CN101070839A - Variable displacement compressor - Google Patents
Variable displacement compressor Download PDFInfo
- Publication number
- CN101070839A CN101070839A CNA2007101029007A CN200710102900A CN101070839A CN 101070839 A CN101070839 A CN 101070839A CN A2007101029007 A CNA2007101029007 A CN A2007101029007A CN 200710102900 A CN200710102900 A CN 200710102900A CN 101070839 A CN101070839 A CN 101070839A
- Authority
- CN
- China
- Prior art keywords
- flange
- compressor
- pressure
- variable displacement
- housing
- 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.)
- Pending
Links
Images
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
- 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
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
- F04B39/0072—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes characterised by assembly or mounting
-
- 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
- F04B27/0873—Component parts, e.g. sealings; Manufacturing or assembly thereof
- F04B27/0878—Pistons
-
- 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
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
-
- 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
-
- 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
- F04B2027/184—Valve controlling parameter
- F04B2027/1854—External parameters
-
- 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
- F04B2205/00—Fluid parameters
- F04B2205/04—Pressure in the outlet chamber
-
- 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
- F04B2205/00—Fluid parameters
- F04B2205/09—Flow through the pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/12—Kind or type gaseous, i.e. compressible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Measuring Volume Flow (AREA)
Abstract
A variable displacement compressor comprises a flange, a movable body, and a detection sensor. The flange is joined to a housing and forms a flange passage for connecting a refrigerant passage and an external refrigerant circuit. The movable body is movably disposed in the flange, is movable according to a flow rate of refrigerant gas in the flange passage, and has a magnet. The detection sensor is fixed to or in the flange for detecting magnetic flux density of the magnet. The flow rate of the refrigerant gas is detected based on the magnetic flux density detected by the detection sensor. The flange is attachable to and detachable from the housing in a state where the flange is provided with the movable body and the detection sensor.
Description
Technical field
The present invention relates to compressor with variable displacement, it comprises in response to the change in flow of refrigerant gas main body movably, and it detects the Magnetic flux density of the magnet in main body, thereby detects the flow velocity of refrigeration agent.
Background technique
Have known variable-displacement compressor (only being called compressor later on), wherein by regulating the aperture of displacement control valve, the tilt angle of dividing plate changes, so the discharge capacity of compressor changes.
Yet in traditional compressor, flow velocity changes order and is only sending aspect control and the change discharge capacity, and actual discharge capacity can not be known.When discharge capacity changes, the variable power of compressor, but it is estimated by calculated value based on the flow velocity bid value.
Therefore, change after order sent out at flow velocity, actual displacement value is different from calculated value, reaches bid value up to discharge capacity, when compressor when vehicle motor start during pressurized gas, above-mentioned difference increase.Therefore, need the long time to make the vehicle inside temperature reach desired level, and bigger load act on the vehicle motor.Just, be difficult to implement suitable control (referring to Japanese Patent Application Publication No.2002-332962) in this case.
If the flow velocity of the refrigerant gas in compressor is detected accurately, the actual displacement of compressor and actual power are known, and this is very effective.For above-mentioned purpose, disclosed electric flowmeter makes and is used for the flow velocity of detection of refrigerant gas in the open No.63-177715 of Japanese utility model application.
Disclose electric flowmeter or area flowmeter among the open No.63-177715 of Japanese utility model application in Fig. 1, it comprises main body, buoyant member (perhaps movable body) and be provided to the guide of the main body above the buoyant member.Magnet is fixed on the buoyant member by bar, and wherein this bar is provided on the upper surface of buoyant member.When the buoyant member vertical movement, magnet is vertical movement in guide.The magnetic field of magnet is vertically formed at the rete place of Hall element (perhaps detecting sensor), and wherein Hall element provides the outer wall that is adjacent to guide.The rete that magnet is parallel to Hall element moves.This Hall element is connected on the controller.
Disclose electric flowmeter among the open No.63-177715 of Japanese utility model application in Fig. 2, it comprises the pressure detector that is connected to high pressure and low pressure introducing passage, and these passages are provided at respectively on the front side and rear side in the hole in the flow channel.The inside of detector is divided into two spaces hermetically by bellophragm film (perhaps movable body).Be incorporated in two spaces that are divided on the both sides of bellophragm film by introducing passage at the front side in hole and the pressure in the flow channel on the rear side, and the magnet that is provided on the bellophragm film moves by the pressure reduction between them.On the direction that moves perpendicular to magnet, provide Hall element (perhaps detecting sensor), and the magnetic pole strength of magnet is to Hall element.This Hall element connects controller.
Even under the situation of the electric flowmeter of using the open No.63-177715 of Japanese utility model application to the compressor, the accuracy of size that is used to detect the parts of flow velocity changes.Therefore, the accuracy of detection flow velocity changes in each compressor.In order to improve the accuracy of flow rate detection, enough refrigerant gass are provided in the compressor with electric flowmeter and flow, and the position of magnet and Hall element are detected then, and Hall element is calibrated.
Yet, when the electric flowmeter of the open No.63-177715 of Japanese Utility Model application only is applied on the compressor, make refrigerant gas in compressor, flow, and the parts that are used to detect flow velocity are regulated and are calibrated, under removable main body and detecting sensor are installed in state status in the housing of compressor.This process be trouble and can not automation.At a large amount of manufacturing site locations of producing the reality of compressor, in each compressor, make the process that refrigerant gas flows increase cost and manufacturing time.Therefore, at the manufacturing site location of reality, this process can not be implemented.
Aim to provide a kind of compressor with variable displacement in the present invention who considers the problems referred to above, it comprises the detection flow velocity parts than easier adjusting of tradition and calibration.
Summary of the invention
A kind of compressor with variable displacement is provided according to an aspect of the present invention, and it comprises housing, coolant channel, piston, dividing plate, flange, removable main body and detecting sensor.Housing has cylinder hole and crank box.Coolant channel is formed in the housing and comprises suction pressure zone and discharge pressure region.In the piston cylinder hole.Dividing plate is arranged in the crank box.The tilt angle of dividing plate is controlled according to the pressure in crank box with by the pressure reduction between the pressure in the cylinder hole of piston, and the pressure in crank box is regulated by supply passage and discharge passage, wherein supply passage is used for supplying with pressure in discharge pressure region in crank box, and discharge passage is used for discharging the pressure of crank box to the suction pressure passage.Flange is connected on the housing and is formed for connecting coolant channel and the flange passageway of external refrigeration path.Removable main body is arranged in the flange, is movably according to the refrigerant gas flow velocity in the flange passageway, and has magnet.Detecting sensor is fixed to or is in the flange of the Magnetic flux density that is used for detecting magnet.The flow velocity of refrigerant gas detects based on the detected Magnetic flux density of detecting sensor, and flange can be fixed to and break away from from housing, and is in flange and provides under the state of removable main body and detecting sensor.
Other aspects and advantages of the present invention will be from following description, and in conjunction with the accompanying drawings, the example by principle of the present invention becomes obvious.
Description of drawings
Think that the feature of the present invention with novelty will set forth in additional claim.With the present invention of purpose and advantages, will in the describing below of in conjunction with the accompanying drawings currently preferred embodiment, better obtain describing, wherein:
Fig. 1 is the longitudinal cross-section view of variable-displacement compressor according to a first advantageous embodiment of the invention;
Fig. 2 is the viewgraph of cross-section of the line A-A in Fig. 1;
Fig. 3 is the viewgraph of cross-section that the part of the flowmeter of first preferred embodiment when guiding valve is arranged on uppermost position in fig-ure is amplified;
Fig. 4 is the viewgraph of cross-section that the part of the flowmeter of first preferred embodiment when guiding valve is arranged on upper/lower positions is amplified;
Fig. 5 shows the view of the adjusting and the calibration of flowmeter; With
Fig. 6 is the viewgraph of cross-section that the part of flowmeter according to a second, preferred embodiment of the present invention is amplified.
Embodiment
Referring to Fig. 1 to Fig. 5, variable-displacement compressor (only being called compressor subsequently) according to a first advantageous embodiment of the invention will be described below.Fig. 1 shows the schematic representation of compressor.Referring to Fig. 1, compressor has housing 11, and this housing comprises cylinder body 12, front case 13 and rear case 14.Front case 13 is connected to the front end of cylinder body 12.Rear case 14 is connected to the rear end of cylinder body 12.In Fig. 1, left side and right side correspond respectively to front side and rear side.
Wire board 18 is fixed on the live axle 16, is used for therewith rotating at crank box 15.Dividing plate 19 is contained in the crank box 15.Dividing plate 19 provides and is supported on the live axle 16 with having the tilt angle, thereby makes dividing plate 19 tilt with respect to the axis of live axle 16, and with respect to live axle 16 still slidably.Linkage 20 is arranged between wire board 18 and the dividing plate 19, allows dividing plate 19 with wire board 18 and live axle 16 rotations, and the axis tilt of relative drive shaft 16.The tilt angle of dividing plate 19 is controlled by displacement control valve 34, and it will described subsequently.
A plurality of cylinders hole 21 is formed in the cylinder body 12 (only showing in Fig. 1).Single head pison reciprocally is arranged in each cylinder hole 12.Each piston 22 engages with the outer circumferential part branch of dividing plate 19 by a pair of bearing shell 23.Therefore, by the rotation of live axle 16, the rotation of dividing plate 19 can be transformed into moving back and forth of piston 22 by bearing shell 23.
Valve port device 24 is inserted between cylinder body 12 and the rear case 14, and pressing chamber 25 is defined in the cylinder hole 21 on the rear side (right side among Fig. 1) by piston 22 and valve port device 24.Be defined in the rear case 14 as the suction chamber 26 in the suction pressure zone of compressor with as the discharge chamber 27 of the discharge pressure region of compressor.
When piston 22 from upper dead center when lower dead centre moves, the refrigerant gas in suction chamber 26 is drawn in the pressing chamber 25 by suction port 28 and the suction valve 29 that is formed in the valve port device 24.When piston 22 from lower dead centre when upper dead center moves, the refrigeration agent of the suction in pressing chamber 25 is compressed to predetermined pressure, and is discharged to and discharges in the chamber 27 by being formed on exhaust port 30 in the valve port device 24 and expulsion valve 31.
Connecting crank case 15 is formed in cylinder body 12 and the valve port device 24 to the discharge passage 32 of suction chamber 26, is used for being released in the pressure of crank box 15 in suction chamber 26.Connection discharge chamber 27 is formed on rear case 14 to the supply passage 33 of crank box 15, in valve port device 24 and the cylinder body 12, is used for supplying with the pressure of discharge chamber 27 in crank box 15.Displacement control valve 34 is arranged in the supply passage 33 in the rear case 14.
Displacement control valve 34 is introduced passage 35 by first pressure and is connected in the suction chamber 26, and the aperture of displacement control valve 34 is regulated based on the pressure in suction chamber 26.Pressure in crank box 15 depend on by supply passage 33 from discharge chamber 27 be incorporated into crank box 15 the high pressure refrigerant gas amount and flow out to balance between the amount of refrigerant gas of suction chamber 26 from crank box 15 by discharge passage 32.Controlled by this balance of aperture of regulating displacement control valve 34.Change in response to the variation in pressure in the crank box 15 by pressure in the cylinder hole 21 of piston 22 and the difference between the pressure in the crank box 15, thereby change is with respect to the tilt angle of the dividing plate 19 of live axle 16.Therefore, compressor changes the stroke of piston 22, and changes its discharge capacity subsequently.
When the pressure in crank box 15 descended, the tilt angle of dividing plate 19 increased, thereby increased the discharge capacity of compressor.The dividing plate 19 that two dot and dash line are represented in Fig. 1 is in the tilt angle with lug plate 18 contacted maximums.On the other hand, when the pressure in the crank box 15 rose, reduced at the tilt angle of dividing plate 19, thereby reduce the discharge capacity of compressor.The dividing plate of representing with solid line in Fig. 1 19 tilts at its place, minimal tilt angle.
The refrigeration path of the air regulator of vehicle (perhaps refrigeration cycle) comprises compressor and external refrigeration path 36, and it connects discharges chamber 27 in suction chamber 26.Carbon dioxide or chloro-fluoro-hydrocarbons can use as refrigeration agent.External refrigeration passage 36 comprises condenser 37, receiving box 38, and expansion valve 39 and vaporizer 40, they are all to be provided with towards the order of this kind shown in the suction chamber 26 from exhaust chamber 27.Pressure transducer 41 is arranged on and connects condenser 37 in the refrigerating channel of receiving box 38, and is suitable for by connecting line 41, and data input unit 43 and connecting line 44 send power detection signal in amplifier 45.This amplifier 45 transmits discharge capacity-change command signal to displacement control valve 34, to be used to control displacement control valve 34 by connecting line 61.This amplifier 45 stores the data of sending from magnetic sensor 60 about the refrigerant gas flow velocity at this, this will be described subsequently, and a plurality of information, the vehicle interior temperature that from data input unit 43, provides for example, the data of the pressure of the refrigerant gas that from pressure transducer 41, transmits.And amplifier 45 is connected on the engine controller (not shown).
The flowmeter that is shown specifically in Fig. 2 to 4 is provided on the upper surface of cylinder body 12.More specifically, flowmeter is provided on the flange 46 of the upper surface that is connected to cylinder body 12.This flange 46 comprises removable main body or the guiding valve 53 that is arranged in the flange 46, as the helical spring 56 of the push mechanism that is used to promote guiding valve 53 be fixed on the lip-deep magnetic sensor 60 of flange 46.
When flange 46 is connected on the cylinder body 12, in flange 46, form flange passageway.As shown in Figure 2, flange passageway comprises high pressure and low- voltage space 48a and 48b, they interconnect by the throttle valve 52 that the separator 46a by flange 46 forms, flow channel 51, it links to each other with low-voltage space 48b, accommodating chamber 49, and it links to each other with low-voltage space 48b, and communication passage 50, it connects high-pressure channel 48a in accommodating chamber 49.High pressure and low- voltage space 48a and 48b are separately positioned on the upstream and downstream place of throttle valve 52.Guiding valve 53 is arranged in the accommodating chamber 49, so that slide with predetermined interval therein.
Still referring to Fig. 2, guiding valve 53 is with cylindrical shape formation and have top major diameter part 54 and bottom small diameter portion 55.Between the inwall of bottom small diameter portion 55 and accommodating chamber 49, form the gap, and helical spring 56 is provided at and is used for the gap that advances guiding valve 53 to make progress.Helical spring 56 has predetermined spring constant, makes that guiding valve 53 is arranged on any preposition when guiding valve 53 is accepted different pressures, and this will describe subsequently.Magnet 57 is embedded in the top major diameter part 54 of guiding valve 53.The top major diameter not external diameter of part 54 is substantially equal to the internal diameter of accommodating chamber 49, and small gap is formed between the top major diameter part 54 and accommodating chamber 49 of guiding valve 53, and it has this width of the sliding movement that allows guiding valve 53.Mating part 58 with hole are installed in the lower end of accommodating chamber 49, being used to support the lower end and the helical spring 56 of bottom small diameter portion 55, and prevent that guiding valve 53 and helical spring 56 are separated from from accommodating chamber 59.The upper end face of top major diameter part 54 is that pressure is accepted face, and it is received in the pressure among the high-pressure space 48a, and the lower end surface of bottom small diameter portion 55 is that pressure is accepted face, and it accepts the pressure among the low-voltage space 48b.
By assembly 59, the relation with in the face of the magnet 57 of guiding valve 53 is fixed on the surface of flange 46, to be used to detect the Magnetic flux density of magnet 57 as the magnetic sensor 60 of detecting sensor.The gap that magnetic sensor 60 is predetermined at interval with flange 46 directly is sent to magnetic sensor 60 with the heat that prevents housing 11.And assembly 59 is formed by heat insulator, and for example rubber or resin are sent on the magnetic sensor 60 with the heat that prevents flange 46.
As mentioned above, the high pressure refrigerant gas that supplies to high-pressure space 48a flows among the low-voltage space 48b by throttle valve 52 under the situation that reduces pressure.The high pressure refrigerant gas of high-pressure space 48a also is incorporated in the accommodating chamber 49 by communication passage 50.The pressure of the high pressure refrigerant gas in high-pressure space 48a is received by the upper-end surface of top major diameter part 54, low pressure refrigerant gas in low-voltage space 48b is received by the lower end surface of bottom small diameter portion 55 simultaneously, therefore, the differential pressure action between them is on guiding valve 53.Therefore, guiding valve 53 vertical movement under differential pressure action.When changing by displacement control valve 34 discharge capacities, the refrigerant gas amount of discharging from discharge chamber 27 also changes.Therefore, the pressure reduction that acts on the guiding valve 53 changes, and guiding valve 53 moves up and down with response pressure reduction.In Fig. 3, when discharge capacity increased, pressure reduction increased to move down guiding valve 53.In Fig. 4, when discharge capacity was in maximum value, guiding valve 53 was in extreme lower position.
When guiding valve 53 moves in response to pressure reduction, change about the Magnetic flux density of the magnet of magnetic sensor 60.Based on magnetic sensor 60 detected Magnetic flux densities, the flow velocity of refrigerant gas is known.Amplifier 45 calculates the current discharge capacity of compressor based on the flow speed data of the refrigerant gas that obtains from magnetic sensor 60, and implements the feedback control of displacement control valve 34.Therefore, the discharge capacity of compressor can obtain suitable control.In addition, the moment of torsion of compressor can calculate based on the flow speed data of the refrigerant gas that obtains from magnetic sensor 60.Therefore, amplifier 45 is implemented the feedback control of engine controller in response to flow velocity.Therefore, the control that the engine speed of vehicle can be suitable.
The adjusting and the calibration of flowmeter of the compressor of first preferred embodiment will be described below.In first preferred embodiment, flange 56 provides guiding valve 53, helical spring 56, mating part 58, magnetic sensor 60 and assembly 59.Therefore, be installed at flange 46 under the state of housing 11 of compressor, the parts that are used to detect flow velocity must not regulated and be calibrated.As shown in Figure 5, for example, flange 46 breaks away from from compressor, and is installed to the regulator T that is used for flowmeter.Regulator T forms the TCH test channel of the flange passageway that is similar to compressor.Make to regulate and calibrate required refrigerant gas and in regulator T and flange 46, flow, and be determined according to the output of the flow velocity magnetic sensor 60 of refrigerant gas.If be different from the actual flow velocity of the refrigerant gas in regulator T and flange 46, implement to regulate and calibration being used to detect on the parts of flow velocity based on the flow velocity of the refrigerant gas of the output of magnetic sensor 60.
This adjusting comprises the position of regulating magnetic sensors 60 with respect to assembly 59, the propelling force of adjusting color screw spring 56, and be relevant to the position of guiding valve 53 regulating magnets 57.This calibration comprises the output of calibrating magnetic sensor 60.In a large amount of compressors of making, when using regulator T to implement adjusting and calibration, flange 46 can not be installed on each compressor.
The compressor of first preferred embodiment has following advantageous effect.
(1) flange 46 provides guiding valve 53, helical spring 56, mating part 58, the assembly 59 of magnetic sensor 60 and formation flowmeter.Handle when being independent of the housing 11 of compressor when flange 56, be installed at flange 46 under the state of housing 11 of compressor, each parts of flowmeter must not regulated and be calibrated.Therefore, the adjusting of the parts of the flowmeter of compressor and calibration can be than easier enforcements in traditional compressor.
(2) in manufacture process, the flange 46 that provides the parts that are used to detect flow velocity is handled the housing 11 that is independent of compressor.Therefore, being used to detect the adjusting and the calibration of the parts of flow velocity can automation.
(3) packing ring 47 that is formed by heat insulator is inserted between flange 46 and the housing 11, thereby makes the heat of housing 11 be difficult to be sent on the flange 46.Therefore, the unfavorable effect of heat is suppressed on magnetic sensor 60.In addition, keep the assembly 59 of magnetic sensor 60 to form by heat insulator, and magnetic sensor 60 and the flange 60 predetermined interval that is separated by.Therefore, 60 heat transmission is further suppressed from housing 11 to magnetic sensor.
Referring to Fig. 6, the compressor of second preferred embodiment will be described below.Second preferred embodiment is in that magnetic sensor is installed is different with first preferred embodiment on the structure of flange.The basic structure of second preferred embodiment is similar to the structure of first preferred embodiment, and therefore, will no longer repeat for the description of like.
Referring to Fig. 6, flange 71 has flange passageway, and it comprises hyperbaric chamber 72, communication passage 74, and flow channel 75 and branched bottom 76, this branched bottom 76 is connected with accommodating chamber 73, and this accommodating chamber 73 is formed in the flange 71 and is connected on the communication passage 74.Flange 71 has the space 85 that is formed on above the accommodating chamber 73, and magnetic sensor 84 is arranged in the space 85 by the assembly 83 that is formed by heat insulator.C ring 82 is arranged in the space 85 below the assembly 83,85 detaches from the space to be used for preventing assembly 83 and magnetic sensor 84.Removable main body or guiding valve 77 are arranged in the accommodating chamber 73 and have top small diameter portion 78, bottom major diameter part 79 and magnet 81.Guiding valve 77 is promoted down in the communication passage 74 by helical spring 80.When pressure reduction did not act on the guiding valve 77, guiding valve 77 contacted with the bottom of the inwall of communication passage 74.When magnet 81 during near magnetic sensor 84, amplifier is bigger based on the pressure reduction that the output of magnetic sensor 84 identifies between hyperbaric chamber 72 and flow channel 75.When magnet 81 during away from magnetic sensor 84, amplifier is less based on the pressure reduction that the output of magnetic sensor 84 identifies between hyperbaric chamber 72 and flow channel 75.Second preferred embodiment provides the advantage identical with first preferred embodiment.
The invention is not restricted to first to the second above-mentioned preferred embodiment, but can also implement, as following example with different interchangeable embodiments.
In above-mentioned first and second preferred embodiments, the vertical slip of removable main body or mobile.Selectable, removable main body can go up slip in any direction or move, for example the width direction of compressor or longitudinal direction.In this case, removable main body is slided and the direction setting of moving is installed to position on the housing corresponding to flange, perhaps is provided with the mounting point of flange irrelevant.
In above-mentioned first and second preferred embodiments, detected at the flow velocity of discharging refrigerant gas on the side.Selectable, the flow velocity of the refrigerant gas on the suction side can be detected.For example, flange can be arranged between the suction chamber and external refrigeration path of compressor, and provides removable main body, and magnetic sensor etc. are to be used to detect the flow velocity of refrigerant gas on the suction side.
In above-mentioned first and second preferred embodiments, throttle valve is provided in the flange passageway, and the pressure reduction between the upstream and downstream pressure of throttle valve is detected by detecting sensor.Selectable, detecting sensor can be check valve-type, and it comes to open or close in response to the resistance of relative fluid in flange passageway as safety check.
In above-mentioned first and second preferred embodiments, flange is formed by metal.Selectable, flange can be formed by heat insulator, for example resin etc.Under this situation, with respect to the situation of using metal rim, heat is difficult to be sent on the magnetic sensor.Therefore, the material that is used for packing ring and assembly is not necessarily limited to heat insulator.And packing ring and assembly can be removed.Under the situation of removing packing ring and assembly, magnetic sensor directly is installed on the flange.
The first and second above-mentioned preferred embodiments show the example of fixing throttle valve respectively, and the example that uses the variable throttle valve of removable main body.As long as the structure that provides makes removable main body in response to the pressure reduction chamber movably, the hyperbaric chamber, communication passage, flow channel and branched bottom can change arbitrarily.
In above-mentioned first and second preferred embodiments, the discharge capacity of control valve is controlled based on the suction pressure of introducing the passage introducing by first pressure.Displacement control valve can be connected to the external refrigeration path and replaces in response to the control valve of the exercisable control of pressure reduction between control signal and 2 by introduce passage by second pressure, perhaps by its electromagnetic force pass of control valve body/close solenoid valve to replace operationally.
Therefore, current example and embodiment think example rather than restriction, and the invention is not restricted to detailed content given herein, but can make amendment in additional claim scope.
Claims (11)
1. compressor with variable displacement, it comprises:
Housing with cylinder hole and crank box;
Be formed on the refrigerating channel in the housing, this refrigerating channel comprises suction pressure zone and discharge pressure region;
Be arranged on the piston in the cylinder hole;
Be arranged on the dividing plate in the crank box;
Be connected to the flange on the housing, this flange is formed for connecting the flange passageway of refrigerating channel and external refrigeration path;
According to the movably removable main body of the flow velocity of the refrigerant gas in flange passageway; This removable main body has magnet; With
Detect the detecting sensor of the Magnetic flux density of magnet, its central diaphragm tilt angle is according to pressure in crank box and controlling by the pressure reduction between the pressure in the cylinder hole of piston, the supply passage of the pressure of pressure in crank box by being used for supplying with discharge pressure region in the crank box, and the pressure that is used for discharging crank box is regulated to the discharge passage in suction pressure zone, and the flow velocity of refrigerant gas detects based on the detected Magnetic flux density of detecting sensor
It is characterized in that:
Removable main body movably is arranged in the flange;
Detecting sensor is fixed to or in flange; With
Provide at flange under the situation of removable main body and detecting sensor, flange can be connected to and can break away from housing.
2. compressor with variable displacement as claimed in claim 1, wherein heat insulator is provided between flange and the housing.
3. compressor with variable displacement as claimed in claim 2, wherein thermal insulation part is the packing ring that is formed by heat insulator.
4. compressor with variable displacement as claimed in claim 1, wherein throttle valve is provided in the flange passageway, and removable main body is movably by the pressure reduction between the pressure in the flange passageway of throttle valve upstream and downstream.
5. compressor with variable displacement as claimed in claim 4, wherein throttle valve is formed by the separator of flange.
6. compressor with variable displacement as claimed in claim 1, wherein flange passageway comprises and is used to be provided with removable main body accommodating chamber therein.
7. compressor with variable displacement as claimed in claim 1, wherein detecting sensor is fixed on the flange by assembly, makes the gap that detecting sensor and flange are predetermined at interval.
8. compressor with variable displacement as claimed in claim 7, wherein assembly is formed by heat insulator.
9. compressor with variable displacement as claimed in claim 1, wherein detecting sensor is fixed in the flange by assembly.
10. compressor with variable displacement as claimed in claim 9, wherein assembly is formed by heat insulator.
11. compressor with variable displacement as claimed in claim 1, its flange is formed by heat insulator.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006133838A JP2007303416A (en) | 2006-05-12 | 2006-05-12 | Variable displacement compressor |
| JP2006133838 | 2006-05-12 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101070839A true CN101070839A (en) | 2007-11-14 |
Family
ID=38353880
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007101029007A Pending CN101070839A (en) | 2006-05-12 | 2007-05-11 | Variable displacement compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20070264131A1 (en) |
| EP (1) | EP1855003A2 (en) |
| JP (1) | JP2007303416A (en) |
| KR (1) | KR100834335B1 (en) |
| CN (1) | CN101070839A (en) |
| BR (1) | BRPI0703889A (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007263097A (en) * | 2006-03-30 | 2007-10-11 | Toyota Industries Corp | Flow detection device in variable displacement compressor |
| JP4558060B2 (en) * | 2008-04-22 | 2010-10-06 | トヨタ自動車株式会社 | Refrigeration cycle equipment |
| JP5697024B2 (en) * | 2010-12-22 | 2015-04-08 | サンデン株式会社 | Compressor |
| JP6101892B2 (en) | 2013-04-24 | 2017-03-29 | 株式会社テージーケー | Variable displacement compressor and flow sensor mounting structure |
| JP6223715B2 (en) * | 2013-05-29 | 2017-11-01 | サンデンホールディングス株式会社 | Flow rate detection device, and compressor and refrigeration device provided with the flow rate detection device |
| KR101984509B1 (en) | 2014-03-19 | 2019-05-31 | 한온시스템 주식회사 | Device for measuring amount of refrigerant flow in compressor |
| CN106461698B (en) | 2014-04-11 | 2020-08-11 | 罗伯特·博世有限公司 | Wheel speed sensor |
| CN104806501B (en) * | 2015-05-06 | 2016-06-08 | 安徽江淮汽车股份有限公司 | automobile air conditioner compressor torque control method and device |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4507976A (en) * | 1982-07-14 | 1985-04-02 | Morris Shamos | Flow meter with hall effect sensor and method |
| AT388809B (en) * | 1985-10-15 | 1989-09-11 | Avl Verbrennungskraft Messtech | MEASURING ARRANGEMENT, METHOD FOR ZERO-POINT ADJUSTMENT OF THE DIFFERENTIAL PRESSURE TRANSMITTER IN A MEASURING ARRANGEMENT, AND MEASURING DISC FOR A MEASURING ARRANGEMENT FOR FLOW MEASUREMENT OF FLUID, PREFERRED GAS FLOWS |
| JPS63177715U (en) * | 1987-05-09 | 1988-11-17 | ||
| EP0533958B1 (en) * | 1991-04-12 | 1997-07-09 | Hitachi Construction Machinery Co., Ltd. | Hydraulic drive system for a construction machine |
| JP3303333B2 (en) * | 1992-06-09 | 2002-07-22 | 株式会社豊田自動織機 | Capacity detection device for variable capacity compressor |
| JP4081965B2 (en) * | 2000-07-07 | 2008-04-30 | 株式会社豊田自動織機 | Capacity control mechanism of variable capacity compressor |
| JP2002332962A (en) * | 2001-05-10 | 2002-11-22 | Toyota Industries Corp | Control valve for variable displacement compressor |
| JPWO2002101237A1 (en) * | 2001-06-06 | 2004-09-30 | 株式会社テージーケー | Variable capacity compressor |
| JP4107141B2 (en) * | 2003-02-21 | 2008-06-25 | 株式会社デンソー | Limiter device |
| JP4100254B2 (en) * | 2003-05-23 | 2008-06-11 | 株式会社豊田自動織機 | Capacity control mechanism of variable capacity compressor |
| JP4173111B2 (en) * | 2004-01-29 | 2008-10-29 | 株式会社テージーケー | Control valve for variable capacity compressor |
-
2006
- 2006-05-12 JP JP2006133838A patent/JP2007303416A/en not_active Withdrawn
-
2007
- 2007-05-03 EP EP07107453A patent/EP1855003A2/en not_active Withdrawn
- 2007-05-07 US US11/800,892 patent/US20070264131A1/en not_active Abandoned
- 2007-05-11 CN CNA2007101029007A patent/CN101070839A/en active Pending
- 2007-05-11 KR KR1020070046035A patent/KR100834335B1/en not_active IP Right Cessation
- 2007-05-11 BR BRPI0703889-5A patent/BRPI0703889A/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| US20070264131A1 (en) | 2007-11-15 |
| KR100834335B1 (en) | 2008-06-02 |
| EP1855003A2 (en) | 2007-11-14 |
| KR20070109946A (en) | 2007-11-15 |
| JP2007303416A (en) | 2007-11-22 |
| BRPI0703889A (en) | 2008-03-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101070839A (en) | Variable displacement compressor | |
| JP3789023B2 (en) | Solenoid control valve | |
| US20040003603A1 (en) | Method of controlling refrigeration cycle | |
| KR100494210B1 (en) | Control valve of variable displacement compressor | |
| US7493829B2 (en) | Flow meter for variable displacement compressor | |
| KR19980080242A (en) | Electronic Control Valve | |
| US6682314B2 (en) | Control valve for variable displacement type compressor | |
| JP2005069072A (en) | Capacity control valve | |
| US20040165994A1 (en) | Displacement varying structure of variable displacement compressor | |
| JP4128433B2 (en) | Control method of refrigeration cycle | |
| JP2007211701A (en) | Flow rate detection device in variable displacement compressor | |
| US7014427B1 (en) | Capacity controller of capacity variable compressor | |
| JP2007211703A (en) | Flow rate detection device in variable displacement compressor | |
| KR20100013736A (en) | Displacement control valve of variable displacement compressor | |
| US6638026B2 (en) | Control valve for variable displacement compressor | |
| US8186172B2 (en) | Structure for sensing refrigerant flow rate in a compressor | |
| JP2021511461A (en) | Compressor control device, electronic control valve used for it, and electric compressor including it | |
| EP1359488B1 (en) | Electrically operated compressor capacity control system with integral pressure sensors | |
| JP2007218139A (en) | Flow rate detection device for variable displacement type compressor | |
| JP3648374B2 (en) | Solenoid control valve | |
| JP4173073B2 (en) | Control valve for variable capacity compressor | |
| JP2003314444A (en) | Control valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |