EP3899382A1 - Elektromagnetisches proportionalventil und system mit einem proportionalventil - Google Patents
Elektromagnetisches proportionalventil und system mit einem proportionalventilInfo
- Publication number
- EP3899382A1 EP3899382A1 EP19832620.9A EP19832620A EP3899382A1 EP 3899382 A1 EP3899382 A1 EP 3899382A1 EP 19832620 A EP19832620 A EP 19832620A EP 3899382 A1 EP3899382 A1 EP 3899382A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- valve
- proportional valve
- electromagnetic proportional
- armature
- 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
- 239000012530 fluid Substances 0.000 claims abstract description 35
- 230000000903 blocking effect Effects 0.000 claims abstract description 23
- 239000003507 refrigerant Substances 0.000 claims abstract description 13
- 238000007789 sealing Methods 0.000 claims description 21
- 238000001816 cooling Methods 0.000 claims description 10
- 238000004378 air conditioning Methods 0.000 claims description 8
- 230000006835 compression Effects 0.000 description 16
- 238000007906 compression Methods 0.000 description 16
- 230000007704 transition Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00485—Valves for air-conditioning devices, e.g. thermostatic valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
- F25B41/345—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by solenoids
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/61—Types of temperature control
- H01M10/613—Cooling or keeping cold
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/62—Heating or cooling; Temperature control specially adapted for specific applications
- H01M10/625—Vehicles
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M10/00—Secondary cells; Manufacture thereof
- H01M10/60—Heating or cooling; Temperature control
- H01M10/65—Means for temperature control structurally associated with the cells
- H01M10/656—Means for temperature control structurally associated with the cells characterised by the type of heat-exchange fluid
- H01M10/6569—Fluids undergoing a liquid-gas phase change or transition, e.g. evaporation or condensation
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H2001/3286—Constructional features
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/06—Details of flow restrictors or expansion valves
- F25B2341/067—Expansion valves having a pilot valve
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01M—PROCESSES OR MEANS, e.g. BATTERIES, FOR THE DIRECT CONVERSION OF CHEMICAL ENERGY INTO ELECTRICAL ENERGY
- H01M2220/00—Batteries for particular applications
- H01M2220/20—Batteries in motive systems, e.g. vehicle, ship, plane
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/10—Energy storage using batteries
Definitions
- the invention relates to an electromagnetic proportional valve.
- the invention further relates to a system with an electromagnetic proportional valve.
- Valves are generally used to shut off and / or control the flow of a fluid. Simpler valves can only be controlled discretely. This means that they can only be switched on / off, i.e. they can only be opened and closed. However, simply opening and closing the valve is no longer sufficient for many applications. For example, use as an expansion valve, which is used in battery cooling, air conditioning or heat pump systems in order to generate a defined and controllable pressure drop between the condenser (heat emission) and evaporator (cooling), often requires more continuous switching. Overall, continuous switching is therefore often required. Such a continuous or continuous switching can take place, for example, by means of proportional valves which allow the switching positions to change continuously. The volume flow of the fluid can thus be adjusted. Such proportional valves not only allow discrete switching positions with the help of a proportional magnet, but also allow a constant transition of the valve opening.
- the structure of the known proportional valves is very complex, so that they cannot be manufactured easily and inexpensively.
- the increased complexity also frequently leads to individual functions of the proportional valve being disturbed.
- the invention is therefore based on the object of specifying a proportional valve which eliminates the above-mentioned problems and disadvantages of the prior art.
- the solution according to the invention consists in specifying an electromagnetic proportional valve, preferably for refrigerant, which has the following: an armature of an electromagnet, which is arranged to be axially movable between a rest position, an actuation position and work positions and on which an actuation element is arranged; a piston which is designed as a hollow piston and has a first opening to an inlet of the expansion valve at a first axial end region and a second opening to a pressure compensation chamber at a second axial end region; and a locking body which is designed to close the second opening, the piston being arranged axially displaceably and the piston being designed to block a fluid passage as a shut-off element of a main valve device, the fluid passage blocking the main valve device in the rest position of the armature is, wherein the actuating element is designed to act in the actuating position of the armature in such a way that the blocking body at least partially opens the second opening, and wherein the fluid passage of the main valve device is open in the
- An electromagnetic proportional valve is, in particular, a proportionally controllable expansion valve.
- the proportional valve is a continuous valve, which is not only discrete (open / close) switchable, but also allows a constant transition of the main valve opening (the opening that can be blocked by means of the piston). This is the volume flow of the fluid adjustable.
- the electromagnetic proportional valve can be controlled by means of the electromagnet.
- the rest position of the armature is also the position in which the armature is in a de-energized state of a coil of the electromagnet.
- the main valve device and also a pressure compensation valve device formed by means of the blocking body are closed. In this state there is high pressure in the inlet and low pressure in the pressure equalization chamber. The high pressure pushes the piston as a shut-off element of the main valve device into a valve seat. It is only possible to open the main valve device after pressure equalization.
- This pressure equalization takes place as follows: If the current (in the coil) increases, the armature moves into the actuation position. As a result, the actuating element also moves into the actuating position, in which the actuating element acts on the locking body in such a way that it releases the second opening at least in some areas.
- a fluid e.g., a refrigerant
- the fluid flows through a through hole in the piston. In particular, the fluid flows from the inlet through the through hole into the pressure equalization space. Therefore, the pressure between the inlet and the pressure compensation space is balanced.
- the pressure compensation valve device is therefore open. The main valve device is still closed.
- the proportional valve is constructed as a piston valve. This means that the displaceable piston is the shut-off body of the main valve device.
- the working positions are a working area in which the piston is movable and fluid can flow through the main valve device. Preferably, a continuous transition of the main valve opening is completely possible in this area, so that the volume flow of the fluid can be controlled (proportionally) by means of the electromagnet. Even if the entire working area is preferably continuously controllable, it is alternatively sufficient if continuous control is only possible in one area thereof.
- Both the valve seat of the main valve device and the valve seat are preferably the pressure compensation valve device is designed as a metallic valve seat.
- a proportional valve which has a particularly low level of complexity and at the same time is able to optimally perform its function.
- the movement of the armature in the working positions is transmitted directly to the piston.
- the main valve opening can therefore be influenced precisely, so that the volume flow of the fluid can be precisely adjusted.
- the direct dependence between the control current (current in the coil) and the position of the piston means that the flow of the proportional valve can be precisely controlled by means of the control current.
- an attachment is arranged on the second axial end region.
- the attachment closes the second opening of the second axial end region in such a way that the locking body cannot be pressed out of the second opening.
- the attachment also has an axial bore through which the locking body can be actuated by means of the actuating element.
- the actuating element has a projection.
- the projection extends axially in the direction of the locking body.
- the projection can be passed through the attachment. This means that the outside diameter of the projection is smaller than the inside diameter of the axial bore.
- the armature is in contact with the actuating element in the working positions, the actuating element is also in contact with the attachment, and the attachment is also in contact with the piston.
- the force flow from the armature to the actuating element takes place Actuator on the attachment and from the attachment on the piston.
- the actuating element also has a step, by means of which direct, ie direct contact (without an intermediate spring element) between the actuating element and the attachment is possible.
- the proportional valve has a valve bushing in which the inlet and the outlet are arranged, the piston being arranged in a bore in the valve bushing.
- the piston is designed to be axially movable in the valve bushing.
- the high pressure of the inlet presses the piston as part of the main valve device into a valve seat which is formed by the valve bushing.
- the piston has a conical shoulder which is pressed onto a shoulder of the valve bushing.
- the piston has a circumferential sealing surface which blocks the fluid passage of the main valve device with an inner surface of the bore of the valve bushing.
- An overlap of a predetermined length is formed between the circumferential sealing surface of the piston and the inner surface.
- the overlap is the area where the inner surface and the sealing surface are (radially) opposite one another.
- the overlap between the circumferential sealing surface of the piston and the inner surface is a predetermined value.
- the predetermined value, ie the length, can be 1 mm, for example.
- the inlet is axially formed and the outlet is radial.
- the inlet Since the inlet is arranged axially, the high pressure of the inlet presses axially against the piston and thus ensures a safe closed state of the main valve device. On the other hand, the radial sequence does not hinder the function and in particular the switching of the proportional valve.
- the locking body is a ball.
- a ball is particularly easy and inexpensive to manufacture. In addition, this reliably fulfills the locking function of the pressure compensation valve device. Due to their geometrically uniform shape, there is no risk of the ball tilting and blocking the valve.
- the electromagnetic proportional valve has a first spring element, which prestresses the piston in the direction of the actuating element.
- the first spring element presses the piston into its blocking position as a blocking element. If the current is switched off and the electromagnet is no longer supplied with current, the piston can therefore be quickly brought back into the blocking position in which the main valve device is closed.
- the axially displaceable piston is thus biased in the bore of the valve bush by means of a first spring element in the direction of the actuating element (or the electromagnet, or the armature).
- the first spring element is preferably designed as a compression spring.
- the first spring element is particularly preferably designed as a spiral spring.
- the first spring element is arranged between a holding element and the piston, wherein the preload of the first spring element can be adjusted by means of the holding element.
- the first spring element is supported on the one hand on a shoulder of the piston and on the other hand on the holding element.
- the shoulder of the piston is preferably the conical shoulder of the piston which comes into contact with the shoulder of the valve bushing.
- the holding element is arranged, for example, screwed into the valve bushing in the region of the inlet.
- the prestressing force of the first spring element can therefore be adjusted by screwing in and unscrewing the holding element.
- the opening behavior of the main valve is easy to change. Therefore, the attachment has a double function, so that the complexity of the proportional valve can be reduced.
- the electromagnetic proportional valve has a second spring element, which prestresses the actuating element in the direction of the armature.
- the second spring element is preferably arranged between the actuating element and the attachment. This means that the attachment is pressed onto the piston by means of the second spring element.
- the second spring element is preferably designed as a compression spring.
- the second spring element is particularly preferably designed as a spiral spring.
- the actuating element is preferably designed as an insert. If the actuating element is designed as an insert and is inserted into the armature, the second spring element can be arranged such that it is held by the armature and the actuating element.
- the electromagnetic proportional valve has a third spring element which prestresses the locking body in the direction of the actuating element.
- the third spring element is arranged between the piston and locking body.
- the third spring element thus presses the locking body into its valve seat (this is formed by the attachment).
- the third spring element is preferably designed as a compression spring.
- the third spring element is particularly preferably designed as a spiral spring.
- the through bore of the piston particularly preferably has a spring shoulder with which the spring comes into contact.
- the spring is also preferably located entirely within the piston.
- the piston has a conical shoulder at the first axial end region.
- the conical shoulder comes into contact with the shoulder of the valve bushing and acts as Shut-off device. Furthermore, this serves as a stop element for the first spring element.
- the piston has a combination of seat and slide function.
- the seat function is formed by means of the conical shoulder on the piston and the shoulder of the valve bushing. This acts as a shut-off device.
- the slide function is fulfilled by means of the circumferential sealing surface of the piston and the inner surface of the bore in the valve bushing, which interact as a proportional slide.
- the solution according to the invention consists in specifying a system, preferably in a vehicle, with one of the electromagnetic proportional valves described above, the system being an air conditioning system, a heat management system or a battery cooling system.
- FIG. 1 shows a detailed longitudinal section of a proportional valve according to the present invention.
- Fig. 3 is an enlarged longitudinal section of a pressure compensation valve device
- Proportional valve according to the present invention in a closed state
- Fig. 4 is an enlarged longitudinal section of a pressure compensation valve device
- FIG. 5 shows a longitudinal section of the proportional valve according to the present invention in an actuating position
- FIG. 6 shows a longitudinal section of the proportional valve according to the present invention in a (fully) open state
- Fig. 7 is an enlarged longitudinal section of a main valve device of the
- Proportional valve according to the present invention in a closed state
- Fig. 8 is an enlarged longitudinal section of a main valve device of the
- Proportional valve according to the present invention in a (fully) open state.
- the proportional valve 1 is also referred to as an expansion valve.
- the inlet 11 and the outlet 12 are arranged in a valve bushing 8 of the proportional valve 1.
- the inlet 1 1 is arranged axially at one longitudinal end of the valve bushing 8.
- the outlet 12 is arranged radially on the valve bushing 8.
- the proportional valve 1 has an electromagnet 2 and an armature 3.
- the armature 3 is axially movable by means of the electromagnet 2.
- the armature 3 is movable in the direction of the inlet 11.
- An actuating element 22 is arranged on the armature 3.
- the actuating element 22 is arranged in particular on an axial end region of the armature 3.
- the actuating element 22 moves together with the armature 3.
- the actuating element 22 is also referred to as an insert since it can be inserted into the armature 3.
- an (axial) bore is also arranged in the valve bushing 8.
- a piston 14 is arranged in the bore.
- the piston 14 is axially movable in the bore of the valve bushing 8.
- the piston 14 has a first axial end region 32 (on the right in FIG. 2) and a second axial end region 34 (on the left in FIG. 2).
- the first axial end region 32 is arranged towards the inlet 11.
- the second axial end region 34 is arranged towards the actuating element 22.
- a first opening 33 is arranged on the first axial end region 32 and a second opening 35 is arranged on the second axial end region 34.
- the openings 33 and 35 are connected to one another via a through hole 28.
- the piston 14 is designed as a hollow piston.
- the piston 14 connects a first space, which adjoins the first axial end region 32, and a second space, which adjoins the second axial end region 34. Therefore, a fluid (e.g., refrigerant) can flow from the first space through the piston 14 to the second space.
- the first space is the inlet 11.
- the inlet 11 is somewhat widened adjacent to the first axial end region 32.
- the second space is a pressure compensation space 29.
- the pressure compensation space 29 is a space between the armature 3 and the valve bushing 8 and is also referred to as a magnet space.
- An attachment 23 is arranged on the second axial end region 34.
- the attachment 23 holds a blocking body 24 in the second opening 35.
- the second opening 35 can be closed in such a way that no fluid can flow through the piston 14. This means that no fluid can flow from the inlet 11 to the pressure compensation chamber 29.
- the actuating element 22, the attachment 23 and the blocking body 24 thus form a pressure compensation valve device 21.
- the pressure compensation valve device 21 is also referred to as a second valve device.
- the blocking body 24 is designed as a ball. Therefore, the locking body 24 is also referred to as a ball.
- the main valve device 13 is also referred to as the first valve device and forms the main seat of the proportional valve 1.
- the main valve device 13 has two valve functions: valve main seat and proportional slide.
- the valve main seat is formed by a conical shoulder 17 on the first axial end region 32 of the piston 14 and a shoulder 19 of the valve bush 8 and acts as a shut-off device.
- a circumferential sealing surface 18 of the piston 14 acts as a proportional slide, which adjoins the conical shoulder 17 in the axial direction and interacts with an inner surface 20 of the bore in the valve bushing 8.
- the main valve device 13 When the main valve device 13 is open, a fluid can flow from the inlet 11 to the outlet 12. On the other hand, if the main valve device 13 is closed, no fluid can flow from the inlet 11 to the outlet 12.
- the main valve device 13 can only be opened when there is pressure equalization between the inlet 11 and the pressure equalization chamber 29. The pressure compensation can only take place when the pressure compensation valve device 21 is open.
- three spring elements 15, 25, 26 are arranged which support and enable the functions of the proportional valve 1.
- the spring elements 15, 25, 26 are designed as compression springs and are therefore also referred to as compression springs.
- the first spring element 15 is designed to press the piston 14 into the bore of the valve bushing 8.
- the spring element 15 is designed to press the conical shoulder 17 against the shoulder 19 of the valve bushing 8.
- the spring element 15 thus serves to keep the main valve device 13 in its closed state.
- the first spring element 15 is formed between the piston 14, in particular the conical shoulder 17 thereof, and a holding element 16. This means that the first spring element 15 is supported on the one hand on the conical shoulder 17 of the piston 14 and on the other hand on the holding element 16.
- the holding element 16 is screwed into the valve bushing 8 in a region of the inlet 11.
- the inflow 11 of the fluid takes place through a recess in the holding element 16 (and the first spring element 15).
- the spring force by means of which the piston 14 is prestressed, can be adjusted by means of the holding element 16. This is particularly easy if the holding element 16 can be screwed into the valve bushing 8.
- the second spring element 25 is arranged between the actuating element 22 and the attachment 23.
- the second spring element 25 serves to bias the attachment 23 in the direction of the piston 14.
- the second spring element 25 serves to bias the actuating element 22 in a direction away from the locking body 24.
- the second spring element 25 thus holds the actuating element 22 in a position in which the locking body 24 is not actuated. If the actuating element 22, as can be seen in FIG. 2, is designed as an insert, the second spring element 25 is held by the armature 3 and the actuating element 22. In particular, the second spring element 25 is guided in regions between an outer circumference of the actuating element 22 and an inner circumference of the armature 3.
- the third spring element 26 is arranged between the locking body 24 and a spring shoulder 36 (see FIG. 3 or 4) in the through bore 28 in the piston 14.
- the third spring element 26 serves to bias the blocking body 24 against a valve seat or sealing seat on the attachment 23. This means that the third spring element 26 keeps the pressure compensation valve device 21 closed. Likewise, the pressure compensation valve device 21 is kept closed by the high pressure, which acts on the blocking body 24 through the through bore 28 of the piston 14 in addition to the pretensioning force of the third spring element 26.
- the state of the proportional valve 1 shown in FIG. 2 is the (completely) closed state of the expansion valve 1.
- the closed pressure compensation valve device 21 is shown in more detail in FIG. 3.
- the locking body 24 is pressed against the sealing seat in the attachment 23.
- a distance is formed between the locking body 24 and the actuating element 22. This means that the actuating element 22 is not in contact with the locking body 24. Since the blocking body 24 closes the second opening 35, no fluid can flow between the high-pressure region of the inlet 11 and the low-pressure region of the pressure compensation chamber 29.
- the closed main valve device 13 is shown in more detail in FIG. 7.
- the conical shoulder 17 on the piston 14 and the shoulder 19 of the valve bushing 8 shut off the main valve device 13.
- the piston 14 is pressed by the first spring element 15 against the shoulder 19.
- the circumferential sealing surface 18 of the piston 14 is in contact with the inner surface 20 of the bore of the valve bushing 8. No fluid can flow between the inlet 11 and the outlet 12. In particular, no fluid can flow past between the piston 14 and the valve bushing 8, since there is no sufficient space between the two components.
- the armature 3 is shown in FIG. 2 in a rest position.
- the rest position is the position on the left in FIG. 2. More generally formulated, the armature 3 is arranged in the rest position in a position which is furthest away from the valve bushing 8 (or also the holding element 16 or also the inlet 11).
- FIG. 5 shows the proportional valve 1 in an actuation position.
- the pressure compensation valve device 21 is open and the main valve device 13 is closed.
- the third spring element 26 is further compressed, the second spring element 25 is slightly compressed and the first spring element 15 is preloaded.
- the armature 3 is shown in FIG. 5 in an actuation position.
- the actuation position is one position further to the right than the rest position. This means that the armature 3 has been moved axially from the rest position to the right into the actuating position. In particular, the armature 3 has been moved axially in the direction of the piston (or also the valve bushing 8, the holding element 16 or the inlet 11).
- the actuating element 22 moves together with the armature 3. The movement of the armature 3 into the actuating position also moves the actuating element 22 into the actuating position.
- the actuating element 22 comes into contact with the locking body 24 in the actuated position.
- an axial projection 30 of the actuating element 22 comes into contact with the locking body 24 in such a way that the locking body 24 is pressed in the direction of the prestressing second spring element 26. This means that the blocking body 24 is moved axially in the direction of the inlet 11.
- the locking body 24 is moved out of the sealing seat of the attachment 23.
- the first opening 33 which was previously closed, is opened in such a way that a fluid can flow between the high pressure region of the inlet 11 and the low pressure region of the pressure compensation chamber 29.
- fluid can then flow around the blocking body 24. A pressure equalization between inlet 11 and pressure equalization space 29 can therefore take place.
- the armature 3 moves in the direction of the valve bushing 8.
- the actuating element 22 moves with the armature 3, the second spring element 25 being compressed.
- the actuating element 22 opens the pressure compensation valve device 21 with the projection 30 which dips into the attachment 23, since the blocking body 24 counteracts the spring force of the third spring element 26 from its Sealing seat is lifted off.
- the high-pressure fluid (refrigerant) can flow through the through bore 28 of the piston 14 in the direction of the pressure equalization chamber 29 and pressure equalization takes place.
- the pressure load on the main valve device 13 is reduced.
- the main valve device 13 is still closed and therefore corresponds to the state shown in FIG. 7.
- the conical shoulder 17 on the piston 14 is still pressed against the shoulder 19 by the first spring element 15.
- the two elements block the proportional valve 1.
- the circumferential sealing surface 18 of the piston 14 is in contact with the inner surface 20 of the bore in the valve bushing 8.
- Fig. 6 shows the proportional valve 1 in a working position.
- both the pressure compensation valve device 21 and the main valve device 13 are open.
- the third spring element 26 is still still maximally compressed
- the second spring element 25 is still somewhat compressed
- the first spring element 15 is likewise maximally compressed.
- the maximum opening state of the main valve device 13 is therefore shown in FIG. 6.
- the armature 3 is shown in FIG. 6 in a working position. There are a variety of work positions. The working positions are generally located further to the right than the operating position. This means that the armature 3 has been moved from the actuating position to the right (in the direction of the inlet 11) into the working position. Since it is a proportional valve 1, not only is one working position formed, but a continuous transition from different working positions is possible. So it can not only be switched discretely, but in several working positions with different volume flow of the fluid.
- the armature 3 has been moved axially further in the direction of the valve bushing 8 (or also the holding element 16 or the inlet 11).
- the actuating element 22 is in direct contact with the attachment 23 in the working position or the working positions.
- a step 31 of the actuating element 22 comes into contact with the attachment 23 such that the Attachment 23 can be moved axially together with the actuating element 22 (and the armature 3). Since the attachment 23 is in direct contact with the piston 14, this can also be moved directly. This means that when the armature 3 moves, the piston 14 also moves accordingly.
- the working positions represent a further displacement of the armature 3 in the direction of the valve bushing 8.
- the first spring element 15 is compressed, so that the conical shoulder 17 of the piston 14 can be lifted off the shoulder 19 of the valve bushing 8.
- the seat function of the main valve device 13 changes into a slide function. If the armature 3 is moved further, the main valve device 13 opens completely. This state of the fully opened main valve device 13 is shown in FIG. 8.
- the piston 14 is displaced axially in the direction of the inlet 11 so far that there is no longer any overlap between the circumferential sealing surface 18 of the piston 14 and the inner surface 20 of the bore of the valve bushing 8. Thus, the fluid can flow from the inlet 11 to the outlet 12.
- the invention relates to an expansion valve for refrigerants and an air conditioning system, a heat management system or a battery cooling system with an expansion valve.
- Expansion valves are used in a battery cooling, air conditioning or heat pump system to generate a defined and controllable pressure drop between the condenser (heat emission) and evaporator (cooling).
- the pressure drop generated by the expansion valve creates an associated temperature change in the refrigerant.
- the valve is part of a regulator that controls the overheating of the refrigerant before it enters the compressor.
- the object of the invention is to provide an expansion valve which is optimized in terms of function. At the same time, an expansion valve is to be specified, which is simple and inexpensive to manufacture.
- Fig. 1 shows an expansion valve 1 for refrigerant according to an embodiment in longitudinal section.
- the expansion valve 1 has an electromagnet 2 with a coil 4 and an armature 3, which is arranged axially displaceably in a pole hat 5.
- the pole hat 5 is provided in one piece and has a pole tube 6 and a pole core 7, a thin connecting web being provided between the pole tube 6 and the pole core 7.
- valve bushing 8 An end section of a valve bushing 8 is sealed by means of a sealing element 9 and is pressed into the pole core 7.
- a circumferential collar 10 of the valve bushing 8 abuts the pole core 7 on the end face, so that the valve bushing 8 is positioned with respect to the electromagnet 2.
- a piston 14 is arranged axially displaceably in the valve bushing 8, which has an axially formed inlet 11 and at least one radial outlet 12.
- the inlet 11 forms a high-pressure connection P
- the radial outlets 12 form a low-pressure connection LP.
- the expansion valve 1 has, in the connection between the inlet 11 and the outlet 12, a first valve device 13, which is a combination of the main valve seat and
- the first valve device 13 can be opened or closed by means of the electromagnet 2.
- the piston 14 is arranged axially displaceably in a bore in the valve bushing 8 and is spring-biased in the direction of the electromagnet 2 by means of a first compression spring 15.
- the compression spring 15 is supported on the one hand on a shoulder of the piston 14 and on the other hand on a holding element 16, which is screwed into the valve bushing 8, for example in the area of the inlet 11.
- the inlet of the refrigerant takes place through a recess in the holding element 16 and the first compression spring 15.
- the spring force, by means of which the piston 14 is preloaded, can be set by means of the holding element 16.
- the first valve device 13 forms the main seat of the expansion valve 1 and has two valve functions: valve main seat and proportional slide.
- the main valve seat is formed by a conical shoulder 17 on the piston 14 and a shoulder 19 of the valve bushing 8 and acts as a shut-off device.
- a circumferential sealing surface 18 of the piston 14 acts as a proportional slide, which adjoins the shoulder 17 in the axial direction and interacts with an inner surface 20 of the bore in the valve bushing 8.
- the conical shoulder 17 of the piston 14 is arranged opposite the shoulder on which the compression spring 15 is supported.
- a second valve device 21 is provided for pressure equalization of the first valve device 13. This comprises an insert 22 fastened in the armature 3, an attachment 23 fastened on one end of the piston 14 and a ball 24 as a closing element.
- a second compression spring 25 is provided between the insert 22 and the attachment 23, which prestresses the attachment 23 in the direction of the piston 14. The ball 24 is further applied by means of a third compression spring 26 against its sealing seat on the attachment 23.
- Sealing elements 27 on the outer circumference of the valve bushing 8 enable a seal against a housing, not shown, etc., in which the expansion valve 1 is arranged.
- valve devices 13 and 21 are closed.
- the valve device 13 is kept closed by the high pressure applied to the inlet 11 and the compression spring 15.
- the second valve device 21 is kept closed by the high pressure, which acts on the ball 24 in addition to the biasing force of the compression spring 26 through a through bore 28 of the piston 14.
- Low pressure prevails in a magnet space 29 between armature 3 and valve bushing 8.
- the armature 3 moves in the direction of the valve bushing 8.
- the insert 22 moves with the armature 3, the second compression spring 25 being compressed.
- the insert 22 opens with one that dips into the attachment 23 Projection 30 the second valve device 21, since the ball 24 can open against the spring force of the third compression spring 26 and is lifted from its sealing seat.
- high-pressure refrigerant can flow through the through bore 28 of the piston 14 in the direction of the magnet chamber 29 and pressure equalization takes place, as a result of which the pressure load on the first valve device 13 can be reduced.
- the first compression spring 15 When the armature 3 is displaced further in the direction of the valve bushing 8, the first compression spring 15 is compressed, so that the conical shoulder 17 of the piston 14 can be lifted off the shoulder 19 of the valve bushing 8.
- the seat function of the first valve unit 13 changes into a slide function.
- the overlap between the circumferential sealing surface 18 of the piston 14 and the inner surface 20 is a predetermined value.
- the invention relates to an expansion valve for refrigerants with an electromagnet with a coil and an axially displaceably arranged armature, a piston arranged axially displaceably in a valve bushing, the valve bushing having an inlet and at least one outlet and a first valve device being provided in the connection between inlet and outlet which has a combination of shut-off function and proportional slide and is designed to be openable or closable by means of the electromagnet, and a second valve device for pressure equalization of the first valve device.
- the first valve device has a combination of seat and slide function.
- the second valve device is designed as a seat valve, for example as a ball seat valve.
- the invention relates to an air conditioning system, in particular an air conditioning system for a vehicle, with an expansion valve according to the preceding embodiments.
- the invention relates to a thermal management system, in particular thermal management system for a vehicle, with an expansion valve according to the previous embodiments.
- the invention relates to a battery cooling system, in particular a battery cooling system for a vehicle, with an expansion valve according to the previous embodiments.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Manufacturing & Machinery (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Electrochemistry (AREA)
- General Chemical & Material Sciences (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102018132448.0A DE102018132448A1 (de) | 2018-12-17 | 2018-12-17 | Expansionsventil für Kältemittel und Klimaanlage, Wärmemanagementsystem und Batteriekühlsystem mit einem Expansionsventil |
PCT/EP2019/085661 WO2020127274A1 (de) | 2018-12-17 | 2019-12-17 | Elektromagnetisches proportionalventil und system mit einem proportionalventil |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3899382A1 true EP3899382A1 (de) | 2021-10-27 |
Family
ID=69143525
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19832620.9A Pending EP3899382A1 (de) | 2018-12-17 | 2019-12-17 | Elektromagnetisches proportionalventil und system mit einem proportionalventil |
Country Status (5)
Country | Link |
---|---|
US (1) | US20220082310A1 (de) |
EP (1) | EP3899382A1 (de) |
CN (1) | CN113195986B (de) |
DE (1) | DE102018132448A1 (de) |
WO (1) | WO2020127274A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2022243409A1 (de) * | 2021-05-19 | 2022-11-24 | Hoerbiger Wien Gmbh | Absperrventil für einen kolbenkompressor |
DE102022120325A1 (de) | 2022-08-11 | 2024-02-22 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Bidirektionale Ventilvorrichtung für ein Pneumatik- und/oder ein Hydrauliksystem und Verfahren zum Betreiben einer bidirektionalen Ventilvorrichtung |
DE102022210913A1 (de) | 2022-10-17 | 2024-04-18 | Continental Automotive Technologies GmbH | Elektromagnetventil für eine Kraftfahrzeugbremsanlage |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19530899C2 (de) * | 1995-08-23 | 2003-08-21 | Bosch Gmbh Robert | Magnetventil, insbesondere für eine schlupfgeregelte, hydraulische Bremsanlage für Kraftfahrzeuge |
LU88659A1 (de) * | 1995-09-18 | 1996-02-01 | Luxembourg Patent Co | Elektromagnetisch betaetigbares Ventil |
JP2002509839A (ja) * | 1998-03-31 | 2002-04-02 | コンチネンタル・テベス・アーゲー・ウント・コンパニー・オーハーゲー | 電磁バルブ |
GB9819965D0 (en) * | 1998-09-15 | 1998-11-04 | Expro North Sea Ltd | Improved ball valve |
DE10323595A1 (de) * | 2003-05-16 | 2004-12-09 | Hydac Fluidtechnik Gmbh | Ventil |
US7341236B2 (en) * | 2006-03-07 | 2008-03-11 | Husco International, Inc. | Pilot operated valve with a pressure balanced poppet |
CN101795910A (zh) * | 2007-09-04 | 2010-08-04 | 丰田自动车株式会社 | 常闭电磁阀、制动控制***、用于常闭电磁阀的控制方法和电磁阀 |
US7984890B2 (en) * | 2008-02-26 | 2011-07-26 | Incova Technologies, Inc. | Pilot operated valve with fast closing poppet |
US7854390B2 (en) * | 2008-05-29 | 2010-12-21 | Kabushiki Kaisha Saginomiya Seisakusho | Expansion valve, heat pump type refrigeration cycle apparatus, and air handling unit |
DE102009019552A1 (de) * | 2009-04-30 | 2010-11-11 | Hydac Fluidtechnik Gmbh | Proportional-Drosselventil |
DE102010005228A1 (de) * | 2010-01-21 | 2011-07-28 | Hydac Fluidtechnik GmbH, 66280 | Ventilvorrichtung |
DE102011076556A1 (de) * | 2011-05-26 | 2012-11-29 | Continental Teves Ag & Co. Ohg | Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeugbremsanlagen |
CN103512288B (zh) * | 2012-06-20 | 2016-07-06 | 浙江三花股份有限公司 | 一种电子膨胀阀 |
DE102013224820A1 (de) * | 2013-12-04 | 2015-06-11 | Robert Bosch Gmbh | Ventil für ein hydraulisches Hybridsystem |
DE102014119592B4 (de) * | 2014-02-05 | 2023-11-09 | Svm Schultz Verwaltungs-Gmbh & Co. Kg | Ventil |
DE102014004796A1 (de) * | 2014-04-02 | 2015-10-08 | Hydac Fluidtechnik Gmbh | Proportional-Druckregelventil |
US11906217B2 (en) * | 2018-10-27 | 2024-02-20 | Zhejiang Sanhua Intelligent Controls Co., Ltd. | Electronic expansion valve |
-
2018
- 2018-12-17 DE DE102018132448.0A patent/DE102018132448A1/de not_active Withdrawn
-
2019
- 2019-12-17 EP EP19832620.9A patent/EP3899382A1/de active Pending
- 2019-12-17 CN CN201980083759.1A patent/CN113195986B/zh active Active
- 2019-12-17 US US17/414,794 patent/US20220082310A1/en active Pending
- 2019-12-17 WO PCT/EP2019/085661 patent/WO2020127274A1/de unknown
Also Published As
Publication number | Publication date |
---|---|
CN113195986B (zh) | 2023-06-06 |
US20220082310A1 (en) | 2022-03-17 |
CN113195986A (zh) | 2021-07-30 |
WO2020127274A1 (de) | 2020-06-25 |
DE102018132448A1 (de) | 2020-06-18 |
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