 14 so as to communicate with the rear oil supply passage portion 51. The cylinder oil supply passage portion 49 is provided independently of the first oil supply passage portion 32 a provided in the cylinder body 14 in the first oil supply passage 32.

  The front oil supply passage portion 50 includes a diameter-enlarged passage portion 52 for accommodating a flow rate adjusting valve 58, which will be described later, an orthogonal passage portion 53 formed in a pair to correspond to both the on-off valve mechanisms 42, A communication passage portion 54 for communicating the orthogonal passage portions with each other. Each orthogonal passage portion 53 has one end connected to the case oil supply passage 52 of each corresponding on-off valve mechanism 42 and the other end opened to the outside of the front side block 15 in the axial direction of the rotary shaft 19. It extends along the direction orthogonal to. One end of the enlarged diameter passage portion 52 is connected to the cylinder oil supply passage portion 49 and the other end is connected to an intermediate position between both ends of the one enlarged diameter passage portion 52. The front oil supply passage portion 50 is provided independently of the first oil supply passage portion 32 b provided in the front side block 15 in the first oil supply passage 32.

  The front housing member 11b has a discharge passage 55 that allows leakage of the lubricating oil in the pressure space 47 to the suction chamber 24 in order to operate the both opening and closing valve mechanisms 42 to shut off both the communication passages 41, and opens and closes the discharge passage. A second on-off valve mechanism (56). In this embodiment, the electromagnetic valve 56 is applied as the second on-off valve mechanism (56).

  The discharge passage 55 has one end connected to the communication passage portion 54 of the front oil supply passage portion 50 in the second oil supply passage 48 and the other end connected to the suction chamber 24. The electromagnetic valve 56 is fitted into the front housing member 11b so as to intermittently connect the discharge passage 55 at an intermediate position.

  The electromagnetic valve 56 includes an electromagnetic valve housing 56a, an electromagnetic valve body 56b that is movably held in the electromagnetic valve housing, and a solenoid coil 56c provided in the electromagnetic valve housing 56a for moving the electromagnetic valve body. And a coil spring 56d for urging the electromagnetic valve body 56b to the closed position of the electromagnetic valve body. The electromagnetic valve 56 opens the discharge passage 55 by applying a voltage to the solenoid coil 56c so that the electromagnetic valve body 56b is pulled up against the urging force of the coil spring 56d. The operation of the electromagnetic valve 56 can be switched, for example, by operating a changeover switch (not shown) provided in the electromagnetic valve.

  The discharge chamber 31 is provided with a filter 57 for preventing foreign matters in the lubricating oil in the discharge chamber from entering the second oil supply path 48. The filter 57 includes a filtration part 57 a having a cylindrical filtration surface and an attachment part 57 b that can be screwed to the rear side block 16. As shown in FIG. 3, the filter 57 is mounted so that the open end of the rear oil supply passage 51 to the discharge chamber 31 is located within the circular cross section of the filtration part 57a when viewed in the axial direction of the rotary shaft 19. The portion 57b is screwed to the rear side block 16 and attached to the rear side block. For this reason, the lubricating oil in the discharge chamber 31 introduced into the second oil supply passage 48 always passes through the filter 57 and is filtered.

  The enlarged diameter passage portion 52 of the front oil supply passage portion 50 is provided with a flow rate adjustment valve 58 urged by a spring 58b in a direction in which the flow rate adjustment valve body 58a is opened. When the flow of the lubricating oil or the refrigerant gas from the discharge chamber 31 to the pressure space 47 or the suction chamber 24 is generated in the enlarged diameter passage portion 52, the flow rate adjustment valve 58 is a push generated in the flow rate adjustment valve body 58a. Depending on the balance between the pressure and the biasing force of the spring 58b, the flow rate in the enlarged diameter passage portion 52 is adjusted or the enlarged diameter passage portion is closed.

  When the variable capacity gas compressor 10 is operated at a normal discharge capacity, that is, when the refrigerant gas compressed from the maximum volume of the compression chamber 22 is discharged, the discharge passage 55 is blocked by the electromagnetic valve 56, and the discharge is performed by this blockage. Lubricating oil having a pressure equal to that of the chamber 31 is supplied to the both pressure spaces 47, and both the openings 40 of both the communication passages 41 are closed by the both on-off valve mechanisms 42 operated under the pressure of the lubricating oil.

  As is well known in the art, in a cooling device, for example, if the evaporator (not shown) as a cooling unit cools the surrounding air too much, water vapor contained in the surrounding air sublimates. It becomes frost, and the cooling effect will reduce because the frost adheres to the evaporator. In order to suppress such a reduction in the cooling effect, the variable displacement gas compressor 10 is switched from an operation with a normal discharge capacity to an operation with a discharge capacity that is lower than the discharge capacity.

  In the variable capacity gas compressor 10, when the operation is switched to reduce the discharge capacity during the operation with the normal discharge capacity, the solenoid valve 56 is operated and the discharge passage 55 is opened. When the discharge passage 55 is opened, the lubricating oil in both the pressure spaces 47 flows out to the suction chamber 24 through both the case oil supply passage portions 52, the two orthogonal passage portions 53, the communication passage portion 54, and the discharge passage 55. Both pressure spaces 47 are equal in pressure to the suction chamber 24. For this reason, the both valve bodies 43 of the both on-off valve mechanisms 42 are moved from the closed position of the valve body 43 to the open position of the valve body by being pushed by the pressure of each compression chamber 22 higher than the suction chamber 24. To do. The two communicating passages 41 are opened by the movement of the valve bodies 43 to the open position. When both the communication passages 41 are opened, as described above, in each compression chamber 22, the compression of the refrigerant gas starts from a volume of 30% of the maximum volume, so the discharge capacity of the capacity variable type gas compressor 10 is It is switched to 30% of its maximum capacity. That is, the discharge amount of the compressed refrigerant gas from the variable capacity gas compressor 10 is switched to 30% of the maximum amount.

  When returning the discharge capacity of the variable capacity type gas compressor 10 to the normal discharge capacity, the solenoid valve 56 is operated to close the discharge passage 55. When the discharge passage 55 is closed, the lubricating oil in the discharge chamber 31 is supplied to the pressure space 47 through the second oil supply passage 48, and both valve bodies 43 of the both on-off valve mechanisms 42 are closed by the pressure of this lubricating oil. Move to position. When the discharge passage 55 is closed and the flow rate adjustment valve 58 is closing the supply passage 54, the flow rate adjustment valve body is caused by the pressure of the lubricating oil leaked from the flow rate adjustment valve 58 and the biasing force of the spring 58b. When 58a moves to the open position, the supply passage 54 is opened, and as described above, both valve bodies 43 move to the closed position. By moving both valve bodies 43 to the closed position, the discharge capacity of the capacity variable type gas compressor 10 returns to the normal discharge capacity again.

  In the variable capacity gas compressor 10, a valve device for connecting and disconnecting both communication passages 41, that is, both on-off valve mechanisms 42, both case oil supply passage portions 52, both orthogonal passage portions 53, communication passage portions 54, and discharge passages. Only the lubricating oil filtered through the filter 57 is taken into the second oil supply passage 48 for supplying the lubricating oil in the discharge chamber 31 to 55 and the electromagnetic valve 56. For this reason, piping construction for incorporating the variable capacity gas compressor 10 into the vehicle air conditioner, for example, foreign matter made of metal powder generated by connecting the evaporator and the variable capacity gas compressor 10 is generated. Intrusion between the valve body 43 and the valve case 44 of the both opening / closing valve mechanisms 42 is prevented. Further, since foreign matter is prevented from entering other parts constituting the valve device, that is, both the case oil supply passage 52, the two orthogonal passage portions 53, the communication passage portion 54, the discharge passage 55, and the electromagnetic valve 56, The malfunction of the valve device due to the entry of foreign matter into the valve device for connecting and disconnecting both communication passages 41 is prevented.

  In the variable capacity gas compressor 10, the first oil supply path 32 for supplying the lubricating oil in the discharge chamber 31 to the compression mechanism 12 is formed independently of the second oil supply path 48. The lubricating oil is supplied to the compression mechanism 12 regardless of the clogging of the filter 57.

  In the variable capacity gas compressor 10, even if the filter 57 that suppresses the malfunction of the valve device due to foreign matter in the lubricating oil is clogged with foreign matter, the lubricating oil passes through the filter due to this clogging. The first oil supply path 32 is provided independently of the second oil supply path 48 even if the valve device does not operate due to the supply stop of the lubricating oil through the second oil supply path 48. Therefore, the supply of lubricating oil to the compression mechanism 12 does not become insufficient, and seizure between the frictional portions of the compression mechanism, that is, between the members that perform relative motion is prevented.

  In the variable capacity gas compressor 10, the open end to the discharge chamber 31 of the first oil supply passage portion 32 c that serves as a lubricant intake port for the discharge chamber 31 in the first oil supply passage 32 is the second oil. The rear oil supply passage 51 serving as a lubricating oil intake port of the discharge chamber 31 in the supply passage 48 is provided below the open end to the discharge chamber 31. For this reason, even if an unforeseen situation occurs and the amount of lubricating oil stored in the discharge chamber 31 is reduced, and the lubricating oil cannot be supplied to the valve device via the second oil supply path 48, the lubrication of the discharge chamber 31 is performed. Unless the oil runs out, lubricating oil can be supplied to the compression mechanism 12.

  Therefore, according to the capacity variable type gas compressor 10 according to the present invention, it is possible to prevent foreign matter from entering the valve device that can switch the discharge capacity without disturbing the supply of the lubricating oil to the compression mechanism 12. be able to.

  In the above-described embodiment, the filter 57 is provided in the discharge chamber 31. However, since it is only necessary to prevent foreign matter in the lubricating oil from entering the valve device, for example, in the second oil supply path 48. Can be provided. However, when the filter 57 is provided in the discharge chamber 31, it is possible to increase the area of the filtration surface as compared with the case where the filter 57 is provided in the second oil supply path 48. When the area of the filtration surface is increased, the probability that the passage of the lubricating oil through the filter 57 is blocked by clogging with foreign substances can be reduced. Therefore, the filter 57 is provided in the discharge chamber 31 as in the above-described embodiment. desirable.

  In the above example, an example is shown in which the present invention is applied to a concentric rotor type compressor in which the rotor 18 is provided so as to have an axis of rotation on the axis of the cylindrical cylinder body 14 having an elliptical inner shape. For example, the present invention may be applied to an eccentric rotor type compressor in which a rotor is disposed so as to have a rotation axis that is different from the axis of the cylinder inside a cylindrical cylinder that has a circular inner shape. However, the present invention is not limited to the examples.

1 is a cross-sectional view showing a variable capacity gas compressor 10 according to the present invention. It is sectional drawing obtained along the II line | wire shown in FIG. It is sectional drawing obtained along the II-II line | wire shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Variable capacity type gas compressor 12 Compression mechanism 17 Cylinder chamber 25 Suction chamber 29 Discharge chamber 32 First oil supply path 41 Communication path 42 (Opening and closing valve mechanism) 47 Pressure space 48 Second oil supply path 52 (constituting valve device) Case oil supply passage portion 53 (constituting valve device) orthogonal passage portion 54 (constituting valve device) communication passage portion 55 (constituting valve device) discharge passage 56 (valve device) Comprising solenoid valve 57 filter

Claims (4)

A compression chamber that has a cylinder chamber for compressing gas, operates under supply of lubricating oil to suck the compressed gas through the suction chamber and discharge the compressed gas to the discharge chamber, and from the cylinder chamber to the suction chamber The pressure of the lubricating oil separated from the compressed gas and stored in the discharge chamber is introduced to enable the intermittent passage of the communication path in order to switch the discharge capacity of the compressed gas and the communication path allowing the gas leakage. A variable capacity gas compressor comprising a valve device,
A first oil supply passage for supplying lubricating oil from the discharge chamber to the compression mechanism, and a second oil supply for supplying lubricating oil from the discharge chamber to the valve device independently of the first oil supply passage road and said to foreign matter in the lubricating oil in the discharge chamber the second through the oil supply passage from said said discharge chamber to prevent from entering the valve device first oil supply channel through by said compression mechanism and a filter provided in the lubricating oil passage leading to no said from the discharge chamber through the second oil supply passage valve device be located in the path of the lubricating oil reaching the,
The first oil supply passage, a variable displacement gas compressor, wherein Rukoto than said second oil supply passage in communication with the discharge chamber below.   The variable capacity gas compressor according to claim 1, wherein the filter is provided in the second oil supply path.   The variable capacity gas compressor according to claim 1, wherein the filter is provided in the discharge chamber.   The valve device opens the communication path with a first on-off valve mechanism having a pressure space to which lubricating oil in the discharge chamber is supplied via the second oil supply path in order to close the communication path. Therefore, a discharge passage that allows leakage of the lubricating oil in the pressure space to the suction chamber and a second on-off valve mechanism that opens and closes the discharge passage to connect and disconnect the communication passage are provided. The capacity variable type gas compressor according to any one of claims 1 to 3.

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