EP1899605B1 - Steuerungsventil für einen kältemittelverdichter und kältemittelverdichter - Google Patents

Steuerungsventil für einen kältemittelverdichter und kältemittelverdichter Download PDF

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Publication number
EP1899605B1
EP1899605B1 EP06776125A EP06776125A EP1899605B1 EP 1899605 B1 EP1899605 B1 EP 1899605B1 EP 06776125 A EP06776125 A EP 06776125A EP 06776125 A EP06776125 A EP 06776125A EP 1899605 B1 EP1899605 B1 EP 1899605B1
Authority
EP
European Patent Office
Prior art keywords
control
pressure
suction
refrigerant compressor
delivery
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.)
Not-in-force
Application number
EP06776125A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1899605A1 (de
Inventor
Joan Aguilar Rojas
Roland Cäsar
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.)
Mercedes Benz Group AG
Original Assignee
Daimler AG
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 Daimler AG filed Critical Daimler AG
Priority to PL06776125T priority Critical patent/PL1899605T3/pl
Publication of EP1899605A1 publication Critical patent/EP1899605A1/de
Application granted granted Critical
Publication of EP1899605B1 publication Critical patent/EP1899605B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B2027/1809—Controlled pressure
    • F04B2027/1813—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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge 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
    • 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
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1831—Valve-controlled fluid connection between crankcase and suction 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
    • 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

Definitions

  • the invention relates to a control valve for a refrigerant compressor according to the preamble of patent claim 1 and a refrigerant compressor according to the preamble of patent claim 8.
  • a refrigerant compressor having a plurality of operating in a drive housing displacement piston, which are driven by a via a drive shaft, a pulley and the belt drive of a drive assembly of a motor vehicle driven swash plate in its conveying movement.
  • the pistons define an axial lifting movement of the associated cylinder bores.
  • the delivery rate of the refrigerant compressor is adjustable via the drive housing pressure p c acting in the cavity of the drive housing, which acts on the rear side facing away from the displacement side of the piston.
  • the Drive housing of the refrigerant compressor with the suction pressure p s having suction chamber and the delivery pressure p D having delivery chamber connected. It is commonly set in the conveying operation of the compressor via a rigidly throttled, permanently open line to the suction chamber and controlled by a valve throttled connection to the delivery chamber of the drive housing pressure p c .
  • the EP 1 033 489 A2 discloses a control valve for a refrigerant compressor for controlling the delivery rate of the refrigerant compressor via adjustment of a drive housing pressure p c of the refrigerant compressor, wherein a control body of the control valve is electromagnetically and driven by a pressure cell and the control body on the one hand a delivery-side control line between a high pressure p D of the compressor loaded delivery chamber and the drive housing of the compressor and on the other hand, a suction-side control line between the drive housing and a suction pressure p s acted upon suction chamber of the compressor changeable throttles and / or shut-off and thereby shut off both the delivery side and the suction side control line.
  • a valve with essentially the same construction and function is also in the EP 0 396 017 A disclosed.
  • the object of the invention is to further improve delivery capacity and control of the refrigerant compressor.
  • a refrigerant compressor or a compressor controlled by such a valve has delivery pistons operating in a drive housing, which perform in an associated cylinder bore of the drive housing alternating strokes.
  • the delivery pistons are moved between a displacement end position delimiting a displacement movement on the one hand and an intake stroke which delimits an intake movement.
  • the displacement movement is directed towards a cylinder bore of the drive housing of the displacement side of the delivery piston opposite limiting valve plate out.
  • the valve plate has two counter-closing check valves, via which the cylinder bore is connected on one side with a suction chamber of the compressor and on the other hand with a delivery chamber of the compressor.
  • the delivery pistons are driven by a swashplate rotating in the drive housing and adjustable in its angle of attack.
  • the swash plate is driven via an associated axle, a seated on the axle pulley and the belt drive of a drive unit of the motor vehicle.
  • the drive housing of the refrigerant compressor forms in the rotation range of the swash plate a with the displacement side of the delivery piston remote from the rear side in communication, hermetically sealed cavity in which.ein drive housing pressure p c acts.
  • drive housing pressure p c acts.
  • a change in the angle of attack of the swash plate is done by adjusting the force acting on the rear sides of the piston drive housing pressure p c .
  • the cavity of the drive housing via two control lines on the one hand with a delivery pressure p D having delivery chamber and the other with a suction pressure p S having suction chamber of the refrigerant compressor is connected, these lines are controllable via a control valve of the refrigerant compressor.
  • the control valve has a control body acting on both control lines, which is electromagnetically driven, so that via an associated control, for example, acting against a spring force magnetic force and about a control position of the control body is adjustable.
  • the control valve and / or refrigerant compressor are both the delivery side and the suction side Control line controlled throttleable or lockable.
  • the suction-side control line can be closed or greatly throttled during operation of the compressor, so that the bypass flow of conventional control valves and refrigerant compressors, which is discharged at the unchangeable throttled suction-side control line from the drive housing to the suction chamber, greatly reduced to improve the cooling capacity, or avoided.
  • the present control valve or the refrigerant compressor on a control body which is driven by a pressure cell is.
  • a pressure cell allows the drive of the control body as a function of pressure variables or pressure differences occurring at the refrigerant compressor or at the refrigerant circuit, so that certain operating pressure states of the refrigerant compressor can flow directly into the control of the control body.
  • the pressure box allows an improvement of the control valve by taking into account direct state variables at the refrigerant compressor.
  • a pressure box for driving the control body which monitors the pressure difference of atmospheric pressure p A of the vehicle environment and suction pressure p s .
  • the control of the control body for mutual opening of the delivery-side control line to reduce the delivery at too low suction pressure and the suction-side control line to increase the flow rate of the refrigerant compressor at high suction pressure. Due to the direct detection of the suction pressure of the refrigeration system and a suction pressure-dependent control of the refrigerant compressor in particular cooling losses and fluctuations, which may occur, for example, in a evaporator temperature-dependent control avoided.
  • the magnetic reaction of the solenoid controlling the control body takes place directly on the control body or an armature fastened to the control body.
  • the force of the electromagnetic effect of the coil on the control body of the control valve act directly and can be considered particularly advantageous as a control variable component given Kraftwegönn the control body, for example, for throttling control of an associated opening.
  • This is particularly advantageous in a combined control of the control body with the aid of various force-applying elements, such as springs or pressure cans.
  • control valve or the refrigerant compressor in undisturbed operation and condition of the associated refrigeration system, the control body occupies a rest position when switching off the refrigeration system operation in which the suction-side control line is locked. This can be achieved by appropriate vote of the involved Feder Thetician drive and switching elements, preferably in this state, the control valve and the associated control is de-energized.
  • the control valve and the associated control By blocking the suction-side control line of the control valve, a deposition of refrigerant condensate in the drive housing of the refrigerant compressor is reduced or avoided during standstill of the refrigeration system, so that when restarting the refrigerant compressor after prolonged shutdown of the refrigeration system improved start cooling capacity is reached.
  • a particular embodiment of the control valve provides that the pressure cell brings the control body at lowering the suction pressure below an associated minimum operating value in a position releasing the conveying side control line. It is thereby achieved that, for example, in the case of leaks in the refrigerant circuit, damage to the refrigerant compressor caused by readjustment of the refrigerating capacity control does not occur if the swash plate is over-tightened, but that by disengaging the delivery-side control line Swash plate brought into neutral position and thus damage can be avoided.
  • control valve and / or the compressor shuts off both control lines simultaneously in a control position. It can thus be controlled in addition to a conveyor-side control line releasing and thus the delivery line lowering control mode, and the suction-side control line releasing and thus increasing the flow rate of the refrigerant compressor control operation holding mode, in which both the suction side and the feed side control line is locked, and thus the set flow rate can be maintained without further control interventions, as well as without the flow rate reducing Beipassstrom the refrigerant via the control lines.
  • control valve and / or the refrigerant compressor In order to ensure a particularly easy to control and functionally reliable operation of the control valve and / or the refrigerant compressor is provided in an embodiment of the control valve or the compressor that the control body is movable over an intermediate position away between two end positions, wherein blocked in a first end position, the conveyor-side control line is, in the intermediate position both Control lines are locked and the suction-side control line is locked in a second end position.
  • control valve or the refrigerant compressor resulting from combinations of the above-mentioned embodiments, or from the drawings and their description.
  • the figures show an embodiment of a control valve or that of an associated refrigerant compressor.
  • FIG. 1 shows a refrigerant compressor of a motor vehicle 1, which is driven by a belt pulley 12 integrated in the belt drive of the drive unit of the motor vehicle.
  • the drive power is transmitted via the pulley 12 and a drive shaft 13, which is arranged sealed in a hermetically sealed drive housing 10 of the refrigerant compressor 1 to a rotatably connected to the drive shaft 13 swash plate 14.
  • the swash plate 14 In the drive housing 10 are provided with the swash plate 14 in engagement pistons 11, which perform an alternating stroke in an associated cylinder. Of the plurality of circumferentially distributed piston 11 only one is shown in the drawing.
  • the rotating swash plate 14 causes the drive of the piston 11 in the lifting movement.
  • the opposite, dead center of the stroke movement of the pistons which ends the suction movement, is variable.
  • the dead-end of the stroke movement ending the suction movement is determined by a force equilibrium between the pressure prevailing in the drive housing p c , which acts on the opposite side of the delivery side of the piston 11, and the pressure acting on the delivery side during the intake movement.
  • the refrigerant compressor 1 delivers refrigerant sucked to the suction line 4 of the refrigerant circuit with then increased pressure to the pressure line 3 of the refrigerant circuit.
  • the suction line 4 is connected to the refrigerant compressor 1 to the suction chamber 102, from which the piston 11 suck refrigerant.
  • the pressure line 3 of the refrigerant circuit is connected to the refrigerant compressor 1 to the delivery chamber 101, in which the piston 11 promote the compressed refrigerant.
  • the delivery pistons 11 of the refrigerant compressor are connected to the suction chamber 102, on the one hand, and the delivery chamber 101, on the other hand, via two non-return valves which determine the delivery direction and interlock.
  • the delivery-side control line 21 is connected to the conveying chamber 101 having the delivery pressure p c
  • the suction-side control line 22 is connected to the suction chamber 102 having the suction pressure p s .
  • the control line 21 is connected via the control chamber 211 and the lead portion 29 with the cavity of the drive housing 10.
  • opening the suction-side control line 22 this is connected via the associated control chamber 221 and the supply line section 28 with the cavity of the drive housing 10.
  • control valve 2 For controlled opening of the two control lines 21 and 22, the control valve 2 has a control body 20 which, when moving in the control bore in the two limiting the stroke of the control body 20 end positions of the control valve 2, the control lines 21 and 22 alternately opens and in one between the end positions arranged intermediate position closes both control lines 21 and 22, wherein the control body 20, the control lines in each case seals against the associated control chamber.
  • the control body 20 of the control valve 2 is driven in the control bore of the control valve 2 by means acting on the armature 201 of the control body 20 magnetic coil 24 and on the other hand by a resilient, in the interior with suction pressure p s acted upon pressure cell 23.
  • a regulated flow rate of the refrigerant compressor 1 an increase in the current flowing through the coil 24 via the increase in the associated magnetic force causes the control body 20 to move in the direction of releasing the suction-side control line 22, which is connected to the suction chamber 102 having the suction pressure p s is.
  • the control line 22 is released relative to the control chamber 221 of the control valve 2 and can reduce the drive housing pressure p c via the supply line section 28 of the control line.
  • suction pressure p s increases, a movement of the control body in the direction of an opening of the suction-side control line takes place, as in the case of the increase of the current flowing through the coil 24. As described, this results in an increase in the delivery rate of the refrigerant compressor, which in turn results in a decrease in the suction pressure p s in the suction chamber 102.
  • a reduction of the current flowing through the magnetic coil 24 and a decrease in the suction pressure p s in the suction chamber 102 of the refrigerant compressor both cause a rectified movement of the control body 20 of the control valve 2 of the refrigerant compressor in which starting from a control state of the control valve of the control valve 21 and 22 Control body 20 is moved in the direction of an opening of the delivery-side control line 21.
  • the current is turned off at the solenoid coil 24, thereby causing with the aid of the resilient action of the pressure cell 23 and any additional spring of the control body 20 in a conveyor-side control line 21 releasing and the suction-side control line 22 blocking position is moved.
  • the delivery-side control line 21 check valve, not shown in the drawing is usually provided.
  • the present coupled control of the control body - by the pressure can on the one hand and the solenoid on the other hand low vibration and easy to control operated.
  • a desired suction pressure With a constant excitation of the magnetic coil 24 can thus be adjusted via the additionally coupled to the control body 20 pressure cell 23, a desired suction pressure.
  • Increases the suction pressure p s for example, by stronger thermal load of the evaporator in the refrigerant circuit is brought by the pressure cell 23 of the control body 20 in a suction-side control line 22 releasing control position, so that as a result of the drive housing pressure p c reduced, the angle of attack of the control disk 14 and so that the capacity of the compressor - to compensate for the increased thermal load - be increased.
  • the suction pressure p s decreases until the level of the desired suction pressure is reached and the suction-side control line 22 is closed again via the pressure box 23 acting on the control body 20.
  • an exactly inverse action by effected by the pressure cell 23 enable the delivery-side control line 21.
  • the control circuit of the proposed control valve 2 and the refrigerant compressor 1 is small and therefore particularly stable, so that by regulating and adjusting the suction pressure control engagement of the pressure cell 23 20 control vibrations of the refrigeration cycle can be prevented on the control body. Changing thermal and drive-related loads on the refrigeration cycle are immediately recorded and readjusted.
  • About the advantageously strongly attenuated variable excitation of the solenoid coil 24 is a basic refrigerant line from the outside adjustable on the control valve 2.
  • FIGS. 2 to 4 show a conceptual representation of an embodiment of the control valve 2 of a refrigerant compressor 1 of a motor vehicle in various control positions.
  • the control valve is the same in all cases with regard to the components and their control-independent arrangement, so that descriptions of corresponding objects and situations in individual figures also apply to the other figures.
  • control valve 2 has in a housing on a control body 20 which is arranged with its cylindrical cross-section within a coordinated cylindrical control bore of the control valve 2 movable.
  • the control body 20 has partial bodies of different diameters.
  • On the control bore of the control valve 2 are on the one hand connected to the 'delivery pressure p D conveying side connected control line 21, one with the suction pressure p s having suction side connected control line 22, and the supply line sections 28 and 29 of the control lines to Drive housing of the refrigerant compressor connected.
  • the central locking body of the control body 20 is divided by completely circumferential sealing abutment against the outer wall of the cylindrical control bore this control bore in a delivery-side control chamber 211 and a suction-side control chamber 221nd These are each connected to the associated drive housing side connected control line sections 28 and 29.
  • the control body 20 may be divided into two adjacent in the axial direction locking body, which are connected by a relative to the two locking bodies in the radial direction constricted push rod, wherein the push rod releases a central control chamber, which is bounded laterally by the blocking bodies.
  • the locking body alternately release the two control lines with respect to the central control chamber, which is connected via a supply line section with the cavity of the drive housing.
  • an electromagnetically operable control coil 24 is arranged in the interior of the control bore. This magnetically acts on an associated armature 201 of the control body 20.
  • the control body 201, the control bore in the radial direction substantially filling at the central opening of the coil 24 is arranged.
  • the armature 201 is connected via a radially reduced as armature connecting rod 202, the local control chamber 211 free-saving region of the control body 20 to the central Störisson.
  • a coil spring 25 In the inner opening of the coil 24 is a coil spring 25, which supports the control body 20 against the magnetic attraction direction.
  • An excitation of the coil 24 causes by the magnetic effect of a tightening of the armature 201 of the control body 20 so that it is moved by increasing the current in the coil 24 with its central locking body in the direction of the delivery-side control line 21.
  • the control body 20 On the opposite side of the armature, the control body 20 has a again designed as a connecting rod 203 in the radial direction executed portion which is sealed carried out through an associated bore of the housing of the control valve to a pressure can chamber 261 and connected to a pressure cell 23.
  • the pressure can chamber 261 is connected via a supply line 26 with atmospheric pressure vehicle environment.
  • the resiliently designed pressure cell 23 is arranged, which is hermetically sealed with its interior relative to the pressure can chamber, and is connected with its interior via the feed line 27 to the suction pressure p s having suction side of the refrigerant compressor.
  • An increase in the suction pressure p s thus causes a displacement of the locking body of the control body 20 in the direction of the delivery-side control line 21.
  • a reduction of the suction pressure p s causes an opposite movement of the control body 20 in the direction of the suction-side control line 22nd
  • FIG. 2 shows a control state of the control valve 2, in which the central locking body 20, the delivery-side control line 21 via the delivery-side control chamber 211 with the connected to the drive housing of the compressor control line section 29.
  • the central locking body of the control body 20 blocks the suction-side control line 22 relative to the drive housing of the compressor from.
  • This control position is taken in particular in two operating cases of the refrigerant compressor. On the one hand, this is the case when the refrigeration system is switched off, that is to say in a quiescent operating state, and, on the other hand, when controlling a delivery capacity reduction at the refrigerant compressor.
  • the currentless coil 24 of the control valve 2 that at this point no the control body 20 in the direction of the delivery-side control line 21 moving force on the control body 20 is initiated.
  • the resilient action of the pressure cell 23 or in the present case supported by the spring 25 causes against the pressure applied in the pressure box 23 worshipsaug réelle on the suction side of the refrigerant circuit, the assumption of the shown control position of the control body 20 in the control valve 2.
  • the delivery-side control line 21 via the Control chamber 211 and the control line section 29 connected to the drive housing of the refrigerant compressor.
  • suction-side control line is sealed by the central locking body of the control body 20 relative to the drive housing of the compressor, so that the entry of condensing refrigerant over the open suction-side control line is avoided at longer stationary refrigeration cycle.
  • the suction pressure p s on the suction side of the compressor lowers and causes a lowering of the pressure in the supply line 27 connected to the suction side
  • the control body 20 is moved in the direction of the suction-side control line 22 via the connecting rod 203, so that when the suction-side control line 22 is closed, the delivery-side control line 21 is released.
  • control position of the control valve 2 may be similar to the in FIG. 2 shown control position may also be provided as a rest position of the control valve, in which case both the delivery-side control line 21 and the suction-side control line 22 are locked.
  • FIG. 3 illustrated control position of the control valve 2 is taken when the delivery of the refrigerant compressor coincides with the provided by the control of the refrigeration system basic delivery.
  • the direction of force of the magnetic force of the coil 24 rectified force of the suction pressure p s in the pressure cell 23 causes the taking of the position of the control body 20 shown in the control bore of the control valve 2, wherein both the delivery-side control line 21 and the suction side Control line 22 relative to the associated control chambers 211 and 221 or connected thereto and connected to the drive housing 10 of the refrigerant compressor 1 control line section 28 and 29 are locked.
  • control state of the control valve 2 causes an increase in the capacity of the refrigerant compressor, which can be done for example by increasing the demand for the basic cooling through the control of the refrigeration cycle - driven by increased current to the coil 24 or at an unchanged actuated basic cooling via a voltage applied to the refrigerant compressor increased suction pressure p s acting on the pressure cell 23.
  • control positions of the control valve 2 can be taken alternately during operation of the refrigerant compressor by different effects.
  • a displacement of the control body 20 is effected by increasing the current of the coil 24 in the direction of blocking the delivery-side control line and reducing the current of the coil 24 in the direction of blocking the suction-side control line.
  • a change of suction pressure p s which rests in the interior of the pressure cell 23, and / or magnetic force of the coil 24 to the armature 201 causes a change in force in the equilibrium of magnetic force, spring forces of coil spring 25 and pressure cell 23 and pressure can force due to the differential pressures applied there.
  • a changed position of the blocking body 204 of the control body 20 is effected until the setting of a new equilibrium of forces.
  • control valve 2 causes a change in the cooling capacity of the refrigerant compressor and thereby a Saugdruckver selectedung which has a control action against the control intervention counteracting and thus the control body 20 again in holding control position effect.
  • a correspondingly changed energization of the coil 24 causes a change in magnetic force on the armature 201 of the control body 20.
  • the forces are transmitted from the armature 201 via the connecting rod 202 on the central locking body 204 of the control body 20 and the push rod 203 on the active surface of the pressure cell 23 having the front of the pressure cell.
  • An altered magnetic force thus causes the intake of the middle holding position of the control body at a corresponding to the change in the magnetic force changed force of the pressure cell 23 and thus at a corresponding to their effective area changed suction pressure.
  • the target suction pressure can be changed at which the holding control position of the control valve 2 is taken.
  • a variable operating point of the refrigerant compressor can be adjusted, via the pressure box 23 this operating point in direct force equilibrium between magnetic force spring elements involved and force of the pressure cell a substantially constant suction pressure p s belonging to Adjusted via the solenoid coil operating point, or changed balance of power regulates.

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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)
EP06776125A 2005-07-06 2006-07-05 Steuerungsventil für einen kältemittelverdichter und kältemittelverdichter Not-in-force EP1899605B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL06776125T PL1899605T3 (pl) 2005-07-06 2006-07-05 Zawór sterujący dla sprężarki czynnika chłodzącego i sprężarka czynnika chłodzącego

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005031511A DE102005031511A1 (de) 2005-07-06 2005-07-06 Steuerungsventil für einen Kältemittelverdichter und Kältemittelverdichter
PCT/EP2006/006545 WO2007003423A1 (de) 2005-07-06 2006-07-05 Steuerungsventil für einen kältemittelverdichter und kältemittelverdichter

Publications (2)

Publication Number Publication Date
EP1899605A1 EP1899605A1 (de) 2008-03-19
EP1899605B1 true EP1899605B1 (de) 2012-01-18

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ID=37025183

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06776125A Not-in-force EP1899605B1 (de) 2005-07-06 2006-07-05 Steuerungsventil für einen kältemittelverdichter und kältemittelverdichter

Country Status (7)

Country Link
US (1) US7950242B2 (ja)
EP (1) EP1899605B1 (ja)
JP (1) JP4778554B2 (ja)
AT (1) ATE542051T1 (ja)
DE (1) DE102005031511A1 (ja)
PL (1) PL1899605T3 (ja)
WO (1) WO2007003423A1 (ja)

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DE102008031508A1 (de) * 2008-07-03 2009-11-05 Daimler Ag Verfahren zum Steuern einer Kupplungseinrichtung
DE102008047294A1 (de) 2008-09-16 2009-05-14 Daimler Ag Kompressionskälteanlage und Verfahren zum Betreiben einer Kompressionskälteanlage
DE102014206952A1 (de) * 2014-04-10 2015-10-15 Magna Powertrain Bad Homburg GmbH Verdichter mit elektrischer Regelung und mechanischem Zusatzventil

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WO2007003423A1 (de) 2007-01-11
PL1899605T3 (pl) 2012-06-29
ATE542051T1 (de) 2012-02-15
EP1899605A1 (de) 2008-03-19
JP4778554B2 (ja) 2011-09-21
US7950242B2 (en) 2011-05-31
DE102005031511A1 (de) 2007-01-11
JP2009500552A (ja) 2009-01-08

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