WO2007046351A1 - 両頭ピストン式圧縮機 - Google Patents
両頭ピストン式圧縮機 Download PDFInfo
- Publication number
- WO2007046351A1 WO2007046351A1 PCT/JP2006/320612 JP2006320612W WO2007046351A1 WO 2007046351 A1 WO2007046351 A1 WO 2007046351A1 JP 2006320612 W JP2006320612 W JP 2006320612W WO 2007046351 A1 WO2007046351 A1 WO 2007046351A1
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- WIPO (PCT)
- Prior art keywords
- compression chamber
- refrigerant
- suction
- chamber
- valve
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
- F04B27/1018—Cylindrical distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/12—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having plural sets of cylinders or pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1073—Adaptations or arrangements of distribution members the members being reed valves
- F04B39/108—Adaptations or arrangements of distribution members the members being reed valves circular reed valves
Definitions
- the present invention relates to a double-headed piston compressor.
- a double-headed piston type compressor described in Patent Document 1 is used as a compressor for vehicle air conditioning of a vehicle.
- a cylinder block of this type of compressor has a plurality of cylinder bores for accommodating double-headed pistons.
- a swash plate that moves together with the rotating shaft reciprocates the double-headed piston within the cylinder bore.
- the double-headed piston type compressor has a compression chamber defined on both sides of the double-headed piston in each cylinder bore.
- the double-head piston compresses the refrigerant sucked into the compression chamber and discharges the compressed refrigerant to the outside of the compression chamber.
- Patent Document 1 discloses a compressor that employs a rotary valve as a refrigerant suction structure into each compression chamber, and a compressor that employs a suction valve as a refrigerant suction structure into each compression chamber.
- Patent Document 1 Japanese Patent Laid-Open No. 5-312146
- An object of the present invention is to provide a double-headed piston type compressor that can reduce the pulsation of the compressor, suppress the generation of noise, and contribute to silence.
- the present invention provides a double-headed piston compressor including a front housing, a rear housing, and a cylinder block provided between the front housing and the rear housing.
- the cylinder block has a plurality of cylinder bores.
- Front housing The rear housing and the cylinder block define a swash plate chamber.
- the compressor defines a suction pressure region.
- the double-headed pistons slidably fitted in the plurality of cylinder bores define a compression chamber on the front housing side and a compression chamber on the rear housing side.
- One of the compression chambers is a first compression chamber, and the other is a second compression chamber.
- the compressor includes a rotating shaft that is rotatably supported in the cylinder block, and a swash plate that rotates together with the rotating shaft in the swash plate chamber.
- the swash plate reciprocates the double-headed piston in the cylinder bore.
- the structure for sucking the refrigerant into the first compression chamber is a rotary valve having an introduction passage for introducing the refrigerant into the first compression chamber.
- the structure for sucking the refrigerant into the second compression chamber is a suction valve that opens and closes due to a differential pressure between the suction pressure region and the second compression chamber.
- FIG. 1 is a cross-sectional view showing a double-headed piston compressor according to a first embodiment that embodies the present invention.
- FIG. 2 is a characteristic diagram showing suction pulsation in the compressor shown in FIG. 1 and a conventional compressor.
- FIG. 3 is an enlarged cross-sectional view showing a main part of another double-headed piston compressor of the present invention.
- FIG. 4 is a cross-sectional view showing a double-headed piston compressor according to a second embodiment of the present invention.
- FIG. 5 is a sectional view showing a double-headed piston compressor according to a third embodiment of the present invention.
- FIG. 6 is a sectional view showing a double-headed piston compressor according to a fourth embodiment of the present invention.
- FIG. 7 is a sectional view showing a double-headed piston compressor according to a fifth embodiment of the present invention.
- FIG. 1 shows a cross-sectional view of a double-headed piston compressor (hereinafter simply referred to as “compressor”) 10 according to a first embodiment. 1 and 4 to 7, the left side is the front side of the compressor 10, and the right side is the rear side of the compressor 10.
- the overall know-how of the compressor 10 includes a front cylinder block 11 on the front side (left side in FIG. 1), a front housing 13 joined to the front cylinder block 11, A rear cylinder block 12 on the rear side (right side in FIG. 1) and a rear housing 14 joined to the rear cylinder block 12 are included.
- the cylinder blocks 11 and 12 are joined together.
- FIG. 1 shows only one bolt through hole BH and one bolt B threaded through the bolt through hole BH.
- Each bolt B is threaded through a plurality of (for example, five) bolt through holes BH formed in the cylinder blocks 11, 12, the front housing 13 and the rear housing 14.
- the threaded portion N formed at the tip of the bolt B is screwed into the rear housing 14.
- the diameter of each bolt through hole BH is larger than the diameter of bolt B.
- the front housing 13 is divided into a front discharge chamber 13a and a front suction chamber 13b.
- the front suction chamber 13b is connected to the bolt through hole BH through a communication path R1 formed in the front housing 13.
- the rear housing 14 is divided into a rear discharge chamber 14a and a rear suction chamber 14b.
- a suction hole P penetrating the inner peripheral surface of the front cylinder block 11 is formed on the outer peripheral surface of the front cylinder block 11.
- An external refrigerant circuit disposed outside the compressor 10 is connected to the suction hole P.
- a discharge hole (not shown) penetrating the inner peripheral surface of the front cylinder block 11 is formed on the outer peripheral surface of the front cylinder block 11. The external refrigerant circuit is connected to the discharge hole.
- the external refrigerant circuit connects the discharge pressure region of the compressor 10 to the suction pressure region.
- the external refrigerant circuit includes a capacitor (condenser), an expansion valve (expansion valve), and an evaporator (evaporator). The condenser, the expansion valve, and the evaporator are sequentially arranged from the discharge pressure region of the compressor 10 on the external refrigerant circuit.
- the front valve plate 15 has a front discharge port 15a formed at a position corresponding to the front discharge chamber 13a, and a front suction port 15b formed at a position corresponding to the front suction chamber 13b.
- the discharge flap plate 16 has a front discharge valve 16a formed at a position corresponding to the front discharge port 15a.
- the front discharge valve 16a which is a flap valve, opens and closes the front discharge port 15a.
- the valve dimension of the front discharge valve 16a formed on the discharge flap plate 16 is set to dimension X.
- the valve dimension means a dimension from the root of the front discharge valve 16a, which is pressed by a partition wall defining the front discharge chamber 13a in the front housing 13, to the tip of the front discharge valve 16a.
- the front retainer plate 17 is formed with a front discharge retainer 17a that regulates the opening degree of the front discharge valve 16a.
- the suction flap plate 18 has a flap valve 18a formed at a position corresponding to the front suction port 15b.
- the flap valve 18a opens and closes the front suction port 15b.
- the front cylinder block 11 has a notch 11c formed so as to correspond to the flap valve 18a, and the wall surface of the notch 11c functions as a front suction retainer that regulates the opening degree of the flap valve 18a.
- a valve plate 19, a discharge flap plate 20, and a retainer forming plate 21 are disposed between the rear housing 14 and the rear cylinder block 12.
- a discharge port 19a is formed in the valve plate 19 at a position corresponding to the discharge chamber 14a.
- the discharge flap plate 20 is formed with a shear discharge valve 20a at a position corresponding to the discharge port 19a.
- the flap discharge valve 20a opens and closes the discharge port 19a.
- the dimension of the discharge valve 20a formed on the discharge flap plate 20 is set to the dimension X.
- the valve dimension means a dimension from the root of the discharger valve 20a, which is held by the partition wall that defines the discharge chamber 14a in the rear housing 14, to the tip of the discharger valve 20a.
- valve dimension (dimension X) of the front discharge valve 16a and the valve dimension (dimension X) of the rear discharge valve 20a are set to the same valve dimension. That is, the discharge flap plates 16 and 20 have the same configuration, and discharge valves 16a and 20a having the same valve dimensions are formed on the discharge flap plates 16 and 20, respectively. Further, the retainer forming plate 21 is formed with a retainer 21a that regulates the opening degree of the discharger discharge valve 20a.
- a rotating shaft 22 is rotatably supported on the cylinder blocks 11, 12. rotation The shaft 22 is passed through shaft holes 11 a and 12 a that are provided through the cylinder blocks 11 and 12. The rotating shaft 22 is passed through a through hole 15c formed in the center of the front valve plate 15. The outer peripheral surface of the rotary shaft 22 and the inner peripheral surface of the through hole 15c constitute a sliding portion of the rotary shaft 22. The rotary shaft 22 is directly supported by the cylinder blocks 11 and 12 through the shaft holes 11a and 12a.
- a lip seal type shaft seal device 23 is disposed between the front housing 13 and the rotary shaft 22. The shaft seal device 23 is accommodated in a seal accommodation chamber 13 c formed in the front housing 13. The front discharge chamber 13a and the front suction chamber 13b are provided around the seal housing chamber 13c.
- a swash plate 24 cooperating with the rotary shaft 22 is fixed to the rotary shaft 22.
- the swash plate 24 is disposed in a swash plate chamber 25 defined between the cylinder blocks 11 and 12.
- a thrust bearing 26 is disposed between the end face of the front cylinder block 11 and the annular base 24a of the swash plate 24.
- a thrust bearing 27 is disposed between the end face of the rear cylinder block 12 and the base 24a of the swash plate 24. The thrust bearings 26 and 27 restrict the movement of the rotary shaft 22 along the center line L direction with the swash plate 24 interposed therebetween.
- the front cylinder block 11 has a plurality of front cylinder bores 28 (five in this embodiment; only one front cylinder bore 28 is shown in FIG. 1) so as to be arranged around the rotary shaft 22. ing.
- the rear cylinder block 12 is formed with a plurality of rear cylinder bores 29 (five in this embodiment; only one rear cylinder bore 29 is shown in FIG. 1) so as to be arranged around the rotary shaft 22. .
- a double-headed piston 30 as a double-headed piston is accommodated in the cylinder bores 28 and 29 which are paired in the front and rear. Cylinder blocks 11 and 12 constitute a cylinder for double-headed piston 30.
- the rear cylinder block 12 and the rear housing 14 are formed with a communication path R2 that communicates the swash plate chamber 25 with the rear suction chamber 14b.
- the swash plate 24 rotates integrally with the rotating shaft 22 by co-operating with the rotating shaft 22.
- the rotational movement of the swash plate 24 is transmitted to the double-headed piston 30 through a pair of shrouds 31 provided with the swash plate 24 interposed therebetween.
- the double-headed piston 30 reciprocates back and forth within the cylinder bores 28 and 29.
- a front compression chamber 28a as a compression chamber and a rear compression chamber 29a as a second compression chamber are partitioned.
- Seal peripheral surfaces l ib and 12 b are formed on the inner peripheral surfaces of the shaft holes 11a and 12a through which the rotary shaft 22 passes.
- the rotary shaft 22 is directly supported by the cylinder blocks 11 and 12 via the seal peripheral surfaces l ib and 12b.
- a suction hole P and a bolt through hole BH are opened in the swash plate chamber 25 of the compressor 10.
- a supply passage 22a as an introduction passage is formed in the rotary shaft 22.
- the supply passage 22a is a hole-like passage that is perforated on the end surface on the rear housing 14 side of the rotary shaft 22 that is a solid shaft. For this reason, one end of the supply passage 22a is open to the rear suction chamber 14b in the rear housing 14.
- a communication passage 32 is formed at a position corresponding to the rear cylinder block 12 on the rotary shaft 22 so as to communicate with the supply passage 22a.
- the opening on the outer peripheral surface side of the rotary shaft 22 in the communication path 32 functions as an outlet 32 b of the communication path 32.
- the rear cylinder block 12 has a plurality of suction passages 33 (five in this embodiment, only one suction passage 33 is shown in FIG. 1) so as to communicate the rear cylinder bore 29 with the shaft hole 12a. ing.
- the suction passage 33 has an inlet 33a that opens onto the seal peripheral surface 12b and an outlet 33b that opens toward the rear compression chamber 29a.
- the outlet 32b of the communication passage 32 communicates intermittently with the inlet 33a of each suction passage 33.
- the portion of the rotary shaft 22 surrounded by the seal peripheral surface 12b functions as a rotary valve 35 formed integrally with the rotary shaft 22.
- the refrigerant (gas) suction structure into the front compression chamber 28a is different from the refrigerant suction structure into the rear compression chamber 29a.
- the refrigerant suction structure to the front compression chamber 28a includes a flap valve 18a disposed between the front suction chamber 13b and the front compression chamber 28a.
- the flap valve 18a is opened and closed by the differential pressure between the front suction chamber 13b and the front compression chamber 28a.
- the refrigerant suction structure into the rear compression chamber 29a includes a rotary valve 35 disposed between the rear suction chamber 14b and the rear compression chamber 29a.
- the rotary valve 35 has a supply passage 22a for introducing the refrigerant (gas) from the front suction chamber 13b into the rear compression chamber 29a.
- a compression chamber into which refrigerant is drawn by the rotary valve 35 is referred to as a first compression chamber
- a compression chamber into which refrigerant is drawn through the flap valve 18a is referred to as a second compression chamber.
- the front compression chamber 28a is the second compression chamber
- the rear compression chamber 29a is the first compression chamber.
- the refrigerant in the external refrigerant circuit is sucked into the swash plate chamber 25 through the suction hole P, and then passes through the bolt through hole BH and the communication path R1 to the front suction in the front housing 13. Reach chamber 13b.
- the refrigerant in the front suction chamber 13b which functions as a suction pressure region, passes through the flap valve 18a from the front suction port 15b due to the differential pressure generated between the front suction chamber 13b and the front compression chamber 28a (front cylinder bore 28). It is pushed away and sucked into the front compression chamber 28a.
- the refrigerant in the front compression chamber 28a is discharged from the front discharge port 15a to the front discharge port.
- the valve 16a is pushed away and discharged to the front discharge chamber 13a that functions as a discharge pressure region.
- the refrigerant discharged to the front discharge chamber 13a flows out from the discharge hole to the external refrigerant circuit through a communication path (not shown).
- lubricating oil is put in the compressor 10 and a refrigerant circulation circuit that is an external refrigerant circuit force, and this lubricating oil flows together with the refrigerant.
- the refrigerant in the rear suction chamber 14b that functions as a suction pressure region is sucked into the rear compression chamber 29a of the rear cylinder bore 29 through the supply passage 22a, the communication passage 32, and the suction passage 33 by the action of the rotary valve 35.
- the refrigerant in the rear compression chamber 29a Is discharged to the discharge chamber 14a that functions as a discharge pressure area. Is done.
- the refrigerant discharged into the discharger chamber 14a flows out from the discharge hole to the external refrigerant circuit through a communication path (not shown).
- FIG. 2 shows the measurement results of the suction pulsation of the compressor in two types of experimental devices related to the refrigerant circulation circuit including the double-head piston compressor and the external connection circuit. That is, FIG. 2 shows the measurement results of the compressor suction pulsation in the present apparatus A1 that obtains the characteristics of the broken line “A1”, and the measurement results of the compressor suction pulsation in the conventional apparatus A2 that obtains the characteristics of the solid line “A2”. Show.
- the compressor in the present apparatus A1 includes a refrigerant suction structure including a flap valve and a refrigerant suction structure including a rotary valve force, like the compressor 10 of the first embodiment.
- the compressor in the conventional apparatus A2 includes a refrigerant suction structure that also has a flap valve force on both sides, like the conventional compressor.
- the present apparatus A1 and the conventional apparatus A2 are different from each other only in the refrigerant suction structure of the compressor, and other configurations, for example, the configuration of the external refrigerant circuit, are set to the same conditions.
- FIG. 2 shows suction pulsation in a specific frequency band in a range of 500 to 2000 rpm, which is a low rotational speed region for the rotational speed NC of the compressor.
- the rotation speed region is set as a region of the rotation speed NC where the self-excited vibration of the intake valve is generated and the sound generated by the vibration can be strange to people in the vehicle.
- the self-excited vibration of the flap valve that functions as the intake valve occurs, the vibration is transmitted to the evaporator through the pipe, thereby generating a sound that shakes the pipe or the evaporator.
- the specific frequency band is 400 ⁇ : LOOOHz, and this value is set as the resonance frequency region of the evaporator used in the external refrigerant circuit.
- the inhalation pulsation of the apparatus A1 is reduced in comparison with the inhalation pulsation of the conventional apparatus A2 in the entire frequency band of 400 to 1000 Hz.
- the quietness was achieved by reducing the suction pulsation in the compressor 10 as a whole.
- the reduction rate of the suction pulsation was the largest at “700 Hz” where the suction pulsation of the conventional device A2 peaked.
- the reduction rate of inhalation pulsation at “700Hz” in Device A1 reached approximately “90%” when the peak value of inhalation pulsation in conventional device A2 was set to “100%”. Also conventional The reduction rate of the inhalation pulsation of this device Al with respect to device A2 was mostly over 50% in the 400 to 1000 Hz frequency band.
- the refrigerant suction structure into the front compression chamber 28a is a flap valve 18a
- the refrigerant suction structure into the rear compression chamber 29a is a rotary valve 35.
- the flap valve 18a and the rotary valve 35 behave differently from each other during refrigerant suction due to structural differences. That is, since the flap valve 18a has a structure that opens and closes due to a differential pressure, when the refrigerant is sucked into the front compression chamber 28a, the flap valve 18a may be delayed in opening or closing.
- the rotary valve 35 is provided on the rotary shaft 22 and cooperates with the rotary shaft 22.
- the supply passage 22a communicates with the rear compression chamber 29a, so that the refrigerant is forcibly sucked into the rear compression chamber 29a. Due to such a difference in behavior, a phase difference is generated between the suction timing to the front compression chamber 28a and the suction timing to the rear compression chamber 29a. Therefore, the amount of suction into the front compression chamber 28a is smaller than the amount of suction into the rear compression chamber 29a.
- the refrigerant density in the front compression chamber 28a after finishing the suction stroke is smaller than the refrigerant density in the rear compression chamber 29a after finishing the suction stroke. Therefore, when shifting from the suction stroke to the discharge stroke, a phase difference occurs between the discharge timing of the front compression chamber 28a and the discharge timing of the rear compression chamber 29a. That is, there is a phase difference between the discharge timing from the front compression chamber 28a to the front discharge chamber 13a and the discharge timing from the rear compression chamber 29a to the rear discharge chamber 14a.
- the discharge timing from the front compression chamber 28a to the front discharge chamber 13a is later than the discharge timing from the rear compression chamber 29a to the rear discharge chamber 14a.
- the refrigerant suction structure into the front compression chamber 28a and the refrigerant suction structure into the rear compression chamber 29a are both configured as flap valves or both as rotary valves.
- the refrigerant suction structure into the front compression chamber 28a and the refrigerant suction structure into the rear compression chamber 29a exhibit the same behavior (operation) during refrigerant suction. Therefore, the suction timing to the front compression chamber 28a and the There is no phase difference with the inhalation timing.
- the present embodiment has the following advantages.
- the refrigerant suction structure into the front compression chamber 28a is different from the refrigerant suction structure into the rear compression chamber 29a.
- the refrigerant suction structure on the front compression chamber 28a side is the flap valve 18a
- the refrigerant suction structure on the rear compression chamber 29a side is the rotary valve 35.
- the suction hole P connected to the external refrigerant circuit is provided in the cylinder block 11.
- the refrigerant is supplied to the front compression chamber 28a and the rear compression chamber 29a via the swash plate chamber 25.
- the refrigerant is also distributed and supplied to the front compression chamber 28a and the rear compression chamber 29a by the central force of the compressor 10, and a reduction in suction efficiency can be suppressed. That is, the suction efficiency into any one of the compression chambers 28a and 29a is not reduced.
- the supply passage 22 a of the rotary valve 35 is a hole-like passage that opens at the end of the rotary shaft 22. For this reason, the refrigerant can be supplied to the rotary valve 35 through the opening end of the rotary shaft 22, and the refrigerant suction efficiency can be improved. That is, the supply passage 22a always communicates with the rear suction chamber 14b, and always rotates at a fixed location, so that it is easy to supply the cooling medium.
- a rotary valve 35 having a hole-like passage is provided on the rear housing 14 side.
- the hole-like passage is not provided in the rotation shaft 22 so that the rear housing 14 side force also extends to the front housing 13 side. I do not get. For this reason, the strength of the rotating shaft 22 is weakened.
- the rotary valve 35 in the form of a hole-like passage is provided on the rear housing 14 side as in the present embodiment, the rear housing 14 on the rotary shaft 22 It is only necessary to provide a hole-like passage only on a part of the side. For this reason, in the present embodiment, a decrease in the strength of the rotary shaft 22 can be suppressed. That is, this embodiment is advantageous in terms of securing the strength of the rotating shaft 22 and ease of force.
- the rotary valve 35 is provided on the rear housing 14 side.
- this embodiment can easily secure the refrigerant suction passage for the rotary valve.
- the supply passage 22a functions as a refrigerant suction passage for the rotary valve 35.
- providing the rotary valve 35 on the rear housing 14 side is advantageous in terms of the load as compared to the case where the rotary valve 35 is provided on the front housing 13 side where the load such as twisting and bending increases. It is. That is, when the rotary valve 35 is provided on the front housing 13 side, the rotary valve (35) and the cylinder block (11, 12) are affected by the load as compared to the case where the rotary valve 35 is provided on the rear housing 14 side. There is an increased risk of slight deformation. The deformation may cause a gap between the rotary valve (35) and the cylinder block (11, 12).
- the deformation may cause refrigerant leakage between the plurality of suction passages (33) that communicate the cylinder bores (28, 29) with the shaft holes (11a, 12a).
- the suction efficiency of the rotary valve (35) may be reduced, leading to a reduction in the efficiency of the compressor. Therefore, in the present embodiment in which the rotary valve 35 is provided on the rear housing 14 side, deformation of the rotary valve 35 and the rear cylinder block 12 can be suppressed. As a result, a reduction in the suction efficiency of the rotary valve 35 can be suppressed, and further a reduction in the efficiency of the compressor can be suppressed.
- the rotary valve 35 is provided on the side of the rear housing 14, and the rear housing 14 is formed with a rear suction chamber 14 b that is always in communication with the rotary valve 35. For this reason, the refrigerant can be stored in the rear suction chamber 14b. That is, the refrigerant can be easily sucked into the rotary valve 35 and has a structure! / Speak.
- the valve dimensions of the front discharge valve 16a are set to be the same as those of the rear discharge valve 20a. Thereby, the discharge structures on both sides of the compressor 10 can be made the same structure, and an increase in manufacturing cost can be suppressed.
- a second embodiment of the present invention will be described with reference to FIG. In each of the embodiments described below, the same reference numerals are given to the same configurations as those of the already described embodiments, and redundant descriptions are omitted or simplified.
- the valve dimension b of the discharge valve 20a in the discharge flap plate 20 is set larger than the valve dimension a of the front discharge valve 16a in the discharge flap plate 16. (A b). That is, the valve size of the front discharge valve 16a in the front discharge chamber 13a is different from the valve size of the shear discharge valve 20a in the rear discharge chamber 14a. Since the front discharge valve 16a has a different valve dimension than the rear discharge valve 20a, the front discharge valve 16a has a different rigidity from the rear discharge valve 20a. Therefore, the front discharge valve 16a and the rear discharge valve 20a have different behaviors when opening and closing.
- This embodiment has the following advantages in addition to the advantages (1) to (6) of the first embodiment.
- the valve size of the front discharge valve 16a for discharging the refrigerant sucked through the flap valve 18a is different from the valve size of the rear discharge valve 2Oa for discharging the refrigerant sucked through the rotary valve 35. For this reason, when the refrigerant is discharged from the front compression chamber 28a and the rear compression chamber 29a, the discharge valves 16a and 20a behave differently, and a phase difference occurs in the discharge timing. Therefore, the discharge pulsation of the compressor 10 can be further reduced.
- the refrigerant suction structure to the front compression chamber 28a is the flap valve 18a in the compressor 10 of the present embodiment, and the refrigerant suction structure to the rear compression chamber 29a. Is a rotary valve 35.
- the passage structure for supplying the refrigerant to the rear compression chamber 29a via the rotary valve 35 is different from the first and second embodiments.
- the passage structure of this embodiment will be mainly described.
- a supply passage 22b as an introduction passage is formed in the rotary shaft 22.
- the supply passage 22b in this state includes a hole-like passage portion 36 and a groove-like passage portion 37 connected to the hole-like passage portion 36.
- the hole-shaped passage portion 36 is formed by drilling the end surface of the rotary shaft 22 that is a solid shaft.
- the groove-shaped passage portion 37 is formed by grooving the outer peripheral surface of the rotary shaft 22.
- the communication path R3 is formed so that the swash plate chamber 25 in the rear cylinder block 12 communicates with the shaft hole 12a.
- the groove-like passage portion 37 is formed so that the suction passage 33 in the rear cylinder block 12 communicates with the communication passage R3.
- the compressor 10 of the present embodiment includes the refrigerant suction structure including the flap valve 18a and the refrigerant suction structure including the rotary valve 35, the compressor 10 operates in the same manner as the compressor 10 of the first and second embodiments. obtain.
- the present embodiment has the same advantages as the advantages (1), (2), (5), (6) of the first embodiment and the advantages (8) of the second embodiment. In addition, the following advantages can be obtained.
- the supply passage 22 b of the rotary valve 35 is a combination of a hole-like passage portion 36 and a groove-like passage portion 37. For this reason, the refrigerant suction volume into the rotary valve 35 can be increased.
- the refrigerant suction structure into the front compression chamber 28a is the rotary valve 49
- the refrigerant suction structure into the rear compression chamber 29a is the flap valve 46a.
- the two refrigerant suction structures in the compressor 10 of the present embodiment are opposite to the first to third embodiments.
- the compression chamber into which the refrigerant is sucked by the rotary valve 49 is referred to as a first compression chamber
- the compression chamber into which the refrigerant is sucked in by the flap valve 46a is referred to as a second compression chamber.
- the front compression chamber 28a is the first compression chamber
- the rear compression chamber 29a is the second compression chamber.
- the rear housing 14 is formed with a rear discharge chamber 14a and a rear suction chamber 14b.
- a valve plate 40, a discharge flap plate 41, and a retainer forming plate 42 are arranged between the front housing 13 and the front cylinder block 11.
- a front discharge port 40a is formed in the valve plate 40 at a position corresponding to the front discharge chamber 13a.
- the discharge flap plate 41 is formed with a front discharge valve 41a at a position corresponding to the front discharge port 40a.
- the retainer forming plate 42 is formed with a retainer 42a that regulates the opening degree of the front discharge valve 41a.
- a valve plate 43, a discharge flap plate 44, a retainer forming plate 45, and a suction flap plate 46 are arranged between the rear housing 14 and the rear cylinder block 12.
- the valve plate 43 has a carrier discharge port 43a formed at a position corresponding to the carrier discharge chamber 14a, and a carrier suction port 43b formed at a position corresponding to the carrier suction chamber 14b.
- the discharge flap plate 44 has a shear discharge valve 44a formed at a position corresponding to the shear discharge port 43a.
- the valve dimension c of the front discharge valve 41a is set larger than the valve dimension d of the rear discharge valve 44a (c> d).
- the retainer forming plate 45 is formed with a retainer 45a that regulates the opening degree of the discharger discharge valve 44a.
- the suction flap plate 46 has a flap valve 46a formed at a position corresponding to the rear suction port 43b.
- the flap valve 46a opens and closes the rear suction port 43b.
- the rear cylinder block 12 has a notch 12c formed so as to correspond to the flap valve 46a. Cut off The wall surface of the notch 12c functions as a rear suction retainer that regulates the opening of the flap valve 46a.
- a supply passage 47 as an introduction passage is formed in the rotary shaft 22.
- the supply passage 47 in this embodiment is a groove-like passage formed by applying a groove force to the outer peripheral surface of the rotary shaft 22 that is a solid shaft.
- One end of the supply passage 47 opens into a seal accommodation chamber 13c in which the shaft seal device 23 is accommodated.
- the front cylinder block 11 has a plurality of suction passages 48 (five in this embodiment, only one suction passage 48 is shown in FIG. 6) so that the front cylinder bore 28 communicates with the shaft hole 1 la. Being!
- the inlet 48 a of the suction passage 48 opens at a position corresponding to the supply passage 47 on the seal peripheral surface l ib.
- the outlet 48b of the suction passage 48 opens toward the front compression chamber 28a.
- the inlet 48 a of the suction passage 48 communicates with the supply passage 47 intermittently.
- the portion of the rotary shaft 22 surrounded by 1 lb of the seal peripheral surface functions as a rotary valve 49 formed integrally with the rotary shaft 22.
- the front housing 13 and the front cylinder block 11 are formed with a communication passage 50 penetrating them.
- the communication passage 50 is located below the cylinder block 11 and passes between the two adjacent cylinder bores 28 and 29.
- the inlet 50a of the communication passage 50 opens to the swash plate chamber 25, and the outlet 50b of the communication passage 50 opens to the seal housing chamber 13c. That is, the communication passage 50 communicates the seal accommodation chamber 13c and the swash plate chamber 25.
- the rear housing 14 is formed with a communication path R 4 that communicates the rear suction chamber 14b and the bolt through hole BH.
- the compressor 10 configured as described above, when the front cylinder bore 28 is in the intake stroke, that is, in the stroke in which the double-headed piston 30 moves from the left side to the right side in FIG.
- the inlet 48a communicates, and the refrigerant is sucked into the front compression chamber 28a via the rotary valve 49. That is, as shown in FIG. 6, the refrigerant in the external refrigerant circuit is sucked into the swash plate chamber 25 through the suction hole P, and then reaches the seal storage chamber 13c through the communication passage 50. Then, the refrigerant in the seal housing chamber 13 c that functions as a suction pressure region is sucked into the front compression chamber 28 a through the supply passage 47 and the suction passage 48 by the action of the rotary valve 49.
- the front cylinder bore 28 is in the discharge stroke, that is, the double-headed piston 30 is shown in FIG.
- the refrigerant in the front compression chamber 28a is discharged from the front discharge port 40a to the front discharge chamber 13a functioning as a discharge pressure region by pushing away the front discharge valve 41a. Then, the refrigerant discharged to the front discharge chamber 13a flows out from the discharge hole to the external refrigerant circuit through a communication path (not shown).
- the refrigerant in the rear suction chamber 14b functioning as the suction pressure region passes through the flap valve 46a from the rear suction port 43b due to a differential pressure generated between the rear suction chamber 14b and the rear compression chamber 29a (rear cylinder bore 29). It is pushed away and sucked into the Lya compression chamber 29a.
- the refrigerant in the rear compression chamber 29a is discharged from the discharge port 43a to the discharge valve 44a. Is discharged and discharged to the discharger chamber 14a that functions as a discharge pressure region.
- the refrigerant discharged into the discharger chamber 14a flows out of the discharge hole through the communication passage (not shown) to the external refrigerant circuit.
- the two refrigerant suction structures of the compressor 10 of the present embodiment include a flap valve 46a and a rotary valve 49. Therefore, also in this embodiment, an operation similar to that of the compressor 10 of the first to third embodiments can be obtained. That is, in the compressor 10 of the present embodiment, the arrangement of the flap valve 46a and the rotary valve 49 is reversed from that of the first to third embodiments, but the obtained action is the same.
- the advantages (1) and (2) of the first embodiment and the advantages (8) of the second embodiment are listed in the following. Benefits can be gained.
- the supply passage 47 of the rotary valve 49 is a groove-like passage. For this reason, the manufacturing cost of the rotating shaft 22 can be reduced as compared with a case where a hole-forming force is applied to the rotating shaft 22 to form a hole-shaped passage.
- the refrigerant suction structure to the front compression chamber 28a in the compressor 10 of the present embodiment is the rotary valve 49, and the refrigerant suction structure to the rear compression chamber 29a is a flap. Valve 46a.
- the passage structure for supplying the refrigerant to the front compression chamber 28a via the rotary valve 49 is different from the fourth embodiment.
- a supply passage 51 is formed in the rotary shaft 22.
- the supply passage 51 of the present embodiment is a groove-like passage formed by performing groove processing on the outer peripheral surface of the rotary shaft 22 that is a solid shaft.
- the communication path R5 is formed in the front cylinder block 11 so as to communicate the swash plate chamber 25 with the shaft hole 11a.
- the supply passage 51 is formed so that a plurality of suction passages 48 (five in the present embodiment, only one suction passage 48 is shown in FIG. 7) in the front cylinder block 11 communicate with the communication passage R5. !
- the compressor 10 configured as described above, when the front cylinder bore 28 is in the intake stroke, that is, in the stroke in which the double-headed piston 30 moves from the left side to the right side in FIG.
- the refrigerant in the swash plate chamber 25 that communicates with the inlet 48 a and functions as a suction pressure region is sucked into the front compression chamber 28 a via the rotary valve 49. That is, as shown in FIG. 7, the refrigerant in the external refrigerant circuit is sucked into the swash plate chamber 25 through the suction hole P, and then reaches the supply passage 51 through the communication passage R5.
- the refrigerant in the supply passage 51 is sucked into the front compression chamber 28 a through the suction passage 48 by the action of the rotary valve 49.
- the refrigerant in the front compression chamber 28a flows from the front discharge port 40a to the front discharge valve 41a. And is discharged into the front discharge chamber 13a that functions as a discharge pressure region.
- the refrigerant discharged to the front discharge chamber 13a passes through a communication path (not shown) and the discharge hole also flows out to the external refrigerant circuit. Note that the refrigerant flow when the rear cylinder bore 29 is in the suction stroke and in the discharge stroke is the same as that in the fourth embodiment.
- the flap valve 46a and the rotary valve 49 are adopted as the refrigerant suction structure, so that the compressor 10 of the fourth embodiment (first to third embodiments) is the same.
- the effect can be obtained.
- advantages (1), (2), advantages of the second embodiment (8) and advantages of the fourth embodiment (10) are the same as the advantages of the first embodiment. Obtainable.
- the passage structure of the rotary valves 35 and 49 may be changed.
- the diameter of the hole-like passage may be changed.
- the groove depth and the groove length may be changed.
- the supply passage 22b of the rotary valve 35 may be configured only by the groove-like passage portion 37.
- valve dimensions of the discharge valves 16a, 20a, 41a, 44a, which are flap valves disposed in the discharge chambers 13a, 14a may be the same.
- the refrigerant suction structure is the flap valves 18a, 46a
- the arrangement of the discharge chambers 13a, 14a and the suction chambers 13b, 14b provided in the front housing 13 or the rear housing 14 may be changed.
- the arrangement of the suction holes P connected to the external refrigerant circuit may be changed.
- the suction hole P may be formed in the rear housing 14.
- the refrigerant supply path from the suction hole P connected to the external refrigerant circuit may be changed.
- the refrigerant is supplied to the suction chambers 13b and 14b using the bolt through hole BH.
- the cylinder blocks 11 and 12 may be provided with a supply passage separate from the bolt through hole BH.
- an oil supply passage 60 communicating with the supply passage 22a of the rotary valve 35 may be formed in the rotary shaft 22.
- the supply passage 22a shown in FIG. 3 extends in front of the compressor 10 more than the supply passage 22a shown in FIG. 1, and the oil supply passage 60 is formed at a position corresponding to the thrust bearing 27. .
- the lubricating oil contained in the refrigerant passing through the supply passage 22a is separated from the refrigerant and supplied to the supply passage 22a. Then, the oil passes through the oil supply passage 60 as the rotary shaft 22 rotates. Lubricating oil in the oil supply passage 60 is supplied to the swash plate chamber 25 through the thrust bearing 27.
- the oil supply passage 60 functions as a return passage for returning the lubricating oil to the swash plate chamber 25.
- the lubricity of the sliding part in the swash plate chamber 25 can be improved.
- the oil rate in the refrigerant circuit, particularly in the external refrigerant circuit connected to the outside of the compressor 10 can be reduced, and the cooling capacity can be improved. Can do.
- the amount of oil flowing out of the compressor 10 it is possible to reduce the amount of oil that is enclosed in the compressor 10 in advance during production.
- the oil supply passage 60 can also be applied to other embodiments.
- a residual refrigerant bypass groove may be formed on the outer surface of the rotary shaft 22 on which the rotary valves 35 and 49 are formed.
- the residual refrigerant bypass groove forms a passage that collects refrigerant remaining in the compression chamber at the end of discharge and supplies the collected refrigerant to the compression chamber at the end of suction. That is, the residual refrigerant bypass groove is formed so that the compression chamber (cylinder bore) at the end of discharge communicates with the compression chamber (cylinder bore) at the end of suction.
- the refrigerant compressed in the compression chamber on the front housing side is discharged to a discharge pressure region by a discharge valve provided between the compression chamber and the front housing, and the compression chamber on the rear housing side
- the compressed refrigerant is discharged into the discharge pressure region by a discharge valve provided between the compression chamber and the reha-housing, and the valve size of the discharge valve on the first compression chamber side is the first size. 2 It is larger than the valve size of the discharge valve on the compression chamber side.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/922,428 US7841840B2 (en) | 2005-10-17 | 2006-10-17 | Double-headed piston type compressor |
BRPI0614644-9A BRPI0614644A2 (pt) | 2005-10-17 | 2006-10-17 | compressor do tipo pistço de cabeÇa dupla |
EP06811867A EP1939448B1 (en) | 2005-10-17 | 2006-10-17 | Double-ended piston compressor |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005-302354 | 2005-10-17 | ||
JP2005302354 | 2005-10-17 | ||
JP2006-281667 | 2006-10-16 | ||
JP2006281667A JP4946340B2 (ja) | 2005-10-17 | 2006-10-16 | 両頭ピストン式圧縮機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007046351A1 true WO2007046351A1 (ja) | 2007-04-26 |
Family
ID=37962444
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/320612 WO2007046351A1 (ja) | 2005-10-17 | 2006-10-17 | 両頭ピストン式圧縮機 |
Country Status (6)
Country | Link |
---|---|
US (1) | US7841840B2 (ja) |
EP (1) | EP1939448B1 (ja) |
JP (1) | JP4946340B2 (ja) |
KR (1) | KR100918217B1 (ja) |
BR (1) | BRPI0614644A2 (ja) |
WO (1) | WO2007046351A1 (ja) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101031812B1 (ko) * | 2005-12-26 | 2011-04-29 | 한라공조주식회사 | 압축기 |
JP2009002203A (ja) * | 2007-06-20 | 2009-01-08 | Toyota Industries Corp | ピストン式圧縮機 |
JP5045555B2 (ja) | 2008-05-29 | 2012-10-10 | 株式会社豊田自動織機 | 両頭ピストン型斜板式圧縮機 |
KR100963987B1 (ko) * | 2008-08-05 | 2010-06-15 | 학교법인 두원학원 | 사판식 압축기 |
JP5045679B2 (ja) * | 2009-01-14 | 2012-10-10 | 株式会社豊田自動織機 | ピストン式圧縮機における潤滑構造 |
JP2010261406A (ja) * | 2009-05-11 | 2010-11-18 | Toyota Industries Corp | 固定容量型ピストン式圧縮機 |
KR20130030743A (ko) * | 2010-03-31 | 2013-03-27 | 가부시키가이샤 발레오 재팬 | 피스톤형 압축기 |
JP5240311B2 (ja) * | 2011-03-15 | 2013-07-17 | 株式会社豊田自動織機 | ピストン式圧縮機のシリンダブロックおよびピストン式圧縮機のシリンダブロック加工方法 |
JP5574041B2 (ja) * | 2011-03-31 | 2014-08-20 | 株式会社豊田自動織機 | 斜板式圧縮機 |
JP5218588B2 (ja) * | 2011-03-31 | 2013-06-26 | 株式会社豊田自動織機 | 両頭ピストン型斜板式圧縮機 |
CN102817819B (zh) * | 2011-06-10 | 2016-06-08 | 德昌电机(深圳)有限公司 | 微型气泵 |
DE102015103743A1 (de) | 2015-03-13 | 2016-09-15 | Mahle International Gmbh | Axialkolbenmaschine mit Auslasssteuerung |
JP6977651B2 (ja) * | 2018-03-30 | 2021-12-08 | 株式会社豊田自動織機 | ピストン式圧縮機 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0569958A1 (en) | 1992-05-13 | 1993-11-18 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type refrigerant compressor |
JPH05312145A (ja) * | 1992-05-06 | 1993-11-22 | Nippondenso Co Ltd | 可変容量圧縮機 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH07111171B2 (ja) * | 1989-11-02 | 1995-11-29 | 株式会社豊田自動織機製作所 | 連続可変容量型斜板式圧縮機 |
JP2616295B2 (ja) * | 1991-09-02 | 1997-06-04 | 株式会社豊田自動織機製作所 | 冷凍装置用斜板式圧縮機 |
JPH05195949A (ja) | 1992-01-21 | 1993-08-06 | Toyota Autom Loom Works Ltd | 往復動型圧縮機 |
US5478212A (en) | 1992-03-04 | 1995-12-26 | Nippondenso Co., Ltd. | Swash plate type compressor |
US5362208A (en) | 1992-03-04 | 1994-11-08 | Nippondenso Co., Ltd. | Swash plate type compressor |
JP3769975B2 (ja) * | 1999-04-16 | 2006-04-26 | 株式会社豊田自動織機 | 弁構造 |
JP4096703B2 (ja) * | 2001-11-21 | 2008-06-04 | 株式会社豊田自動織機 | ピストン式圧縮機における冷媒吸入構造 |
JP2004225557A (ja) * | 2003-01-20 | 2004-08-12 | Toyota Industries Corp | ピストン式圧縮機 |
JP3855949B2 (ja) * | 2003-03-18 | 2006-12-13 | 株式会社豊田自動織機 | 両頭ピストン式圧縮機 |
-
2006
- 2006-10-16 JP JP2006281667A patent/JP4946340B2/ja not_active Expired - Fee Related
- 2006-10-17 KR KR1020087002510A patent/KR100918217B1/ko active IP Right Grant
- 2006-10-17 US US11/922,428 patent/US7841840B2/en not_active Expired - Fee Related
- 2006-10-17 EP EP06811867A patent/EP1939448B1/en not_active Not-in-force
- 2006-10-17 WO PCT/JP2006/320612 patent/WO2007046351A1/ja active Application Filing
- 2006-10-17 BR BRPI0614644-9A patent/BRPI0614644A2/pt not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH05312145A (ja) * | 1992-05-06 | 1993-11-22 | Nippondenso Co Ltd | 可変容量圧縮機 |
EP0569958A1 (en) | 1992-05-13 | 1993-11-18 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Swash plate type refrigerant compressor |
JPH05312146A (ja) * | 1992-05-13 | 1993-11-22 | Toyota Autom Loom Works Ltd | 斜板式圧縮機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP1939448A4 |
Also Published As
Publication number | Publication date |
---|---|
KR20080025188A (ko) | 2008-03-19 |
BRPI0614644A2 (pt) | 2013-04-02 |
US7841840B2 (en) | 2010-11-30 |
EP1939448A4 (en) | 2011-05-18 |
EP1939448B1 (en) | 2012-05-16 |
JP4946340B2 (ja) | 2012-06-06 |
US20090238697A1 (en) | 2009-09-24 |
KR100918217B1 (ko) | 2009-09-21 |
JP2007138925A (ja) | 2007-06-07 |
EP1939448A1 (en) | 2008-07-02 |
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