EP1120568A2 - Gasverdichter - Google Patents

Gasverdichter Download PDF

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Publication number
EP1120568A2
EP1120568A2 EP01201412A EP01201412A EP1120568A2 EP 1120568 A2 EP1120568 A2 EP 1120568A2 EP 01201412 A EP01201412 A EP 01201412A EP 01201412 A EP01201412 A EP 01201412A EP 1120568 A2 EP1120568 A2 EP 1120568A2
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EP
European Patent Office
Prior art keywords
compressor
oil
passage
oil passage
compression
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.)
Granted
Application number
EP01201412A
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English (en)
French (fr)
Other versions
EP1120568B1 (de
EP1120568A3 (de
Inventor
Makoto c/o Seiko Seiki Kabushiki Kaisha Ijiri
Tatsuhiro c/o Seiko Seiki K.K. Tohyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Marelli Corp
Original Assignee
Seiko Seiki KK
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Filing date
Publication date
Priority claimed from JP8033952A external-priority patent/JP2913155B2/ja
Application filed by Seiko Seiki KK filed Critical Seiko Seiki KK
Publication of EP1120568A2 publication Critical patent/EP1120568A2/de
Publication of EP1120568A3 publication Critical patent/EP1120568A3/de
Application granted granted Critical
Publication of EP1120568B1 publication Critical patent/EP1120568B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F04C29/021—Control systems for the circulation of the lubricant

Definitions

  • the present invention relates to a gas compressor which is used in, for example, a car air-conditioner. More particularly, the invention concerns a gas compressor which is adapted to prevent the occurrence of inconveniences due to oil compression at a time of restarting the operation, such as an increase in the starting torque.
  • the main body 3 of the compressor has between a front-side block 4 and a rear-side block 5 a cylinder 6 whose inner periphery is substantially elliptical, a rotor 8 being rotatably laid laterally within a cylinder chamber 7 defined by the both side blocks 4, 5 and the cylinder 6.
  • the rotor 8 has integrally formed thereon a rotor shaft 8a which passes through end faces.
  • the rotor shaft 8a is supported by an F bearing 4a of the front-side block 4 and by an R bearig 5a of the rear-side block 5.
  • the rotor 8 has formed therein slit-like vanes grooves 9, 9, --- in its radial direction. Vanes 10, 10, --- are mounted in the vane grooves 9, 9, --- in such a way as to freely advance and retreat.
  • the vanes 10, 10, --- are urged against the inner wall side of the cylinder by the centrifugal force and the oil pressure at the bottom of the vane grooves.
  • the high pressure refrigerant gas after having been compressed is discharged into a discharge chamber 16 through discharge ports 13, 13, --- discharge valves 14, 14, discharge communication passage 19, oil separator 15, etc.
  • the oil separator 15 separates an oil portion from the high pressure refrigerant gas, the thus separated oil portion being pooled at the bottom of the discharge chamber 16, thereby forming an oil pool 17 in which lubricating oil is pooled.
  • the lubricating oil in the oil pool 17 is pressure supplied to sliding portions such as the F bearing 4a and R bearing 5a through an oil passage 18.
  • This pressure supply of the lubricating oil is effected by the high/low pressure difference between the suction chamber 12 or compression chamber 11 and the discharge chamber 16, i.e., the low pressure portion and the high pressure portion.
  • the lubricating oil that has been supplied to the sliding portion flows finally into the suction chamber 12 that constitutes the low pressure portion and thereafter becomes mist in the low pressure refrigerant gas of the suction chamber 12 and is sucked into the main body 3 of the compressor wherein the thus sucked oil mist is again compressed together with the refrigerant gas.
  • the present invention has been made under the above-mentioned circumstances and an object thereof is to provide a gas compressor which prevents the occurrence of inconveniences resulting from the oil compression at a time of restarting the operation of the compressor, such as an increase in the starting torque.
  • a gas compressor which comprises a suction chamber having a low pressure refrigerant gas introduced thereinto, a main body of the compressor equipped with a compression chamber for sucking the low pressure refrigerant gas of the suction chamber and compressing it, a discharge chamber into which a high pressure refrigerant gas after having been compressed is discharged from the main body of the compressor, an oil pool on which the pressure of the discharge chamber acts, and an oil passage having an inflow opening to the oil pool and an outflow opening open to sliding portions of the main body of the compressor, whereby a lubricating oil is supplied due to a high/low pressure difference between the suction chamber or compression chamber and the discharge chamber from the oil pool to the sliding portions of the main body of the compressor through the oil passage, and in which the oil passage is provided with oil passage opening/closing means that opens the oil passage in interlocking relationship with a compression starting operation of the main body of the compressor and closes the oil passage in inter
  • a gas compressor which comprises a suction chamber having a low pressure refrigerant gas introduced thereinto, a main body of the compressor equipped with a compression chamber for sucking the low pressure refrigerant gas of the suction chamber and compressing it, a discharge chamber into which a high pressure refrigerant gas after having been_compressed is discharged from the main body of the compressor, an oil pool on which the pressure of the discharge chamber acts, and an oil passage having an inflow opening open to the oil pool and an outflow opening open to sliding portions of the main body of the compressor, whereby a lubricating oil is supplied due to a high/low pressure difference between the suction chamber or compression chamber and the discharge chamber from the oil pool to the sliding portions of the main body of the compressor through the oil passage, and in which the gas compressor is provided with pressure difference eliminating means which when stopping the compression operation of the main body of the compressor releases the high pressure refrigerant gas of the discharge chamber to the suction chamber side to thereby eliminate a
  • a gas compressor which comprises a suction chamber having a low pressure refrigerant gas introduced thereinto, a main body of the compressor equipped with a compression chamber for sucking the low pressure refrigerant gas of the suction chamber and compressing it, a discharge chamber into which a high pressure refrigerant gas after having been compressed is discharged from the main body of the compressor, an oil pool on which the pressure of the discharge chamber acts, and an oil passage having an inflow opening open to the oil pool and an outflow opening open to sliding portions of the main body of the compressor, whereby a lubricating oil is supplied due to a high/low pressure difference between the suction chamber or compression chamber and the discharge chamber from the oil pool to the sliding portions of the main body of the compressor through the oil passage, and in which the gas compressor is equipped with oil passage opening/closing means that is provided in the oil passage and that opens the oil passage in interlocking relationship with a compression starting operation of the main body of the compressor and closes the oil
  • a gas compressor in which the oil passage opening/closing means comprises a valve chest provided midway in the oil passage and an oil passage opening/closing valve element that is slidably disposed within the valve chest and that, after the start of the compression operation of the main body of the compressor, is slid by a discharged jet flow of the high pressure refrigerant gas from the main body of the compressor to thereby open the oil passage and that, after the stoppage of the compression operation, is slid by an urging force of urging means composed of a spring or the like to thereby close the oil passage.
  • a gas compressor which further comprises an electromagnetic clutch that transmits and interrupts a power needed for performance of the compression operation according to the ON and OFF operations thereof, and in which the oil passage opening/closing means is constituted by an oil passage electromagnetic valve that opens and closes the oil passage according to the ON and OFF operations of the electromagnetic clutch.
  • a gas compressor in which the pressure difference eliminating means comprises a communication passage that is opened at one end to the suction chamber and opened at the other end to the discharge chamber, a valve chest that is so provided as to intersect the communication passage, and a communication passage opening/closing valve element that is slidably disposed within the valve chest and that, after the start of the compression operation of the main body of the compressor, is slid by a discharged jet flow of the high pressure refrigerant gas from the main body of the compressor to thereby close the communication passage and that, after the stoppage of the compression operation, is slid by an urging force of urging means composed of a spring or the like to thereby open the communication passage.
  • a gas compressor which further comprises an electromagnetic clutch that transmits and interrupts a power needed for performance of the compression operation according to the ON and OFF operations thereof, and in which the pressure difference eliminating means comprises a communication passage that is opened at one end to the suction chamber and opened at the other end to the discharge chamber, and a communication passage electromagnetic valve that opens and closes the communication passage according to the ON and OFF operations of the electromagnetic clutch.
  • a gas compressor in which a unified means-of the oil passage opening/closing means and the pressure difference eliminating means comprises a communication passage that is opened at one end to the suction chamber and opened at the other end to the discharge chamber, a two-passage communication valve chest that is so provided as to intersect the communication passage and the oil passage, and a two-passage dual purpose valve element that is slidably disposed within the two-passage communication valve chest and that, after the start of the compression operation of the main body of the compressor, is slid by a discharged jet flow of the high pressure refrigerant gas from the main body of the compressor to thereby open the oil passage and close the communication passage and that, after the stoppage of the compression operation, is slid by an urging force of urging means composed of a spring or the like to thereby close the oil passage and open the communication passage.
  • a gas compressor which comprises an electromagnetic clutch that transmits a power needed for performance of the compression operation to the main body side of the compressor according to the ON operation thereof and interrupts the transmission of this power according to the OFF operation thereof, and in which a unified means of the oil passage opening/closing means and the pressure difference eliminating means comprises a communication passage that is opened at one end to the suction chamber and opened at the other end to the discharge chamber, and a two-passage dual purpose electromagnetic valve that according to the ON operation of the electromagnetic clutch opens the oil passage and closes the communication passage and that according to the OFF operation thereof closes the oil passage and opens the communication passage.
  • the oil passage opening/closing means closes the oil passage interlockingly therewith. Accordingly, when the compression operation stops, even if there exists the residual high/low pressure difference between the suction compression chamber and the discharge chamber, it does not happen that during this period of time the lubricating oil is supplied due to the high/low pressure difference from the oil pool to the suction or compression chamber side through the oil passage and sliding portions. As a result, the flow of the lubricating oil into the suction or compression chamber during the stoppage of the compression operation is prevented.
  • the high/low pressure difference between the suction chamber and the discharge chamber is eliminated by the pressure difference eliminating means, with the result that the flow of the lubricating oil into the suction chamber or compression chamber side due to such high/low pressure difference is stopped.
  • the oil passage becomes closed interlockingly therewith and at this time simultaneously the high pressure refrigerant gas that remains to exist in the discharge chamber is released into the suction chamber, whereby the high/low pressure difference between the discharge chamber and the suction or compression chamber is eliminated.
  • the basic construction of the gas compressor such as that the main body 3 of the compressor when the rotor 8 rotates and as a result the volume of the compression chamber space portions 11, 11, --- varies, the suction of the low pressure refrigerant gas from the suction chamber 12 into the main body 3 of the compressor and the compression thereof within this main body 3 are effected by the volume variation and after compression the high pressure refrigerant gas is discharged into the discharge chamber 16 through the discharge valves 14, 14 and oil separator 15, that the oil separator 15 separates the oil portion from the high pressure refrigerant gas and the thus separated oil portion pools at the bottom portion of the discharge chamber 16 whereupon the oil pool 17 is formed, that the lubricating oil in the oil pool 17 is forcedly supplied to the sliding portions such as the F bearing 4a, R bearing 5a, etc.
  • this gas compressor has midway in the oil passage 18 an oil passage opening/closing valve element 20 that serves as oil passage opening/closing means (a) therefor.
  • This valve element 20 is slidably disposed within a valve chest 21 that is provided midway in the oil passage 18.
  • the valve chest 21 is so formed as to intersect the oil passage 18.
  • a trunk portion 200 of the valve element 20 has a constricted portion 201 formed in a part thereof.
  • this valve element 20 is slid whereby this constricted portion 201 and the oil passage 18 positionally coincide with each other, the oil passage 18 is opened.
  • the constricted portion 201 gets off from this position of coincidence, the oil passage 18 is closed.
  • the oil passage opening/closing valve element 20 is built in near the discharge valve 14 on the rear-side block side 5.
  • An end face (pressure receiving surface) 20a of the valve element 20 is caused to face a discharge communication passage for making communication between the discharge valve 14 and the discharge chamber 16 (refer to Fig. 3) and it is arranged for the high pressure refrigerant gas at a time immediately after having been discharged from the discharge valve 14 to act directly on this end face 20a as a discharged jet flow thereof.
  • the valve element 20 is urged toward a position where it opens the oil passage 18.
  • a spring 22 is disposed as urging means and by the force of this spring 22 the valve element 20 is urged toward a position where it closes the oil passage 18.
  • valve element 20 When the discharged jet flow acts on the end face 20a of the valve element 20, the valve element 20 is slid against the force of the spring 22 by the dynamic pressure thereof, whereupon the constricted portion 201 and the oil passage 18 positionally coincide with each other, with the result that the oil passage 18 is opened.
  • the oil passage opening/closing valve element 20 is slid interlockingly with the compression starting operation and, during a time period from immediately after the start of the compression to the stoppage thereof, opens the oil passage 18.
  • the oil passage opening/closing valve element 20 is slid interlockingly with the compression stopping operation and, during a time period from immediately after the stoppage of the compression operation to the start thereof, closes the oil passage 18.
  • the high pressure refrigerant gas that has been compressed by the main body 3 of the compressor immediately thereafter acts directly on the end face 20a of the valve element 20 from the discharge valve 14.
  • the valve element 20 is slid against the force of the spring 22, whereby the oil passage 18 is opened.
  • the high pressure refrigerant gas that has acted on the end face 20a of the valve element 20 is thereafter discharged into the discharge chamber 16 through the discharge communication passage 19, oil separator 15, etc.
  • the oil separator 15 separates the oil portion from the high pressure refrigerant gas and the thus separated oil portion pools at the bottom of the discharge chamber 16, whereby the oil pool 17 for the lubricating oil is formed (refer to Fig. 17).
  • the lubricating oil in the oil pool 17 which has been pooled as mentioned above is forcedly supplied to the sliding portions such as the F bearing 4a, R bearing 5a, etc. through the oil passage 18 due to the high/low pressure difference between each of the suction chamber 12 and compression chamber 11 and the discharge chamber 16 (refer to Fig. 4).
  • the gas compressor of the above-mentioned embodiment is that which is provided with the oil passage opening/closing valve element 20 that closes the oil passage 18 interlockingly with the compression stopping operation. For this reason, when the compression operation is stopped, during even a time period in which the high/low pressure difference remains to exist between each of the suction chamber 12 and compression chamber 11 and the discharge chamber 16 it does not happen that due to the high/low pressure difference the lubricating oil is supplied from the oil pool 17 to the suction chamber and compression chamber 11 side through the oil passage 18 and the sliding portions (F bearing 4a, R bearing 5a, etc.). That is, during the stoppage of the compression operation, it is possible to prevent the flow of the lubricating oil into the suction chamber 12 and compression chamber 11.
  • the lubricating oil that is sucked from the suction chamber 12 to the main body 3 side of the compressor as it is in a liquid state as well as the lubricating oil within the compression chamber 11 is decreased to the largest possible extent. Accordingly, the oil compression in the main body 3 of the compressor when starting the compressor ceases to occur, with the result that it is possible to restart the compression operation with a small starting torque, decrease the shock at the starting time that results from the oil compression, etc.
  • Fig. 5 illustrates another embodiment of the present invention. Since the basic construction of the gas compressor illustrated in this figure is the same as that in the above-mentioned embodiment, the same components as those therein are denoted by the same reference numerals and a detailed description thereof is omitted.
  • the gas compressor illustrated in the figure is provided with a communication passage 23 as means (pressure difference eliminating means (b)) for, when the compression operation of the main body 3 of the compressor is stopped, eliminating the high/low pressure difference between the suction chamber 12 and the discharge chamber 16.
  • the communication passage 23 has one end open to the suction chamber 12 and the other end open to the discharge chamber 16 and is provided in such a way as to communicate from the suction chamber 12 to the discharge chamber 16 through the front-side block 4, cylinder 6 and rear-side block 5.
  • a communication passage opening/closing valve element 24 is provided midway in the communication passage 23 and this valve element 24 is disposed in the vicinity of the discharge valve 14 on the rear-side block 5 side (refer to Fig. 7).
  • valve element 24 is slidably disposed within the valve chest 21 that is so provided as to intersect the communication passage 23 and a trunk portion 240 of the valve element has a constricted portion 241 formed in a part thereof.
  • valve element 24 When the valve element 24 is slid and the constricted portion 241 of the trunk portion 240 thereof intersects or positionally coincides with the communication passage 23, this communication passage 23 is opened. When the constricted portion 241 gets off from this position of coincidence, the communication passage 23 is closed.
  • the end face (pressure receiving surface) 24a of the valve element 24 is so provided as to face the discharge communication passage 19 (refer to Fig. 9) that connects the discharge valve 14 and the discharge chamber 16 and to cause the high pressure refrigerant gas at a time immediately after having been discharged from the discharge valve 14 to act directly thereon as a discharged jet flow.
  • the valve element 24 is urged toward a position where it closes the communication passage 23 (refer to Fig. 7).
  • the spring 22 is disposed as urging means and, by the force of this spring 22, the valve element 24 is urged toward a position where it opens the communication passage 23 (refer to Fig. 8).
  • valve element 24 When the discharged jet flow of gas acts on the end face 24a of the valve element 24, the valve element 24 is slid against the force of the spring 22 by the dynamic pressure thereof, with the result that the position of the constricted portion 241 of the trunk portion 240 of the valve element in coincidence with the communication passage 23 gets off from the position that corresponds thereto. As a result, the communication passage 23 is closed.
  • valve element 24 When the discharged jet flow with respect to the end face 24a of the valve element is stopped, the valve element 24 is slid by the force of the spring 22 whereby the constricted portion 241 of the trunk portion 240 of the valve element and the communication passage 23 positionally coincide with each other, with the result that the communication passage 23 is opened.
  • the communication passage opening/closing valve element 24 is slid interlockingly with the compression starting operation and, during a time period from immediately after the start of the compression to the stoppage of the compression, closes the communication passage 23. Also, when the main body 3 of the compressor stops its compression and as a result the high pressure refrigerant gas ceases to be discharged, the communication passage opening/closing valve element 24 is slid interlockingly with the compression stopping operation and, during a time period from immediately after the stoppage of the compression operation to the start thereof, opens the communication passage 23.
  • the high pressure refrigerant gas that has acted on the end face 24a is thereafter discharged into the discharge chamber 16 through the discharge communication passage 19, oil separator 15, etc.
  • the oil separator 15 separates the oil portion from the high pressure refrigerant gas and the thus separated oil portion pools at the bottom of the discharge chamber 16, whereby the oil pool 17 for the lubricating oil is formed.
  • the lubricating oil in the oil pool 17 is forcedly supplied to the sliding portions such as the F bearing 4a, R bearing 5a, etc. through the oil passage 18 due to the high/low pressure difference between the suction chamber 12 and the discharge chamber 16.
  • This embodiment is the same as the above-mentioned embodiment in this respect (refer to Figs. 4 and 5).
  • the communication passage 23 is opened immediately thereafter, whereby the high/low pressure difference between the discharge chamber 16 and the suction chamber 12 is forcedly eliminated.
  • the lubricating oil is prevented from being supplied due to such high/low pressure difference from the oil pool 17 to the suction chamber 12 and compression chamber 11 side through the oil passage 18 and sliding portions (F bearing 4a, R bearing 5a, etc.), whereby the flow of the lubricating oil into the suction chamber 12 and compression chamber 11 is prevented. Accordingly, the unnecessary lubricating oil which when restarting the compression operation is sucked from the suction chamber 12 to the main body 3 side of the compressor and the unnecessary lubricating oil which is within the compression chamber 11 are decreased to the largest possible extent.
  • the gas compressor according to this embodiment is constructed such that when the compression operation of the main body 3 of the compressor 3 is stopped, the high pressure refrigerant gas that remains to exist in the discharge chamber 16 is released into the suction chamber 12 by the pressure difference eliminating means (b) that is constituted by the communication passage 23 and communication passage opening/closing valve element 24 to thereby make zero the high/low pressure difference between the discharge chamber 16 and the suction chamber 12 or compression chamber 11.For this reason, immediately after the stoppage of the compression operation, the pressure of the discharge chamber 16 and that of the suction chamber 12 or compression chamber 11 become equalized with each other, with the result that the flow of the lubricating oil into the suction chamber 12 and compression chamber 11 side due to such high/low pressure difference is prevented.
  • the unnecessary lubricating oil which when restarting the compression operation is sucked as is in a liquid state from the suction chamber 12 to the main body 3 side of the compressor and the unnecessary lubricating oil which is within the compression chamber 11 are decreased to the largest possible extent.
  • no oil compression occurs in the main body 3 of the compressor at the starting time, and the restarting of the compression operation with a small starting torque, the decrease in the shock at the starting time that results from the oil compression, etc. can be achieved.
  • the gas compressor according to each of the above-mentioned embodiments is of the type equipped with either one of the oil passage opening/closing means (a) and the pressure difference eliminating means (b), from the standpoint of reliably preventing the oil compression in the main body 3 of the compressor at the starting time and the occurrence of the resulting inconveniences (the increase in the starting torque, the increase in the shock occurring at the starting time, etc.), it is also possible to provide the gas compressor with both the oil passage opening/closing means (a) and the pressure difference eliminating means (b).
  • the oil passage opening/closing means (a) and the pressure difference eliminating means (b) may be provided individually independently, it is also possible to construct the both means into a single unified structure as illustrated in Fig. 10, namely to construct the both means (a) and (b) by the communication passage 23, two-passage communication valve chest 25 and two-passage dual purpose valve element 26.
  • the two-passage communication valve chest 25 is provided so as to intersect each of the communication passage 23 and oil passage 18, whereby the two-passage dual purpose valve element 26 is slidably disposed within the two-passage communication valve chest 25.
  • the two-passage dual purpose valve element 26 has the constricted portion 261 formed in the trunk portion 260 of its valve element.
  • the end face (pressure receiving surface) 26a of the two-passage dual purpose valve element 26 is provided so as to face the discharge communication passage 19 that connects the discharge valve 14 and the valve chamber 16 and to cause the high pressure refrigerant gas at a time immediately after having been discharged from the discharge valve 14 to act directly thereon as a discharged jet flow.
  • the two-passage dual purpose valve element 26 is urged toward a position where it closes the communication passage 23 and opens the oil passage 18 (refer to Fig. 11).
  • the spring 22 is disposed as urging means and, by the force of this spring 22, the two-passage dual purpose valve element 26 is urged toward a position where it opens the communication passage 23 and closes the oil passage 18 (refer to Fig. 12).
  • the two-passage dual purpose valve element 26 is slid by the force of the spring 22, whereby the position of the constricted portion 261 of the trunk portion 260 thereof in coincidence with the oil passage 18 gets off from the position thereof, with the result that the oil passage 18 is closed. Also, at this time, the constricted portion 261 of the trunk portion 260 of the valve element arrives at a position of its coinciding with the communication passage 23, whereby the communication passage 23 is opened.
  • the two-passage dual purpose valve element 25 is slid interlockingly with this compression starting operation and, during a time period from immediately after the start of the compression operation to the stoppage of the compression, opens the oil passage 18 and closes the communication passage 23. Also, when the main body 3 of the compressor stops its compression and as a result the high pressure refrigerant gas ceases to be discharged, the two-passage dual purpose valve element 25 is slid interlockingly with the compression stopping operation and, during a time period from immediately after the stop of the compression operation to the start of the compression operation, closes the oil passage 18 and opens the communication passage 23.
  • the gas compressor is provided with the oil passage opening/closing means (a) and pressure difference eliminating means (b) in a form wherein the both means (a) and (b) are constructed into a single unified structure and where although the both means are not constructed into one unified structure the gas compressor is provided with the both means, when the compression operation has been stopped, the oil passage 18 becomes closed interlockingly therewith. Simultaneously, the high pressure refrigerant gas that remains to exist in the discharge chamber 16 is released through the communication passage 23 into the suction chamber 12. As a result, the high/low pressure difference between the discharge chamber 16 and the suction chamber 12 or compression chamber 11 is eliminated.
  • an electromagnetic valve 30 for use in the oil passage such as that illustrated in Fig. 13 can also be applied in place of the oil passage opening/closing valve element 20.
  • the oil passage electromagnetic valve 30 illustrated in this figure is constructed so as to open and close the oil passage 18 interlockingly with the ON/OFF operations of an electromagnetic clutch 40 (refer to Fig. 5).
  • the electromagnetic clutch 40 transmits through its ON operation a power (power needed for rotation of the rotor 8) needed for performance of the compression operation from a power source (not illustrated) such as an engine to the main body 3 of the compressor and, when performing its OFF operation, interrupts transmission of the power to the main body 3 side of the compressor.
  • a power source not illustrated
  • the oil passage electromagnetic valve 30 has a coil 30a on its outer periphery and it is arranged for a clutch current to flow into the coil 30a according to the ON/OFF operations of the electromagnetic clutch 40.
  • a communication passage electromagnetic valve 31 can also be applied in place of the communication passage opening/closing valve element 24 as illustrated in Fig. 14.
  • the communication passage electromagnetic valve 31 illustrated in this figure is constructed so as to open and close the communication passage 23 interlockingly with the ON and OFF operations of the electromagnetic clutch 40 (refer to Fig. 5).
  • the concrete construction of the electromagnetic clutch 40 that is, the construction thereof that the electromagnetic clutch 40 transmits through its ON operation a power (power needed for rotation of the rotor 8) needed for performance of the compression operation from a power source (not illustrated) such as an engine to the main body 3 of the compressor and, when performing its OFF operation, interrupts transmission of the power to the main body 3 side of the compressor, is the same as in the above-mentioned embodiment.
  • the communication passage electromagnetic valve 31 has a coil 31a on its outer periphery and it is arranged for a clutch current to flow into the coil 31a according to the ON/OFF operations of the electromagnetic clutch 40.
  • the two-passage dual purpose valve element 26 has been used when unifying the oil passage opening/closing means (a) and pressure difference eliminating means (b) into a single structure, it is also possible to use as such a single structure in place of the valve element 26 a two-passage dual purpose electromagnetic valve 32 such as that illustrated in Fig. 15.
  • the two-passage dual purpose electromagnetic valve 32 illustrated in the figure is constructed such that the valve 32 opens the oil passage 18 and closes the communication passage 23 interlockingly with the ON operation of the electromagnetic clutch 40 (refer to Fig. 5) while, on the other hand, the valve 32 closes the oil passage 18 and opens the communication passage 23 interlockingly with the OFF operation of the electromagnetic clutch 40.
  • the concrete construction of the electromagnetic clutch 40 is the same as in the above-mentioned embodiment and therefore a detailed explanation is omitted.
  • the two-passage dual purpose electromagnetic valve 32 has a coil 32a on its outer periphery and it is arranged for a clutch current to flow in the coil 32a according to the ON and OFF operation of the electromagnetic clutch 40.
  • each of these electromagnetic valves 30, 31 and 32 is not operated by the jet flow of discharged high pressure refrigerant gas unlike the oil passage opening/closing valve element 20 or the like but operated by the clutch current. Therefore, it is not needed to cause a jet flow of discharged high pressure refrigerant gas to act on the end face thereof.
  • the oil compression occurs due to the oil which has been pooled mainly within the compression chamber whose pressure has been decreased when the compression is out of operation.
  • the lubricating oil flows on one hand into a rotor bearing portion (a) of the front-side block side and flows on the other hand into a high pressure supply hole (c) that communicates the oil passage 18 with the vane back pressure chamber 9a at the rotor bearing portion (b) of the rear-side block side and in the vicinity thereof.
  • this lubricating oil is also introduced into the compression chamber 11 by way of the rotor 8, side clearance between the rear-side block and the vanes 10, and vane slit clearance.
  • the high pressure supply hole (c) is provided for the purpose of increasing the vane back pressure during the compressor operation.
  • the oil flowrate ratio among the rotor bearing portion (a), rotor bearing portion (b) and high pressure supply hole (c) is 1 : 1 : 3400 (where it is assumed that the oil flowrate in the rotor bearing portion (a) be 1). As understood, in the high pressure supply hole (c) the oil is the easiest to flow.
  • the oil passage opening/closing valve element 20 is installed at a portion (A) which is the inlet portion of the oil passage 18 at which the oil enters thereinto from the oil pool 17, it can completely serve its purpose.
  • the valve element 20 since even mere closing of only the high pressure supply hole (c) which is high in the oil flowrate can sufficiently serve the purpose, the valve element 20 may be installed at a portion (B) of the oil passage 18 which communicates with the high pressure supply hole (c).
  • oil passage opening/closing means (a) which is constructed such that the oil passage 18 is opened and closed by the trunk portion 200 of the valve element 20, regarding this oil passage opening/closing means (a) it may also be arranged to open and close the oil passage 18 by the end face 20a of the valve element 20 as illustrated in Fig. 17.
  • the oil passage opening/closing means (a) illustrated in Fig. 17 has the valve element 20 within a valve chest 21 provided midway in the oil passage 18, and the end face 20a of the valve element 20 opposes an inlet/outlet 18a, 18b of the valve chest 21 with respect to the oil passage 18 and this end face 20a is formed into a size which enables closure of the outlet 18b of the valve chest 21.
  • a pressure receiving portion 202 is formed on the end face 20a of the valve element 20 in such a way as to protrude therefrom and this pressure receiving portion 202 is caused to face the discharge communication passage 19 (refer to Fig. 3) which communicates the discharge valve 14 with the discharge chamber 16, whereby it is arranged to cause the high pressure refrigerant gas which is immediately after having been discharged from the discharge valve 14 to act directly thereon as a discharged jet flow of the gas.
  • valve element 20 is arranged to cause the discharge jet flow of high pressure refrigerant gas to act on the end face 20a of the valve element through the pressure receiving portion 202, with the result that the valve element 20 is urged by the dynamic pressure of such discharged jet flow in such a direction as to cause the end face 20a thereof to part away from the outlet 18b of the valve chest of the oil passage 18b of the valve chest of the oil passage 18 (in such a direction as to make the oil passage 18 open).
  • valve element 20 there is disposed the spring 22 as urging means.
  • the valve element 20 is urged in such a direction as to cause the end face 20a thereof to abut against the outlet 18b of the valve chest of the oil passage 18 (in such a direction as to make the oil passage 18 close).
  • valve element 20 When the discharged jet flow of the gas has acted on the pressure receiving portion 202 of the valve element 20, as illustrated in Fig. 17(b) the valve element 20 is caused by the dynamic pressure thereof to slide against the force of the spring 22, whereby the end face 20a of the valve element parts away from the outlet 18b of the valve chest of the oil passage 18. As a result, this oil passage 18 is opened.
  • the passage opening/closing means which makes the oil passage close interlockingly with the compression stopping operation. For this reason, when the compression operation has been stopped, in even a case where there exists a residual high/low pressure difference between the discharge chamber and suction chamber or compression chamber, there occurs no supply of the lubricating oil from the oil pool to the suction chamber and compression chamber side through the oil passage and sliding portions due to such high/low pressure difference. Therefore, it is possible to prevent the flow of the lubricating oil into the suction chamber and compression chamber side during the stoppage of the compression operation.
  • the present invention is arranged when the compression operation of the main body of the compressor has been stopped to release the high pressure refrigerant gas that remains to exist in the discharge chamber into the suction chamber by the pressure difference eliminating means, to thereby zero the high/low pressure difference between the discharge chamber and the suction or compression chamber. For this reason, immediately after the stoppage of the compression operation, the pressure of the discharge chamber and the pressure of the suction or compression chamber become equalized with each other, with the result that the flow of the lubricating oil to the suction and compression chamber side due to such high/low pressure difference is prevented.
  • the two means which are the passage opening/closing means and the pressure difference eliminating means, whereby it is arranged when the compression operation has been stopped to make the oil passage close interlockingly with the stoppage and at this time simultaneously to release the high pressure refrigerant gas that remains to exist within the discharge chamber into the suction chamber and thereby zero the high/low pressure difference between the discharge chamber and the suction chamber and compression chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP01201412A 1995-09-01 1996-08-30 Gasverdichter Expired - Lifetime EP1120568B1 (de)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP22532595 1995-09-01
JP22532595 1995-09-01
JP24982995 1995-09-27
JP24982995 1995-09-27
JP3395296 1996-02-21
JP8033952A JP2913155B2 (ja) 1995-09-01 1996-02-21 気体圧縮機
EP96306330A EP0761975B1 (de) 1995-09-01 1996-08-30 Gasverdichter

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP96306330A Division EP0761975B1 (de) 1995-09-01 1996-08-30 Gasverdichter

Publications (3)

Publication Number Publication Date
EP1120568A2 true EP1120568A2 (de) 2001-08-01
EP1120568A3 EP1120568A3 (de) 2001-08-29
EP1120568B1 EP1120568B1 (de) 2004-10-13

Family

ID=30773286

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01201412A Expired - Lifetime EP1120568B1 (de) 1995-09-01 1996-08-30 Gasverdichter

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Country Link
EP (1) EP1120568B1 (de)
DE (2) DE69633644T2 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8628317B2 (en) 2006-04-10 2014-01-14 Wabco Automotive Uk Limited Vacuum pump with an axial oil feed conduit
US9683570B2 (en) 2011-08-17 2017-06-20 Wabco Automotive Uk Limited Vacuum pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2235251A (en) * 1939-10-25 1941-03-18 Wagner Electric Corp Compressor unloading valve mechanism
FR2218491A1 (de) * 1973-02-20 1974-09-13 Bauer Kompressoren
EP0044530A1 (de) * 1980-07-23 1982-01-27 COMPAGNIE INDUSTRIELLE DES TELECOMMUNICATIONS CIT-ALCATEL S.A. dite: Elektrisches Pumpenaggregat mit Flügelkolben und Öldichtung
JPS59180095A (ja) * 1983-03-30 1984-10-12 Toyoda Autom Loom Works Ltd 圧縮機における潤滑油の供給過剰防止機構

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2235251A (en) * 1939-10-25 1941-03-18 Wagner Electric Corp Compressor unloading valve mechanism
FR2218491A1 (de) * 1973-02-20 1974-09-13 Bauer Kompressoren
EP0044530A1 (de) * 1980-07-23 1982-01-27 COMPAGNIE INDUSTRIELLE DES TELECOMMUNICATIONS CIT-ALCATEL S.A. dite: Elektrisches Pumpenaggregat mit Flügelkolben und Öldichtung
JPS59180095A (ja) * 1983-03-30 1984-10-12 Toyoda Autom Loom Works Ltd 圧縮機における潤滑油の供給過剰防止機構

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 009, no. 038 (M-358), 19 February 1985 (1985-02-19) & JP 59 180095 A (TOYODA JIDO SHOKKI SEISAKUSHO KK), 12 October 1984 (1984-10-12) *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8628317B2 (en) 2006-04-10 2014-01-14 Wabco Automotive Uk Limited Vacuum pump with an axial oil feed conduit
US9683570B2 (en) 2011-08-17 2017-06-20 Wabco Automotive Uk Limited Vacuum pump
US10371148B2 (en) 2011-08-17 2019-08-06 Wabco Automotive Uk Limited Vacuum pump

Also Published As

Publication number Publication date
EP1120568B1 (de) 2004-10-13
DE69633644T2 (de) 2005-02-17
DE69631310T2 (de) 2004-07-01
DE69633644D1 (de) 2004-11-18
EP1120568A3 (de) 2001-08-29
DE69631310D1 (de) 2004-02-19

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