EP1308621A2 - Compresseur à plateau en biais à capacité variable - Google Patents

Compresseur à plateau en biais à capacité variable Download PDF

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Publication number
EP1308621A2
EP1308621A2 EP02024681A EP02024681A EP1308621A2 EP 1308621 A2 EP1308621 A2 EP 1308621A2 EP 02024681 A EP02024681 A EP 02024681A EP 02024681 A EP02024681 A EP 02024681A EP 1308621 A2 EP1308621 A2 EP 1308621A2
Authority
EP
European Patent Office
Prior art keywords
discharge
pressure
predetermined range
suction
discharge pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP02024681A
Other languages
German (de)
English (en)
Inventor
Masahiro Kawaguchi
Satoshi Umemura
Satoshi Koumura
Masaki Ota
Tomoji Tarutani
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Toyota Industries Corp filed Critical Toyota Industries Corp
Publication of EP1308621A2 publication Critical patent/EP1308621A2/fr
Withdrawn legal-status Critical Current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
    • 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
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure

Definitions

  • the present invention relates generally to a variable displacement type compressor adapted for use in an air conditioner, and more specifically to a displacement control system for the variable displacement type compressor which makes it possible to achieve the desired air conditioning performance by appropriately controlling the displacement of the compressor.
  • a variable displacement type compressor for example, for use in an automotive air conditioner has incorporated therein a control valve for controlling discharge amount of a refrigerant.
  • operating performance of the air conditioner varies depending on the relationship between the discharge pressure and suction pressure of the refrigerant.
  • FIG. 12 shows three different operating regions A, B and C of the compressor, indicated by shaded areas, in connection with the relationship between the discharge pressure Pd and suction pressure Ps of the refrigerant.
  • the region A represents a region where the compressor is operating under a low cooling load and with low discharge pressure Pd.
  • the present invention relates to a variable displacement type compressor, an air conditioning system equipped with such a compressor and a method for controlling the displacement of such a compressor which will not impose an excessive load on an engine while the compressor is running under a high load.
  • a variable displacement type compressor circulates a fluid in an air conditioning circuit.
  • the fluid is drawn into a suction region before compression.
  • the pressure in the suction region is defined as suction pressure.
  • the fluid is discharged to the discharge region after compression.
  • the pressure in the discharge region is defined as discharge pressure.
  • the suction region is connected to the discharge region.
  • the compressor has a compression mechanism and a displacement control valve.
  • the compression mechanism compresses the fluid.
  • the displacement control valve controls discharge amount of the fluid of the compressor.
  • In a first predetermined range of the discharge pressure the suction pressure decreases at a first variation as the discharge pressure increases.
  • In a second predetermined range of the discharge pressure that is higher than the first predetermined range the suction pressure varies at a second variation as the discharge pressure increases.
  • the second variation is constituted of at least one of a third variation that is smaller than the first variation and at which the suction pressure decreases as the discharge pressure increases, a fourth variation at which the suction pressure increases as the discharge
  • the present invention also provides a method for controlling displacement in a variable displacement type compressor that circulates a fluid in an air conditioning circuit.
  • the fluid is drawn into a suction region before compression.
  • the pressure in the suction region is defined as suction pressure.
  • the fluid is discharged to the discharge region after compression.
  • the pressure in the discharge region is defined as discharge pressure.
  • the suction region is connected to the discharge region.
  • the method comprises the steps of decreasing the suction pressure at a first variation as the discharge pressure increases in a first predetermined range of the discharge pressure, setting a third variation that is smaller than the first variation and at which the suction pressure decrease as the discharge pressure increases in a second predetermined range of the discharge pressure that is higher than the first predetermined range, setting a fourth variation at which the suction pressure increases as the discharge pressure increases in the second predetermined range, setting a second variation by using at least one of the third variation, the fourth variation, and substantially zero in the second predetermined range, and varying the suction pressure at the second variation as the discharge pressure increases in the second predetermined range.
  • variable displacement type compressor The following will describe a preferred embodiment of a variable displacement type compressor according to the present invention while having reference to the accompanying drawings. It is noted the following description will deal with a variable displacement swash plate type compressor adapted for use in an automotive air conditioning system.
  • variable displacement swash plate type compressor 100 (referred to merely as “compressor” hereinafter) includes a cylinder block 1 having formed therein a plurality of cylinder bores 1a arranged around the central axis of the cylinder block 1 and each receiving therein a reciprocally movable piston 18.
  • a front housing 2 is sealingly fastened to the front end of the cylinder block 1, and a rear housing 5 is similarly fastened to the rear end of the cylinder block 1 with a valve plate assembly 6 interposed therebetween.
  • the cylinder block 1 and the front housing 2 cooperate to define a crank chamber 9 as a crank chamber pressure region in which a wobble plate 15 and its associated parts are disposed as will be described in detail in later part hereof.
  • the rear housing 5 has formed therein a suction chamber 3 as a suction region or a suction pressure region into which refrigerant before compression is drawn and a discharge chamber 4 as a discharge region or a discharge pressure region into which refrigerant compressed in the respective cylinder bores 1a is discharged.
  • the valve plate assembly 6 is formed therethrough with a suction port for providing communication between the suction chamber 3 and each cylinder bore 1a through a suction valve 3a and also with a discharge port for communication between the discharge chamber 4 and each cylinder bore 1a through a discharge valve 4a.
  • a retainer 4b is fixed in the discharge chamber 4 so as to limit the maximum opening of the discharge valve 4a.
  • a displacement control valve 30 serving as the displacement control means of the present invention which will be described in detail in later part hereof.
  • a first supply passage 20 extends through the cylinder block 1 and the rear housing 5 for communication between the crank chamber 9 and the displacement control valve 30.
  • a bleed passage 21 having therein an orifice 21a is formed in the cylinder block 1 for communication between the crank chamber 9 and the suction chamber 3.
  • the rear housing 5 has formed therein a pressure sensing passage 22 and a second supply passage 23 for communication of the suction chamber 3 and the discharge chamber 4 with the displacement control valve 30, respectively, as will be described more in detail with reference to FIG. 2.
  • a drive shaft 8 is disposed in the crank chamber 9 and rotatably supported in the cylinder block 1 and the front housing 2 by bearings 1b and 2b arranged in the cylinder block 1 and the front housing 2, respectively.
  • the drive shaft 8 is connected at the front end thereof to a vehicle engine by way of a suitable clutching means such as electromagnetic clutch (not shown).
  • a shaft seal 2a is provided between the drive shaft 8 and the front housing 2. It is noted that the compressor 100 may dispense with the clutch so that the drive shaft 8 is driven constantly by means of a belt and pulley arrangement.
  • a rotor 7 is fixedly mounted on the drive shaft 8 for rotation therewith in the crank chamber 9 with a thrust bearing 2c disposed between the rotor 7 and the inner wall of the front housing 2, and a sleeve 19 is axially slidably mounted on the drive shaft 8 adjacent to the rotor 7.
  • the rotor 7 is formed with an elongated through-hole 7b through which a pin 11a of a swash plate 11 is inserted slidably in the elongated through-hole 7b.
  • the swash plate 11 is rotatable with the drive shaft 8 and pivotally supported by a pair of trunnion pins 19a projecting from opposite sides of the sleeve 19 so that, as the drive shaft 8 is rotated, the swash plate 11 makes a nutational motion about the drive shaft 8 at an inclination angle.
  • a wobble plate 15 is fitted to the swash plate 11 by way of a thrust bearing 12, a plane bearing 10, a race 13 and a thrust washer 14, and a guide rod 16 extends in the crank chamber 9 to prohibit rotation of the wobble plate 15.
  • Each of the pistons 18 received in the cylinder bores 1 a is connected to the wobble plate 15 by a rod 17.
  • the wobble plate 15 makes a wobbling movement in response to the nutational motion of the swash plate 11 and the pistons 18 connected to the wobble plate 15 are caused to move reciprocally in their associated cylinder bores 1 a.
  • Refrigerant is drawn from the suction chamber 3 into the cylinder bore 1a during the suction stroke of the piston 18 and then compressed in and then discharged out of the cylinder bore 1a during the discharge stroke of the piston 18, thus compressed refrigerant being discharged into the discharge chamber 4.
  • Displacement of the compressor 100 depends on the length of stroke of the piston 18 and such stroke length varies with the inclination angle of the swash plate 11.
  • the stroke length of the piston 18 and hence the displacement is increased with an increase of the angle at which the swash plate 11 is inclined with respect to a plane perpendicular to the axis of the drive shaft 8, and vice versa.
  • This inclination angle of the swash plate 11 during compressor operation is determined by the pressure differential between the pressure in the cylinder bores 1a and in the crank chamber 9, and this pressure differential is adjusted by the displacement control valve 30.
  • the displacement control valve 30 includes a main valve portion 33, a cylindrical housing 31 fixed at one end thereof to one end of the main valve portion 33, and a cap 38 fixed to the other end of the main valve portion 33.
  • An adjusting portion 32 is screwed into the other end of the cylindrical housing 31 by way of an O-ring, and an insert 37 is disposed in the cap 38.
  • the main valve portion 33, the cylindrical housing 31 and the adjusting portion 32 cooperate to define a suction pressure chamber 51 as a suction region which is in communication with the suction chamber 5 via the aforementioned pressure sensing passage 22 in the rear housing 5 and radial passages 51a formed in the cylindrical housing 31.
  • suction pressure Ps prevails in the suction pressure chamber 51 of the displacement control valve 30.
  • a bellows 36 having one end thereof fixed to the adjusting portion 32 and the other end thereof engaged with a rod 35 which is slidably disposed in an axial bore formed in the main valve portion 33.
  • the bellows 36 has therein a spring 36a urging the bellows 36 in the direction indicated by arrow F 1 and the bellows interior is maintained under vacuum.
  • F 1 represents the sum of the elastic force of the bellows 36 and the urging force of the spring 36a both acting in the same arrow direction.
  • the bellows 36 which serves as the suction pressure Ps sensitive means of the invention, has an effective pressure sensing area S1 to which suction pressure Ps acts in the direction opposite to the arrow direction F 1 . It is noted that any suitable means such as diaphragm may be used in place of the bellows 36 as the suction pressure Ps sensitive means of the invention.
  • the rod 35 is slidable in the axial bore in the main valve portion 33 by contraction or expansion of the bellows 36.
  • the main valve portion 33 has formed therein at an intermediate position thereof an axial bore 20b into which the distal end of the rod 35 extends and first radial supply ports 20a extending radially from the axial bore 20b.
  • the first supply ports 20a are in communication with the aforementioned first supply passage 20 formed through the cylinder block 1 and the rear housing 5 for communication with the crank chamber 9.
  • the axial bore 20b is formed with a cross sectional area S2.
  • the main valve portion 33 and the insert 37 define therebetween a discharge pressure chamber 52 as a discharge region which is in communication with the discharge chamber 4 through the second supply passage 23 formed in the rear housing 5 and second radial supply ports 23a which are formed in the main valve portion 33.
  • the first supply passage 20, the first supply port 20a, the second supply passage 23 and the second supply port 23a constitute communication routes of the variable displacement type compressor according to the present invention.
  • crank pressure chamber 53 as a crank chamber pressure region which is in communication with the crank chamber 9 of the compressor 100 by way of a communication passage 33a formed in the main valve portion 33.
  • the insert 37 is formed at the axial center thereof with an axial bore through which a discharge pressure correction rod 41, which serves as the discharge pressure sensitive means of the invention, is slidably inserted.
  • This rod 41 has a flange portion 41 a disposed in the discharge pressure chamber 52 and a stem portion 41b passing through the insert 37 and extending into the crank pressure chamber 53.
  • a spring 42 having a spring constant k 2 is provided in the crank pressure chamber 53 for urging the correction rod 41 toward the discharge pressure chamber 52 as indicated by arrow 70 with force F 2 .
  • the stem portion 41 b of the correction rod 41 has a cross sectional area S3.
  • a valve box 60 serving as the rod supplementing member of the invention is disposed within the discharge pressure chamber 52, and a valve body 40 in the form of a spherical ball serving as the valve means of the invention and part of the correction rod 41 including its flange portion 41 a and part of the stem portion 41 b adjacent to the flange portion 41a are incorporated within the valve box 60.
  • a spring 63 with a spring constant k 3 is disposed between the flange portion 41a and the inner end of the valve box 60.
  • Part of the valve body 40 which protrudes out of the valve box 60 through its first opening 61 is contactable with the rod 35.
  • the discharge pressure correction rod 41 is movable axially through the opposite second opening 62 of the valve box 60.
  • the discharge pressure correction rod 41, the spring 42 and the valve box 60 constitute the urging means of the present invention.
  • Reference numeral 39 designates a valve seat for the valve body 40.
  • the compressor 100 having incorporated therein such displacement control valve 30 is disposed in a refrigeration circuit together with a condenser, expansion valve, evaporator, etc. (not shown).
  • a condenser, expansion valve, evaporator, etc. (not shown).
  • the swash plate 11 is rotated at an inclined angle by the rotor 7 that is fixed on and hence rotatable with the drive shaft 8.
  • the wobble plate 15 fitted to the swash plate 11 makes a wobbling movement at the inclined angle of the swash plate 11, which causes the pistons 18 to move reciprocally in their associated cylinder bores 1a for a stroke length corresponding to the inclined angle of the wobble plate 15.
  • the displacement control valve 30 is provided as an internal control mechanism of the compressor 100 wherein the valve body 40 of the displacement control valve 30 is operable by way of the bellows 36 as the suction pressure sensitive means and the discharge pressure correction rod 41 as the discharge pressure sensitive means, respectively.
  • the displacement control valve 30 thus constructed is configured such that a Pd-Ps characteristic curve as indicated by a solid line in FIG. 6 is achieved, as compared with a curve of a dotted line achievable by prior art.
  • FIG. 6 showing two Pd-Ps characteristic curves, wherein the solid line curve shows Pd-Ps characteristic achievable by use of the displacement control valve 30 of the illustrated embodiment, while the dotted line curve represents similar characteristic of the prior art control valves.
  • symbols T1 and T2 depict inflection points of Pd-Ps characteristic curve of the displacement control valve 30, so that the curve may be divided into three line sections L1, L2 and L3 by such inflection points T1 and T2.
  • the displacement control valve 30 is configured to operate as follows.
  • the low-load control region R3 (or the third mode in the invention) corresponding to the line section L3 where the compressor 100 is operating under a low discharge pressure Pd and hence with a low displacement
  • suction pressure Ps increases with an increase in discharge pressure Pd.
  • the intermediate-load control range R1 (or the first mode in the invention) corresponding to the line section L1 between the inflection points T1 and T2 where discharge pressure Pd is in a middle range
  • the suction pressure Ps decreases with an increase of discharge pressure Pd.
  • suction pressure Ps is maintained substantially at a constant level irrespective of a change of discharge pressure Pd.
  • suction pressure Ps is prevented from being dropped.
  • the Pd-Ps characteristic describes a curve so that it avoids interference with any of the shaded region A where a mist tends to be produced, the region B where evaporator frosting tends to occur and the region C where cooling performance tends to be decreased.
  • the compressor 100 operating according the Pd-Ps characteristic curve can forestall these three problems.
  • suction pressure Ps in the intermediate-load control range R1 between the inflection points T1 and T2 is generally raised or set higher than that of the characteristic curve attainable by the prior art control valves as indicated by a dotted line, without interfering with the operating region C. Furthermore, suction pressure Ps in the high-load control range R2 of the Pd-Ps characteristic curve is maintained substantially while avoiding interference with the operating region C. As is apparent from comparison with the dotted line, maintenance of a substantially constant suction pressure Ps in the high-load control range R2 is accomplished by providing the inflection point T2 between the line sections L1 and L2 so as to differentiate the inclinations of the line sections L1 and L2.
  • FIG. 2 shows a state of the displacement control valve 30 when the compressor 100 is operating under a low load in the control range R3.
  • the discharge pressure correction rod 41 is urged in the direction of the arrow 70 by the spring 42, and the valve body 40 is pushed by the correction rod 41 accordingly to be seated on the valve seat 39, so that the axial bore 20b which is in communication with the crank chamber 9 through the first supply passage 20 in the cylinder block 1 is shut off from the discharge pressure chamber 52. That is, the discharge chamber 4 and the crank chamber 9 are shut off from each other.
  • the spring 63 has one end thereof free from contact with its adjacent inner surface of the valve box 60 and hence provides no urging action.
  • crank chamber 9 and the suction chamber 3 are in communication with each other by way of the bleed passage 21 having therein the orifice 21 a, part of the refrigerant in the crank chamber 9 flows into the suction chamber 3. Since flowing of refrigerant under high pressure from the discharge chamber 4 into the crank chamber 9 is shut off, crank chamber pressure Pc is reduced and the back pressure acting on the pistons 18 is reduced, accordingly. Therefore, the inclination angle of the wobble plate 15 is increased thereby to increase the stroke length of the pistons 18, with the result that the displacement is increased.
  • the valve body 40 is not lifted off from the valve seat 39 unless suction pressure Ps in the suction pressure chamber 51 is substantially reduced relatively to the force F 1 . Therefore, suction pressure Ps is increased with a build-up of discharge pressure Pd. At this state, the crank chamber pressure Pc and the suction pressure Ps are maintained substantially to be equal to each other.
  • the inclination of the line is determined by -(S2 - S3) / (S1 - S2 + S3). Since the cross-sectional areas of S1, S2 and S3 are such that S1>S3>S2, the inclination of the line, or the manner in which suction pressure Ps varies with discharge pressure in the Pd-Ps characteristic line, is positive. That is, the displacement control valve 30 provides Pd-Ps characteristic as shown by the line section L3 of FIG. 6 in the low-load control range R3.
  • the discharge pressure correction rod 41 is moved in the direction of an arrow 72 with an increase of the discharge pressure Pd while overcoming the urging force of the spring 42.
  • the spring 63 is merely moved in the direction of the arrow 72 with the correction rod 41, exerting no urging force.
  • the valve body 40 is moved off the valve seat 39 and, therefore, the first supply port 20a and the second supply port 23a become in communication with each other, thereby allowing refrigerant under a high pressure in the discharge chamber 4 to flow into the crank chamber 9 through the second supply passage 23, the second supply port 23a, the first supply port 20a and the first supply passage 20.
  • crank chamber pressure Pc is increased and the back pressure acting on the pistons 18 is increased accordingly, so that the inclination angle of the wobble plate 15 is decreased.
  • the stroke length of the pistons 18 is shortened, causing the displacement to be reduced. Since the suction pressure Ps in the suction pressure chamber 51 acts against F1, the force to open the valve body 40 is decreased with an increase of the suction pressure Ps.
  • the inclination of the line is determined by -S2/(S1-S2). Since the cross-sectional area S1 is greater than S2, or S1 > S2, the inclination of the Pd-Ps characteristic line in the control range R1 is negative. That is, the displacement control valve 30 provides Pd-Ps control characteristic as shown by the line section L1 of FIG. 6 in the intermediate-load control range R1.
  • the variation of suction pressure Ps with respect to discharge pressure Pd in the control range R1 is referred to as the first variation in the invention.
  • FIG. 5 showing a state of the displacement control valve 30 when the compressor 100 is operating under a high load in the control range R2
  • the discharge pressure correction rod 41 is moved further in the direction of the arrow 72 with a buildup of the discharge pressure Pd while overcoming the urging force of the spring 42.
  • the spring 63 begins to be compressed and to act against the force F2.
  • the valve box 60 and the valve body 40 are moved together with the discharge pressure correction rod 41 in the direction of the arrow 72 which causes the valve body 40 to open. That is, in the high-load control range R2, the valve body 40 is moved in its opening direction by cooperative action of the correction rod 41, the valve box 60 and the spring 63.
  • the urging forces of the springs 42 and 63 are expressed by k 2 ⁇ x 2 and k 3 ⁇ x 3 , respectively, wherein x 2 and x 3 represent the distances by which the respective springs 42 and 63 are compressed.
  • the displacement control valve 30 operates in the high-load control range R2 such that characteristic is represented by the line section L2 which is substantially flat as shown in FIG. 6.
  • the variation of suction pressure Ps with respect to discharge pressure Pd in the control range R2 is referred to as the second variation in the invention. It is noted that, since the values x 2 and x 3 are dependent on discharge pressure Pd, the urging forces k 2 x 2 and k 3 x 3 of the springs 42 and 63, respectively, vary with discharge pressure Pd. Therefore, the inclination of the line section L2 depends on the values of the first and second terms of the right side of the equation (6).
  • the displacement control valve 30 makes it possible to rationally control displacement of the compressor 100 in each of the control ranges R1, R2 and R3.
  • controlling is performed such that suction pressure Ps is maintained substantially constant irrespective of an increase in discharge pressure Pd in the high-load control range R2
  • controlling of suction pressure Ps in this range may be changed as required.
  • setting may be made such that change of suction pressure Ps with respect to a rise of discharge pressure Pd occurs in any combination of manners of changes which include decreasing of suction pressure Ps at a third variation which is smaller than the first variation in the intermediate-load control range R1, increasing of suction pressure Ps at a fourth variation and maintaining suction pressure Ps substantially constant.
  • a modified displacement control valve 130 is provided, wherein like reference numerals or symbols designate like elements or parts of the displacement control valve 30 of the preferred embodiment.
  • the cylindrical housing 31 is formed with third supply ports 23b communicating with the second supply passages 23 in the main valve body 33 and a discharge pressure chamber 152 as a discharge region where discharge pressure Pd prevails due to the communication of the above third supply port 23b and the second supply passage 23.
  • the first supply passage 20, the first supply port 20a, the second supply passage 23 and the second supply port 23a and the third supply port 23b constitute the communication routes of the variable displacement type compressor according to the present invention.
  • a discharge pressure correction rod 141 is disposed within the discharge pressure chamber 152.
  • the stem portion 141b of this correction rod 141 has a cross-sectional area S4.
  • the discharge pressure correction rod 141 acts on the bellows 36 in the direction of an arrow 170, or rightward as seen in FIG. 10, against the urging force of a spring 142 disposed in the discharge pressure chamber 152 and having a spring constant k 4 .
  • These discharge pressure correction rod 141 and the spring 142 are referred to as the urging means of the invention.
  • the discharge pressure correction rod 141 and the spring 142 cooperate to urge the valve body 40 in the direction that causes the valve to open.
  • the displacement control valve 130 operates in the same manner as the counterpart 30 of the preferred embodiment.
  • FIG. 11 showing a further modification of the present invention, this modification differs from the preferred embodiment in the structure of valve box as the rod supplementing member of the invention.
  • the rod supplementing member of FIG. 11 includes a spring 80 and spring washers 81 and 82.
  • the discharge pressure correction rod 41 is disposed passing through a through-hole 82a formed in the spring washer 82.
  • This rod supplementing member can perform the same function as the counterpart comprising the valve box 60 and the spring 63 of the preferred embodiment.
  • the spring 80 and the spring washer 82 may be substituted by a single member including a modified spring.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressor (AREA)
EP02024681A 2001-11-06 2002-11-05 Compresseur à plateau en biais à capacité variable Withdrawn EP1308621A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001340800 2001-11-06
JP2001340800A JP3982237B2 (ja) 2001-11-06 2001-11-06 可変容量圧縮機および該可変容量圧縮機を備えた空調装置、可変容量圧縮機における制御方法

Publications (1)

Publication Number Publication Date
EP1308621A2 true EP1308621A2 (fr) 2003-05-07

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EP02024681A Withdrawn EP1308621A2 (fr) 2001-11-06 2002-11-05 Compresseur à plateau en biais à capacité variable

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EP (1) EP1308621A2 (fr)
JP (1) JP3982237B2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004162567A (ja) * 2002-11-12 2004-06-10 Fuji Koki Corp 可変容量型圧縮機用の制御弁
JP4644475B2 (ja) * 2004-11-30 2011-03-02 株式会社不二工機 圧力調整弁
WO2016027357A1 (fr) * 2014-08-22 2016-02-25 三菱電機株式会社 Dispositif d'entraînement de moteur électrique et appareil de conditionnement d'air utilisant le dispositif d'entraînement de moteur électrique ou appareil de conditionnement d'air de réfrigération utilisant le dispositif d'entraînement de moteur électrique

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04321779A (ja) 1991-04-22 1992-11-11 Nippondenso Co Ltd 斜板型可変容量圧縮機
JPH06123279A (ja) 1992-10-08 1994-05-06 Toyota Autom Loom Works Ltd 可変容量型圧縮機用制御弁
JPH07119642A (ja) 1993-10-15 1995-05-09 Toyota Autom Loom Works Ltd 可変容量型圧縮機用制御弁

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4051134B2 (ja) * 1998-06-12 2008-02-20 サンデン株式会社 可変容量圧縮機の容量制御弁機構
JP2000320464A (ja) * 1999-05-10 2000-11-21 Saginomiya Seisakusho Inc 容量可変型圧縮機用制御弁
US6340293B1 (en) * 2000-08-25 2002-01-22 Delphi Technologies Inc Clutchless compressor control valve with integral by pass feature

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04321779A (ja) 1991-04-22 1992-11-11 Nippondenso Co Ltd 斜板型可変容量圧縮機
JPH06123279A (ja) 1992-10-08 1994-05-06 Toyota Autom Loom Works Ltd 可変容量型圧縮機用制御弁
JPH07119642A (ja) 1993-10-15 1995-05-09 Toyota Autom Loom Works Ltd 可変容量型圧縮機用制御弁

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JP2003148337A (ja) 2003-05-21
JP3982237B2 (ja) 2007-09-26
US20030108432A1 (en) 2003-06-12

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