DE102022125928A1 - Method for positioning a closure element of a valve or ejector, and valve or ejector - Google Patents

Abstract

In a method for positioning a closure element of a valve or ejector that can be moved between a first end position and a second end position by means of a drive, the closure element is moved into one of the first end position and the second end position and after moving the closure element into the one end position, a compensation cycle occurs carried out, during which the closure element is controlled to carry out a first compensation movement in the direction of the other end position and to carry out a second compensation movement in the direction of one end position.

Description

The invention relates to a method for positioning a closure element of a valve or ejector that can be moved by means of a drive between a first end position and a second end position, wherein the closure element blocks a flow opening of the valve or ejector in the first end position against a flow of fluid or gas and the flow opening in the second end position for a flow of fluid or gas.

The invention further relates to a valve or an ejector.

For example, a valve may be provided to regulate a fluid or gas flow. For this purpose, the valve can have at least one inlet and at least one outlet, wherein gas or fluid can flow into the valve through a flow opening of the inlet and flow out through a flow opening of the outlet when both flow openings are open. In order to be able to restrict or interrupt the flow, such a valve can have a closure element, wherein at least one flow opening, for example the flow opening of the inlet, can be closed by moving the closure element into a first end position, which can also be referred to as the closed position to limit or prevent the flow of gas or fluid through the valve.

An ejector can be provided to guide and accelerate a propellant medium flowing in through a propellant connection through a propulsion nozzle in order to be able to suck in a suction medium through a suction connection using the negative pressure generated in this way and to be able to lead it out of the ejector together with the propellant medium through an outlet of the ejector . Even with such an ejector, a closure element can be provided, for example, to selectively limit or close the flow opening for the inflowing propellant medium, whereby blocking the entry of the propellant medium into the ejector also prevents the suction effect and thus prevents liquid or gas from escaping the output of the ejector can be stopped.

In order to achieve precise regulation of a fluid or gas flow through a valve or an ejector, it is therefore necessary that the closure element, on the one hand, reliably closes the flow opening after moving into the first end position or closed position and prevents unwanted leakage, on the other hand, optionally and can be reliably moved between the end positions to enable either flow through the valve or the ejector.

However, since a flow of gas or fluid through the valve or the ejector is prevented after moving the closure element into the first end position, for example by cooling the valve or ejector due to a lack of flow of a warm medium or by heating the valve or Ejector due to a lack of flow of a cold medium - thermal stresses occur, which are reflected in deformations of the valve or ejector and in particular a housing of the valve or ejector and can thereby influence a closing force exerted by the closure element. In particular, different thermal expansion coefficients of the components installed in the valve or ejector can lead to such stresses, and pressure differences that occur, for example, after the flow opening has been closed can also affect the closing force.

In this respect, a closing force set by moving the closure element into the first end position can possibly change unintentionally without the closure element being controlled to move, which can make precise regulation of the flow and/or the operability of the valve or ejector more difficult. For example, shortening of a valve or ejector due to thermal stresses can lead to an increased force acting on the closure element and jamming the closure element so that it can no longer be moved into the second end position. Conversely, for example, expansion of the valve or ejector can occur due to changing thermal conditions, which can reduce the closing force exerted by the closure element and possibly lead to an unwanted leak. In addition, tensions can also occur in the second end position or an open position of the closure element, which lead to the closure part jamming, so that it can no longer be moved into the first end position or closed position in order to close the flow opening.

It is therefore an object of the invention to provide a method for positioning a closure element of a valve or ejector and/or a valve or an ejector through which or in which a flow opening of the valve or ejector can be reliably closed or opened, in particular over longer periods of time, as well as a subsequent reliable one Moving the closure element into an opposite end position can be achieved.

This task is solved by a method with the features of claim 1.

In this method, the closure element is moved into one of the end positions (first end position or second end position) and after moving the first closure element into one end position, a compensation cycle is carried out, the closure element being used during the compensation cycle to carry out a first compensation movement in the direction of the other End position and to carry out a second compensation movement in the direction of one end position is controlled.

For example, the closure element can first be moved into the first end position, which can also be referred to as the closed position, in order to close the flow opening. The first end position can in this respect represent the end position of the movement of the closure element in the direction of the flow opening, which can be defined in that the closure element closes the flow opening with a force that can be transferred from the drive to the closure element and / or the force that can be transferred from the drive to a Sealing the flow opening. The closure element can therefore be moved to move into the first end position up to a stop, at which, for example, a motor shaft of an electric motor of the drive blocks and/or an electric stepper motor of the drive causes one or more step losses when a further movement towards the flow opening is activated suffers. Conversely, the second end position, which can also be referred to as the open position, can correspond, for example, to an end position of the movement of the closure element opposite the first end position, in which the flow opening is released for a maximum flow taking into account the design and dimension of the valve or ejector.

Furthermore, the closure element can be movable into various intermediate positions, which lie between the first end position and the second end position and enable a flow of gas or fluid through the flow opening, the flow being increased by moving the closure element closer to the second end position or open position Intermediate positions can be increased and reduced by moving into intermediate positions closer to the first end position or closed position. The intermediate positions thus make it possible to regulate the strength of the flow between a maximum flow achieved in the second end position and a blocking of the flow in the first end position.

While the flow of gas or fluid can be reliably blocked in the first end position, in some valves or ejectors the flow can also be blocked by moving the closure element into a blocking position, in which the closure element already closes the flow opening with sufficient force to prevent a flow, but without having already reached the first end position, which depends on the force that can be transmitted by the drive. In this respect, a flow through the flow opening can basically be blocked by positioning the closure element in a blocking section, which is limited by the first end position and the blocking position, which can be slightly offset from the first end position in the direction of the second end position.

In order to ensure that the closure element is reliably positioned in the end positions, but on the other hand can also be released from the respective end position if necessary, the method described here provides that the closure element is not stationary in the end position after moving into a respective end position remains, but a compensation cycle is carried out. During this compensation cycle, the closure element is controlled to carry out a first compensation movement in the direction of the respective other end position and to carry out a second compensation movement in the direction of the one end position, which can be done in particular by appropriately controlling the drive. In particular, the closure element can carry out the first compensation movement and the second compensation movement during the compensation cycle and can be moved in the direction of the other end position and in the direction of the one end position. The compensation cycle can also be carried out during a period of time during which the closure element is not controlled for movement into the other end position or one of the intermediate positions mentioned above, but rather the flow opening should fundamentally remain in one end position - the closed position or the open position .

By not leaving the closure element motionless in one end position, thermal stresses that have built up after reaching one end position can be compensated for. For example, a thermal voltage that leads to an increased closing force after moving the closure element into the first end position or closed position, can be compensated for by moving the closure element in the direction of the second end position or open position. In particular, this movement can reduce the force exerted by the closure element on the flow opening or a seal of the flow opening, so that components of the valve or ejector, in particular a housing of the valve or ejector, follow the movement of the closure element in the direction of the second end position to a certain extent and can be shortened in order to reduce the thermal stresses. By moving the closure element again in the direction of the first end position, it can be ensured that the flow opening is again closed reliably and, for example, with a predetermined closing force. However, an absolute position of the first end position may have shifted due to the shortening of the valve or ejector, so that the controlled movement in the direction of the first end position may not be completely carried out, but the (shifted) first end position may already be reached beforehand.

In addition, the procedure explained can also be used to compensate for thermally induced reductions in the closing force exerted by the closure element if the lack of mass flow due to the closure element being in the first end position leads to an expansion of the valve or ejector. This can be the case in particular if the lack of flow of a cold medium leads to the valve or ejector heating up.

As a result of such an expansion, the flow opening can possibly move slightly away from the closure element, so that the closing force exerted by the closure element is reduced without the closure element being activated for movement out of the first end position or closed position. However, such thermal changes can be compensated for by moving the closure element in the direction of the first end position during the compensation cycle, in that the closure element can, as it were, track the expansion of the valve or ejector. This makes it possible in particular to prevent unwanted leakage.

In order to ensure that both thermally caused shortenings and thermally caused expansions of the valve or ejector can be compensated for, it can be provided in particular that the closure element is controlled to move a greater distance in the direction of the first end position than in the direction of the second end position, so that the closure element can ultimately follow any expansion of the valve or ejector in the course of the compensation cycle and compensate for this expansion. If, on the other hand, the valve or the ejector has experienced a shortening, this shortening can be compensated for by moving in the direction of the second end position, whereupon at least part of the controlled distance in the direction of the first end position or part of the second compensation movement is not carried out and the due to the Shortening postponed first end position can be reached beforehand. For example, a stepper motor of the drive can therefore suffer one or more step losses as a result of the controlled second compensation movement. In this case too, however, a closing force occurs, which is determined and therefore defined by the force that can be transmitted to the closure element by the drive during movement in the direction of the first end position. This will be explained in more detail below.

While compensation for thermal stresses and prevention of leakage due to expansion of the valve or ejector were explained above in particular after moving the closure element into the first end position or the closed position, the compensation cycle can also be carried out after the second end position or the Open position should be provided. In particular, even after reaching the second end position, tensions can build up, which can possibly result in the closure element jamming. However, such tensions can be released by carrying out the compensation cycle and in particular the movement in the direction of the first end position or in the direction of the closed position in order to be able to position the closure element again in the second end position by a subsequent movement in the direction of the second end position. If a larger movement towards the second end position than away from the second end position is controlled during the compensation cycle, any incorrect positioning of the closure element can also be compensated for if the closure element was not originally positioned completely in the second end position or open position, for example due to step losses . The compensation cycle can therefore also serve to compensate for any original incorrect positioning after moving into one end position and to move the closure element further in the direction of the respective desired first or second end position.

Furthermore, it can be provided that the compensation cycle is repeated cyclically, provided that the closure element is not moved out of one end position, for example after a first to be able to compensate for thermal stresses built up during the th compensation cycle.

In principle, it can be provided to move the closure element into one end position by the second compensation movement, so that the closure element can be controlled to carry out a compensation movement into one end position. However, it is possible that before the compensation cycle is carried out, an expansion occurs that cannot be completely compensated for by the controlled second compensation movement in the direction of one end position, for example a movement by a predetermined distance, so that one end position is not completely reached . However, such expansions can also be completely compensated for in particular by repeating the compensation cycle cyclically.

In addition, the drive can in particular be controlled to move the closure element only slightly in the direction of the other end position, in particular only slightly in the direction of the second end position, after the closure element has been moved into the first end position or closed position. The closure element can therefore, after moving into the first end position by the first compensation movement in the direction of the second end position, in particular not be moved to the second end position and/or not to one of the above-mentioned intermediate positions, but, for example, only so far in the direction of the second end position that the flow opening is still blocked and no leakage occurs. In this respect, the closure element - after moving into the first end position - can only be moved between the first end position and the above-mentioned blocking position and/or in a blocking section of the valve or ejector by moving in the direction of the second end position. Even after moving the closure element into the second end position, the closure element can only be moved slightly towards the first end position during the compensation cycle, so that the compensation cycle is not accompanied by an unwanted or relevant prevention of the flow through the flow opening. On the other hand, the closure element can basically be moved to one end position by moving in the direction of one end position.

A valve can have at least one inlet with a flow opening and an outlet with a flow opening, it being possible to regulate an input flow entering through the inlet and an output current exiting through the outlet by means of the closure element. For example, the closure element can be provided to selectively block the flow opening of the inlet or to release it for a flow, which then leaves the valve as an output flow through the outlet and its flow opening. However, it is also possible to either close or open a flow opening of an outlet of a valve using a closure element.

An ejector can have a driving connection with a flow opening through which a driving medium enters and is guided through a driving nozzle. Due to the negative pressure generated thereby, a suction medium can be sucked in through a suction connection, for which purpose an ejector can have a further flow opening. A mixture of the propellant medium and the suction medium sucked in can be passed through an outlet of the ejector with a further flow opening, so that the ejector can in particular have at least three flow openings. For example, it can be provided that the flow opening assigned to the drive connection can be selectively closed by means of a closure element in order to be able to prevent both the flow of propellant medium through the ejector and the suction effect. An ejector can basically be referred to as a jet pump.

Further embodiments of the invention can be found in the dependent claims, the description and the drawings.

In some embodiments it can be provided that the compensation cycle is carried out after a predetermined or predefinable waiting time after reaching one end position. In this respect, in some embodiments, the closure element can remain stationary for a predetermined or predeterminable waiting time after reaching one end position in order to be able to carry out the compensation cycle after the waiting time has elapsed and in particular to be able to release thermal tensions that have built up during the waiting time.

However, in some embodiments it is also possible for at least a first compensation cycle to be carried out immediately after one end position has been reached. After the first compensation cycle, the closure element can, for example, remain stationary for the waiting time mentioned in order to carry out another compensation cycle after the waiting time has elapsed.

In addition, in some embodiments, the compensation cycle can be repeated cyclically, wherein a cycle time of the cyclic repetition can correspond in particular to the waiting time mentioned, so that after the end of a respective compensation cycle, a further compensation cycle can be carried out, provided that the closure element is not activated for a movement out of one end position during the waiting time after the previous compensation cycle has ended.

However, in some embodiments it can be provided that at most a predetermined maximum number of compensation cycles is carried out and after the maximum number of compensation cycles has been reached, no further compensation cycle is carried out as long as the closure element does not move out of one end position and then again into one of the first End position and the second end position is moved. In addition, in some embodiments it can be provided that the closure element is permanently activated to carry out compensation movements after reaching one end position, as long as the closure element is not activated for a movement out of one end position or into the other end position or one of the intermediate positions mentioned , so that in some embodiments, another compensation cycle can be started immediately after a compensation cycle ends.

In some embodiments, the closure element can be translationally movable between the first end position and the second end position. For example, the closure element can be intended to be moved into a valve seat of a seat valve in order to close a flow opening formed on the valve seat. The compensation cycle can therefore be used to compensate for translational expansions and/or shortenings of the valve or ejector along a direction of movement of the closure element.

In order to be able to move the closure element translationally between the first end position and the second end position, the drive can, for example, comprise a spindle drive. Such a spindle drive can generally include a spindle with an external thread (e.g. threaded rod) and a spindle nut with an internal thread, which is in threaded engagement with the spindle. By means of a rotary drive of one element, the other element, which is mounted in a rotationally fixed but axially displaceable manner, is driven in the axial direction, whereby a high gear ratio to slow speed can be achieved. The closure element can be connected, for example, to a spindle (in particular held in a rotationally fixed manner) of such a spindle drive. Alternatively, the closure element can be connected to a (in particular non-rotatably held) spindle nut of such a spindle drive. The drive of the closure element can further comprise, in particular, a stepper motor, so that the drive can be controlled, for example, to carry out a respective number of steps of the stepper motor to move the closure element.

In some embodiments, the closure element can first be controlled to carry out the first compensation movement and then to carry out the second compensation movement; or the other way around. In this respect, during the compensation cycle, the closure element can first be controlled to move away from the one end position in which the closure element was positioned and then to move back towards the one end position, or the closure element can initially move towards the one end position and then controlled to remove one end position.

In principle, it can be provided to move the closure element towards one end position at the end of the compensation cycle, i.e. to first control the first compensation movement and then the second compensation movement. This sequence of compensation movements can ensure that the closure element can be positioned in one end position after the compensation cycle and/or can be positioned further in the direction of one end position by carrying out the compensation cycle than before the compensation cycle was activated.

Alternatively, however, the closure element can also be controlled first to carry out the second compensation movement and then to carry out the first compensation movement, so that the closure element can be positioned away from one end position towards the other end position at the end of the compensation cycle. This can be provided in particular if the first compensation movement directed away from one end position is so slight that the opening state of the flow opening ultimately does not change. If the closure element is initially positioned in the first end position or closed position and such a compensation cycle is then carried out, the closure element can initially be adjusted to any expansion of the valve by the second compensation movement in order to reduce any tensions through the subsequent first compensation movement. If the first compensation movement is so slight that the closure element is not led out of the locking section already mentioned, a leakage can occur after the compensation cycle has been carried out despite the flow from the first end positioning of the closure element away from the location can be prevented.

In some embodiments, the closure element can be controlled to carry out the first compensation movement by a first distance and to carry out the second compensation movement by a second distance, wherein the second distance can be greater than the first distance.

As already explained above, this procedure can in particular compensate for both thermally caused shortenings and thermally caused expansions of the valve or ejector, in that the closure element enables a shortening, in particular after moving into the first end position or closed position by the first compensation movement, due to which larger movement in the direction of the first end position in the course of the second compensation movement, however, any expansion can be tracked to a certain extent. The first compensation movement and the particularly subsequent second compensation movement can therefore compensate for expansions which are less than the difference between the second distance and the first distance or correspond to this difference. With a corresponding expansion of the valve or ejector before carrying out the compensation cycle, the closure element can be moved in particular by the first distance in the direction of the second end position and by the second distance in the direction of the first end position.

If an expansion of the valve or ejector, in particular a housing of the valve or ejector, which occurred before the compensation cycle is carried out, is less than the difference between the second path and the first path or the valve or the ejector experiences a shortening, it can be provided that the drive is activated to move the closure element by the second distance, but the closure element does not completely carry out this movement. In particular, the closure element can close the flow opening even before the second distance has been completely covered in the direction of the first end position with a closing force that can be transferred to the closure element by the drive and is therefore defined, so that the first end position is reached and the closure element no longer moves towards the flow opening can be moved. The movement of the closure element therefore stops in such a case by striking the passage opening, so that, for example, a stepper motor driving the closure element can lose steps. Likewise, in the case of a second compensation movement directed towards the second end position, the closure part can reach the second end position before the second distance has been covered, for example if the closure element was in the second end position before the first compensation movement was activated. If the valve or the ejector undergoes a shortening that at least corresponds to the first distance, the closure element can, due to this shortening, ultimately remain in one end position even despite the first compensation movement, so that the closure element can be used to move the drive when the drive is subsequently activated Closure element remains stationary in the direction of the first end position.

Furthermore, any incorrect positioning of the closure element can also be compensated for by such a ratio between the first and the second distance if the closure element was not originally moved to a mechanical end position. In particular, by carrying out the compensation cycle, the closure element can therefore be moved further in the direction of the second end position and/or the first end position if the respective end position was not originally reached, for example due to step losses of a stepper motor not being taken into account.

The explained control for moving the closure element by a first distance in the direction of the other end position and by a second distance in the direction of one end position thus enables both thermally induced shortenings and thermally induced expansions to be compensated. If the valve or the ejector also experiences an expansion that is greater than the difference between the first distance and the second distance, such expansions can also be completely compensated for by cyclically repeating the compensation cycle, in addition by successively tracking the closure element after moving In the first end position it can at least be prevented that the closure element moves away from the locking section mentioned and a leak occurs.

In some embodiments, the closure element can be stepwise movable and can be controlled to carry out the first compensation movement by a first number of steps and to carry out the second compensation movement by a second number of steps, the second number of steps being greater than the first number of steps can. In order to be able to carry out such control, the drive in particular includes a stepper motor.

In particular, the second number of steps can be at least one step larger than the first number of steps. In turn, the control of the drive for moving the closure element by a first number of steps towards the other end position and by a second number of steps in the direction of one end position makes it possible to control the drive for moving the closure element by different distances and both shortenings and expansions of the valve or ejector. In particular, all steps of the second number of steps can therefore be carried out if the valve or the ejector experiences an expansion before carrying out the compensation cycle or has not originally reached an end position, whereas step losses occur or steps cannot in any case not be completely carried out if this Valve or the ejector experiences a shortening or merely an expansion that is less than the distance of the closure element to be covered by one step. In contrast, in some embodiments, the first number of steps can always be carried out and/or the above-mentioned first distance can always be covered.

In some embodiments, the second number of steps may be exactly one step larger than the first number of steps. For example, it can be provided to control the drive for moving the closure element by two steps in the direction of the other end position and by three steps in the direction of one end position. In other embodiments, however, it can also be provided that the second number of steps is larger than the first number of steps by exactly two, exactly three, exactly four or exactly five steps. A larger difference between the second number of steps and the first number of steps can be provided in particular if, due to the application or design, relatively large expansions of the valve or ejector are to be expected or the compensation cycle is only carried out after a waiting time after one end position has been reached , so that relatively large expansions can occur. If waiting times are longer and/or greater reductions are expected, the number of steps towards the other end position can also be increased, for example to three steps, four steps or five steps.

In some embodiments, the closure element can be controlled to move by less than 50 μm, in particular by less than 20 μm, in the direction of the other end position in order to carry out the first compensation movement. For example, the closure element can be moved by approximately 15 μm towards the other end position. Through such a slight movement, it can be achieved, in particular after moving the closure element into the first end position or closed position, that the closure element exerts a closing force despite the movement towards the second end position or open position, which prevents fluid or gas from flowing through the flow opening, so that performing the compensation cycle does not result in leakage through the flow opening. Rather, the flow opening can remain reliably closed and the compensation movements only serve to compensate for and/or reduce thermal stresses and/or to correct any incorrect positioning.

In some embodiments in which the closure member is stepwise movable, the closure member may be moveable through a step of less than 20 μm. In particular, the closure element can be movable by a step of less than 15 μm and/or by less than 10 μm. Furthermore, in some embodiments, the closure element may be movable through a step of approximately 7 μm. In this respect, in such embodiments, the closure element can be moved precisely step by step by only such small distances that the closure element, in particular when moving from the first end position towards the second end position, does not have to be moved out of a blocking section of the valve or ejector, but rather the flow opening despite remains reliably closed during the movement of the closure element.

In some embodiments, the controlled first compensation movement can be compensated for by an elastic deformation of an elastically deformable compensation element, which is arranged in a force transmission path from a housing of the valve or the ejector to the closure element. In such embodiments, the compensation element can be elastically deformed, in particular due to a movement of the closure element into one end position and the force which is exerted on the closure element by a stop of a housing of the valve or ejector, for example a limitation of the flow opening, and is transmitted to the compensation element . If the closure element is then controlled during the compensation cycle for the first compensation movement in the direction of the other end position, the force exerted by the stop on the closure element and transmitted to the compensation movement is reduced, so that the compensation element can unfold against the previously experienced elastic deformation and can thereby compensate for the first compensation movement.

The force transmission path mentioned can generally result from the closure element being supported directly or indirectly on a housing of the valve or the ejector so that a closing force can be built up. For example, the closure element can be supported on the housing of the valve or the ejector via a part of a spindle drive and/or via a bearing (in particular a roller bearing). The compensation element can variably accommodate any play present in the force transmission path.

In such embodiments, a closing force exerted by the closure element can be reduced and thermal stresses can be reduced by the first compensation movement, but the closure element ultimately remains stationary in the previously controlled position. In such embodiments, the closure element can therefore in particular not cover a controlled first distance for carrying out the first compensation movement due to the compensation by the compensation element.

In particular, it can be provided that the closure element is biased by the compensation element in the direction of the first end position or the closed position. In such embodiments, if the closure element is controlled for the first compensation movement and thus a movement in the direction of the second end position after moving into the first end position during the compensation cycle, this movement can, as explained above, be achieved by unfolding the compensation element and reducing the amount of the compensation element Compensating element developed bias can be compensated, so that although a closing force exerted by the closure element can be reduced, a position of the closure element can remain unchanged. For example, the closure element can be supported on the housing via a compensation element designed as a preloaded spring, for example a plate spring, whereby the spring can expand as a result of the reduction in the closing force due to the controlled first compensation movement and can thereby compensate for the first compensation movement. By means of such a compensation element, a force exerted by the closure element after moving into the first end position can be reduced as a result of the activation of the first compensation movement, in order to be able to reduce any built-up tensions and prevent the closure element from jamming, but without the closure element being separated from the Flow opening is removed. In this respect, leakage in particular as a result of the first compensation movement can be reliably prevented.

In addition, such a compensation element - alternatively or in addition to the control-related compensation of thermal shortenings or expansions of the valve or ejector - can also achieve mechanical compensation for such expansions or shortenings, as will be explained in more detail below.

In some embodiments, the compensation cycle can be carried out after a predetermined or predeterminable waiting time after one end position has been reached. It can therefore be provided that the closure element remains stationary for a waiting time after reaching one end position before the compensation cycle is carried out after the waiting time has elapsed, in particular in order to be able to reduce thermal stresses built up during the waiting time. The waiting time can, for example, be stored in a control for driving the closure element and/or optionally adjustable by a user of the valve in such a control. In particular, the waiting time can be selected such that, on the one hand, jamming of the closure element and/or unwanted leakage can be prevented, but on the other hand, movements of the closure element and the associated loads on the components of the valve or ejector can be minimized. In this respect, the waiting time can depend on the design and/or application of the valve or ejector, in particular the expected thermal conditions, a temperature of the medium flowing through and/or the materials of the valve or ejector. In principle, however, the waiting time can also be calculated and thereby specified by a controller for driving the closure element.

The waiting time may be less than 120 seconds in some embodiments. In particular, the waiting time can be less than 60 seconds and/or less than 30 seconds. Furthermore, in some embodiments the waiting time can be approximately 10 seconds, in particular between 9 seconds and 11 seconds and/or exactly 10 seconds. In particular, the waiting time can be selected depending on the respective application and/or the respective design of the valve or the ejector, for example the materials used. In principle, for example, shorter waiting times can be provided if - for example when using very cold or very hot fluids or gases - relatively high thermal stresses occur can be expected in a short period of time. However, in some embodiments it can also be provided that the waiting time is less than 500 seconds or 500 seconds.

In some embodiments, a first compensation cycle can also be carried out immediately after one end position has been reached. In such embodiments, the closure element can therefore be activated immediately after reaching it to carry out the two compensation movements. After carrying out the first compensation cycle, the compensation cycle can, for example, be repeated cyclically with the predetermined or predeterminable waiting time as a cycle time, for example a waiting time of 10 seconds, provided that the closure element is not moved out of the respective end position. In addition, it can also be provided that the first compensation movement and the second compensation movement are carried out permanently in succession, as long as the closure element is not controlled for a movement out of one end position, so that another compensation cycle can immediately follow the first compensation cycle without this Closure element remains stationary for a waiting time between the compensation cycles.

In some embodiments, the closure element may be moved to the first end position and the compensation cycle may be performed after moving the closure element to the first end position. In particular, by carrying out the compensation cycle, jamming of the closure element in the first end position or closed position due to thermal stresses and/or leakage due to expansion of the valve or ejector can be prevented.

In some embodiments, the flow opening can be closed with a first closing force by moving the closure element into the first end position.

In particular, the first closing force can be predetermined or can be predetermined and can be defined, for example, by the force that can be transmitted from the drive to the closure element. This force can be determined, for example, by a motor current or a motor torque of a motor of the drive, whereby the motor current or the motor torque can optionally be adjustable. In this respect, the first closing force can correspond to the force transmitted to and/or adjusted to the closure element when the closure element is moved into the first end position. For example, the closure element can exert the first closing force on a seal of the flow opening.

The first end position can therefore fundamentally be defined by reaching the closing force, although the absolute position of the first end position can depend on the state of the valve or ejector. In particular, an absolute position of the first end position can shift due to expansions or contractions of the valve or ejector, since the closure element can be moved towards the flow opening from the second end position towards the flow opening, for example due to an expansion of the valve or ejector, starting from the second end position before this Closure element closes the flow opening with the force that can be transmitted by the drive.

In some embodiments, the first closing force can correspond to a force that can be transmitted to the closure element by the drive, in particular a force that can be transmitted and/or transmitted during the movement into the first end position.

In some embodiments, the flow opening can be closed by performing the second compensation movement with a second closing force, wherein the second closing force can be less than the first closing force.

The second closing force can also be specified or can be specified, for example, and in particular correspond to a force that can be transmitted and/or transmitted to the closure element by the drive during the second compensation movement. In this respect, it can be provided, for example, that a motor current of a motor of the drive is reduced when the closure element is moved in the direction of the first end position in the course of the compensation cycle compared to the previous movement of the closure element into the first end position. For example, the motor current applied while moving the closure element in the direction of the first end position can correspond to 80% of the motor current that is applied to move the closure element into the first end position. A second closing force defined in this way can be set in particular when the closure element reaches the first end position due to the controlled second compensation movement.

By reducing the closing force, in particular the load on the components due to carrying out the compensation cycle can be reduced in order to avoid a possible increase in load - especially when the compensation cycle is repeated cyclically with a short cycle time between successive compensations sation cycles - to be minimized compared to leaving the closure element in the first end position. In addition, by setting a reduced second closing force, the flow opening can be closed with a better defined force in that the closure element can be moved more gently onto a seal of the flow opening and force peaks or force losses as a result of the closure element striking with high force can be avoided.

In some embodiments, the drive can be controlled to drive the closure element during the second compensation movement with a lower force than when moving into one end position. In this respect, in some embodiments the drive can be controlled to move the closure element with a lower force in the direction of one end position than in the one end position. For example, a motor current of a motor of the drive for moving the closure element in the direction of one end position - i.e. during the second compensation movement - can be reduced compared to a setting for moving the closure element in the one end position - which can in particular define the first closing force mentioned. In such embodiments, if the closure element again reaches the first end position, for example due to the controlled second compensation movement, in which the closure element closes the flow opening with the force that can be transmitted by the drive during the movement in the direction of the first end position, the flow opening can be with a compared to that The first closing force can be closed with a reduced, but more clearly defined and less stressful force. In this respect, in some embodiments, the closure element can be moved during the second compensation movement with a reduced force compared to the first closing force.

The force that can be transmitted to the closure element by the drive can be adjustable in some embodiments, in particular by adjusting an electrical motor current of a motor of the drive.

In some embodiments, the force transmitted to the closure element by the drive when moving into one end position can be reduced before the one end position is expected to be reached.

In order to ensure, for example, that the first end position is reliably reached, when driving the closure element by means of a stepper motor, provision can be made to set a number of steps in which the closure element would move beyond the expected position of the first end position, so that step losses of the stepper motor after reaching the first end position. A similar procedure can also be provided for moving the closure element into the second end position or open position. When using a stepper motor, the motor current can therefore be reduced in such embodiments before the expected end position is reached, for example approximately ten steps before the expected end position is reached, in order to increase the force with which the closure element strikes when the respective end position is reached reduce and, for example, to achieve the gentlest possible impact of the closure element on a seal of the flow opening.

For example, the force transmitted by the drive to the closure element can be reduced to the force with which the closure element is moved towards the one end position during the compensation cycle before one end position is expected to be reached. In this respect, the transmitted force can be reduced to the above-mentioned second closing force, particularly when moving into the first end position. The force reduction can in particular be carried out by reducing a motor current of a motor of the drive, so that the motor current can be reduced to 80% of the original motor current, for example, before reaching the end position.

In contrast to moving the closure element into one end position, to which the drive can therefore in particular be overridden, the movement towards the one end position can take place during the compensation cycle by controlling a movement by a specified distance and/or a specified number of steps. Therefore, one end position can only be reached by moving towards one end position if the distance of the closure element from one end position after moving towards the other end position and/or before carrying out the second compensation movement is less than the specified distance and/or step count. In principle, however, a force-controlled movement in the direction of one end position is also conceivable, in which the closure element can always be moved to one end position.

In some embodiments, the flow of the fluid or gas through the flow opening can be blocked by moving the closure element into a blocking section of the valve or ejector, which is limited by the first end position and a blocking position offset from the first end position in the direction of the second end position, and that Closure element can - after moving into the first end position - can only be moved within the locking section by the first compensation movement. In this respect, in such embodiments, the closure element can be moved between the first end position and the blocking position and not out of the blocking section by moving in the direction of the second end position, so that the flow through the flow opening remains blocked despite the movement of the closure element in the direction of the second end position .

In general, moving the closure element in the direction of the second end position - after moving into the first end position - can therefore not result in any flow of gas or fluid through the flow opening and/or the valve or the ejector.

The blocking position can in principle be defined relative to the first end position, whereby an absolute position of the first end position can in turn depend on external conditions and, for example, an expansion of the valve or ejector. For example, the locking position can be defined by a number of steps of a stepwise movable closure element starting from the first end position in the direction of the second end position, with the closure element only being moved by this number of steps or a smaller number of steps in the direction of the second end position Drive for moving the closure element can be controlled by such a number of steps. If the position of the first end position changes due to expansion or contraction of the valve or ejector and this change is compensated for by carrying out the compensation cycle, the blocking position also changes accordingly, so that starting from the new first end position by moving by the constant number of steps and/or or distance of the closure element in the direction of the second end position can be ensured that the flow opening does not open.

In some embodiments, the drive can be controlled to drive the closure element during the first compensation movement with a greater force than during the second compensation movement and/or than when moving into one end position. In this respect, in some embodiments the drive can be controlled to move the closure element with a greater force in the direction of the other end position than in the direction of one end position and/or in some embodiments the drive can be controlled to move the closure element with a greater force in the direction of the other end position than to be controlled in one end position.

This increase in force compared to the driving during the second compensation movement and/or during the movement into one end position makes it possible for the closure element to remain in place despite thermal stresses or forces that build up before the compensation cycle is carried out, which lead to an increase in the force force acting on the closure element and/or jamming of the closure element, can be moved towards the other end position and these thermal stresses or forces can be compensated for. For example, a motor current can be increased compared to moving the closure element into one end position or in the direction of one end position.

In addition, in some embodiments it can be provided that the closure element is moved into the other end position and/or an intermediate position, with the drive for moving the closure element into the other end position and/or the intermediate position with a speed in comparison to the movement of the closure element which can be controlled to an end position and/or increased force compared to the second compensation movement. Even when the closure element is moved to the other end position, any tensions can be reliably overcome. In particular, the motor current can be increased at the beginning of the movement into the other end position and/or an intermediate position in order to then reduce the motor current again and complete the movement, for example with the force with which the closure element was moved into the one end position lead.

In some embodiments, the compensation cycle may be repeated cyclically. In particular, the compensation cycle can be repeated cyclically as long as the closure element is not moved to the other end position or one of the intermediate positions mentioned in order to consciously change a flow through the flow openings. The cyclic control can therefore be carried out as long as the flow opening is closed or should remain closed after moving to the first end position or as long as the flow opening is or should remain open after moving to the second end position.

Furthermore, in some embodiments, a cycle time between two successive executions of the compensation cycle may be constant or may increase successively. In particular, in some embodiments the cycle time can correspond to the waiting time already mentioned.

For example, it can be provided that the drive is activated cyclically to carry out the compensation To control the sation cycle after the closure element has been moved to the first end position or the second end position. If you choose a constant waiting time of 10 seconds, it can be provided, for example, that the drive is activated to carry out the compensation cycle 10 seconds after reaching one end position, in order to be activated again to carry out the compensation cycle 10 seconds after the compensation cycle has been completed. In some embodiments, however, compensation cycles can also be carried out permanently, so that after the end of a compensation cycle, another compensation cycle can be started immediately, as long as the closure element is not available for movement out of one end position or for movement into the other end position or into one the intermediate positions mentioned are controlled.

As an alternative to a constant cycle time, it can also be provided that the time between respective compensation cycles and thus the cycle time increases successively with each cycle or after a predetermined number of compensation cycles, for example with every second or third cycle, so that the movements mentioned become increasingly rare can be carried out. Through this successive extension of the cycle time, the load on the components of the ejector valve associated with the movements of the closure element can be minimized and the effect can be taken into account that the valve or the ejector moves with increasing duration of remaining in one end position and in particular the interruption of the flow through the flow opening is already increasingly approaching a thermal equilibrium and any thermal stresses build up more slowly. Therefore, such tensions can be compensated for even as cycle times lengthen.

In some embodiments, the cyclic repetition of the compensation cycle may be terminated after performing a predetermined or predeterminable maximum number of compensation cycles. In particular, a predetermined or predeterminable maximum number of compensation cycles can therefore be carried out, wherein after the maximum number of compensation cycles have been carried out, a further compensation cycle is only carried out after the closure element has been moved out of one end position and the closure element has been moved again into one of the first end positions the second end position can be carried out. For example, provision can be made to carry out a maximum of five or a maximum of ten compensation cycles.

For example, such a maximum number of compensation cycles can be stored in a controller and/or can be specified by an operator of the valve or ejector. By ending the cyclical repetition of compensation cycles in this way, unnecessary movements of the closure element that lead to stress on the components of the valve or the ejector can be avoided if the closure element remains in the end position for a longer period of time and therefore in view of the increasing approach to a thermal Equilibrium no longer requires major thermal expansion or contraction of the valve or ejector.

The invention further relates to a valve or an ejector, which comprises a closure element movable between a first end position and a second end position, the closure element being designed to close a flow opening of the valve or ejector in the first end position against a flow of fluid or gas to block and to release the flow opening in the second end position for a flow of fluid or gas. Furthermore, the valve or ejector comprises an elastically deformable compensation element, which is arranged in a force transmission path from a housing of the valve or ejector to the closure element. In particular, the valve or the ejector can further comprise a drive for moving the closure element.

The elastically deformable compensation element can generally be constructed and arranged as explained above.

Such an elastically deformable compensation element arranged in a force transmission path from a housing of the valve or ejector, which can also be referred to as a shell, and the closure element can in particular make it possible, for example, to accommodate changes in one of the housing that occur as a result of thermally induced shortening or expansion of the housing to absorb the force transmitted by the closure element through an elastic deformation and thereby achieve mechanical compensation for such expansions and/or contractions.

For example, the compensation element can be designed to exert a bias on the closure element directed away from the second end position (or open position) when the closure element has been moved into the first end position (or closed position). In particular, the compensation element can be elastically deformed when the closure element is positioned in the first end position, so that the compensation element can exert a force opposite to this elastic deformation on the closure element and thereby bias the closure element further in the direction of the flow opening. If the housing of the valve or the ejector then expands, the force exerted by the housing on the closure element, for example via a limitation of the flow opening, is reduced, so that the force transmitted to the compensation element is correspondingly reduced and the compensation element moves in the opposite direction to that previously experienced elastic deformation can develop. This unfolding or deformation of the compensation element allows the closure element to follow the expansion of the housing and in particular the flow opening that moves away due to this expansion, so that the flow opening can still remain reliably closed against leakage. In this respect, such an expansion can lead to a reduction in a closing force, which ultimately corresponds to the reduced preload on the closure element due to the unfolding of the compensation element, but a change in position of the closure element relative to the flow opening as a result of an expansion of the housing of the valve or ejector and a resulting caused leakage can be prevented.

In the opposite case of a shortening of the housing of the valve or ejector in a situation in which the closure element is in the first end position, a force exerted by the housing on the closure element in the direction of the second end position can increase, as a result of which the closure element could fundamentally jam . However, by arranging the elastically deformable compensation element in the force transmission path from the housing to the closure element, this increased force can be absorbed by an elastic deformation of the compensation element, so that the closure element can evade the shortening to a certain extent and jamming of the closure element can be prevented.

In a corresponding manner, expansions or contractions in the second end position can in principle be compensated for in that the compensation element can, for example, be elastically deformed when the closure element is positioned in the second end position, in order to thereby develop a preload on the closure element directed away from the first end position .

Such mechanical compensation of forces transmitted from the housing to the closure element by thermal stresses can thus achieve the object underlying the invention of creating a valve or an ejector in which a reliable closing or opening of a flow opening of the valve or ejector, in particular over longer periods of time, as well as a subsequent reliable movement of the closure element into an opposite end position can be achieved by, on the one hand, achieving reliable positioning of the closure element in the end positions even in the event of any expansion of the housing and, on the other hand, preventing the closure element from jamming when the housing is shortened can be. In particular, such a mechanical compensation can be provided as an alternative or in addition to the positioning method explained above in order to achieve the object on which the invention is based.

The compensation element can be, for example, a spring. However, it is also possible for the closure element to have an elastically deformable section, for example a section made of rubber or plastic, which forms the compensation element and/or that such a section is provided on a component of the valve or ejector, which is located in the Power transmission path from the housing to the closure element is located. Furthermore, the compensation element can be elastically deformable, in particular along a direction of movement of the closure element, in order to be able to mechanically compensate for expansions and/or contractions of the housing of the valve or ejector with respect to this direction of movement by elastically deforming the compensation element.

In some embodiments, the closure element can be supported on the housing via the compensation element. In particular, the closure element can be supported on the housing directly or indirectly via the compensation element. For example, the compensation element can be arranged directly on a housing section of the housing, so that the closure element can be supported on the housing directly via the closure element. However, it is also possible, for example, for the compensation element to be supported on a component of a drive of the closure element that is immovable relative to the housing, for example a motor attached to the housing, so that the closure element is attached to the housing indirectly via the compensation element and the component of the drive can be supported. However, regardless of direct or indirect support, it enables such support of the closure element via an elastically deformable compensation element, the closure element ment as a result of a change in a force exerted on the closure element, bypassing the drive, relative to the support and thus relative to the housing by elastically deforming the compensation element in order to be able to compensate for such force changes. In particular, force changes due to thermally caused changes in length of the housing when the closure element is in one of the end positions and in particular the first end position can be compensated for.

In some embodiments, the closure element can be translationally movable between the first end position and the second end position. In particular, in such embodiments, the compensation element can be elastically deformable axially with respect to the translational movement of the closure element.

In some embodiments, the closure element can be biased towards the first end position by the compensation element. In particular, in some embodiments, the closure element can be biased by the compensation element in the direction of a movement directed away from the second end position when the closure element is positioned in the first end position. As already explained, such a preload can in particular compensate for expansions and/or contractions of the valve or ejector when the closure element is positioned in the first end position and a flow of fluid or gas through the flow opening is thereby blocked.

Furthermore, in some embodiments, the compensation element can be designed to be elastically deformed as a result of a movement of the closure element into the first end position. For example, as a result of moving the closure element into the first end position and abutment of the closure element against a stop of the housing, for example a limitation and/or seal of the flow opening, a force can be transmitted via the closure element to the compensation element, through which the compensation element is elastically deformed can. The compensation element can therefore be deformed in particular elastically when the closure element is positioned in the first end position. This elastic deformation allows the compensation element to exert a preload on the closure element, which is directed away from the second end position and towards the flow opening. If the valve or the ejector then experiences an expansion, the force exerted by the stop on the closure element and transmitted to the compensation element is reduced, so that the compensation element performs a deformation in the opposite direction to the deformation generated by moving the closure element into the first end position and the closure element can thereby track the expansion of the valve or ejector. In particular, an elasticity of the compensation element can be coordinated with a force transmitted to the closure element by a drive for the closure element during the movement into the first end position in such a way that the compensation element is elastically deformable by the force transmitted by the drive.

For example, it can be provided that a spring arranged in the force transmission path from the housing to the closure element is compressed into the first end position as a result of a movement of the closure element, so that the closure element can track any expansion of the valve or ejector by unfolding the spring.

In some embodiments, the compensation element can be elastically deformable by a force exerted on the closure element and directed in the direction of the second end position when the closure element is positioned in the first end position. In particular, the compensation element can thus be designed to absorb larger forces than a force transmitted to the closure element by the drive during the movement of the closure element into the first end position or a closing force developed by the closure element in the first end position through elastic deformation. The compensation element can therefore, for example, absorb a force exerted on the closure element due to a shortening of the housing of the valve or ejector by, in particular, further elastic deformation, so that the closure element can, as it were, avoid the shortening or be carried along with the shortening of the housing. Such a design of the compensation element can therefore in particular prevent the closure element from jamming due to shortening of the housing when the closure element is positioned in the first end position. In order to be able to be elastically deformed by a force exerted on the closure element and directed in the direction of the second end position when the closure element is positioned in the first end position, the compensation element in particular cannot be completely elastically deformed by moving the closure element into the first end position . For example, turns of a compensation element designed as a spring, which is already compressed by moving the closure element into the first end position, cannot come into contact with one another as a result of this movement of the closure element reach, so that further compression of the spring is possible if the housing is shortened.

In some embodiments, the compensation element can be arranged on the closure element or on a connecting section that can be moved in translation together with the closure element. For example, such a compensation element can be formed by an elastically deformable section of the closure element, which can be elastically deformable, in particular as a result of moving the closure element into an end position, in particular the first end position, in order to thereby move the closure element to one of the other end positions, in particular the second End position, to bias away movement and to be able to compensate for any thermal expansion and / or shortening of the valve. For example, such a compensation element can be formed by a section of the closure element made of rubber or plastic and/or by a spring.

A connecting section on which the compensation element can be arranged in some embodiments can, for example, be a section connected to the closure element, which can be movable together with the closure element relative to the housing of the valve or ejector. For example, the connecting section can comprise a plunger which is arranged between the closure element and the drive and transmits a force from the drive to the closure element. By arranging the compensation element on such a section, the compensation element can thus be arranged in a force transmission path from the housing to the closure element in order to be able to compensate for any mechanical stresses.

In some embodiments, the valve or the ejector can comprise a spindle drive for driving the closure element, which has a spindle nut or spindle that can be driven to a rotational movement, the spindle nut or spindle, in particular via a bearing (preferably a roller bearing), through the compensation element on the housing can be supported. In particular, the spindle nut or spindle can only be driven by the drive for a rotary movement, but not for an axial movement. If the closure element is connected to a spindle that is mounted in a rotationally fixed but axially displaceable manner, the closure element can be driven in the axial direction by a threaded engagement of the rotating spindle nut with the spindle. If - in other embodiments - the closure element is connected to a spindle nut that is mounted in a rotationally fixed but axially displaceable manner, the closure element can be driven in the axial direction by a threaded engagement of the rotating spindle with the spindle nut.

In particular, in such embodiments, axial forces transmitted to the closure element can be transferable to the spindle nut or spindle, so that the compensation element can be arranged in a force transmission path from the housing to the closure element and the closure element can also be supported on the housing via the compensation element. Furthermore, in particular direct or indirect support of the spindle nut or spindle can be provided.

The spindle nut or spindle can be driven, for example, via a drive shaft. The drive shaft can, for example, form a motor shaft of a motor of the drive.

The drivable spindle nut or spindle can be biased towards the first end position by the compensation element, in particular via a bearing. In particular, in some embodiments, the spindle nut or spindle can be biased towards the first end position by the compensation element when the closure element is positioned in the first end position. As explained above, the closure element can also be biased in the direction of a movement directed towards the flow opening when the closure element is positioned in the first end position in order to be able to compensate for both thermally caused expansions and contractions of the housing.

In some embodiments, the drivable spindle nut or spindle on the one hand and a drive shaft on the other hand can be rigidly connected to one another, the drive shaft being axially movable relative to an associated drive. For example, the drive shaft can be formed by a rotor of an electric motor, which is axially movable relative to an associated stator of the electric motor; or the drive shaft can be connected to a rotor of an electric motor in a rotationally fixed but axially movable manner. In principle, a slight axial mobility of the drive shaft is sufficient. In other embodiments, the drivable spindle nut or spindle on the one hand and the drive shaft on the other hand can be connected to one another in a rotationally fixed manner, but can be axially displaceable relative to one another. In particular, in such embodiments, the spindle nut or spindle can be axially movable relative to a drive shaft that is axially fixed with respect to the housing. Furthermore, in particular, a bearing of the spindle nut or spindle can also be axially relative to the drive shaft be arranged movably. Such an axially movable connection can in particular enable a movement of the closure element bypassing the drive - by elastically deforming the compensation element - in order to be able to compensate for shortenings or expansions of the housing, but due to the always rotationally fixed coupling of the spindle nut or the spindle to the drive A targeted movement of the closure element by the drive is possible at any time.

In some embodiments, the valve or the ejector can comprise a motor, in particular a stepper motor, through which a drive shaft can be driven.

In some embodiments, the compensation element can also be designed as a spring, in particular a plate spring. In particular, a disc spring as a compensation element can make it possible to absorb relatively large forces with a small spring travel, so that minor expansions and/or shortenings of the valve or ejector can be reliably mechanically compensated for by such a disc spring.

Furthermore, in some embodiments, the valve or the ejector can have a controllable drive for the closure element and the valve or the ejector can be connected to a control device which is designed to position the closure element according to one of the methods explained above. In such embodiments, it can therefore be provided in particular that, in addition to the described mechanical compensation of expansions and/or contractions, control technology compensation can also be carried out using the positioning method explained.

The invention further relates to a valve and/or ejector system, which comprises a valve or an ejector and a closure element movable between a first end position and a second end position, the closure element permitting a flow of fluid or gas through a flow opening of the valve or ejector blocked in the first end position and releases the flow opening in the second end position for a flow of fluid or gas. In addition, the system includes a drive, in particular an electric drive, for moving the closure element and a control device which is set up to position the closure element according to a method of the type described herein.

In particular, the control device can be provided to control the drive for moving the closure element in such a way that the closure element is positioned according to a method of the type described herein. The control device can be provided directly for the valve or the ejector or can be part of a control device of a device in which the valve or the ejector is installed. For example, the control device can be part of a control device of a refrigeration system, a heating system or a refrigeration cabinet or can be formed by such a control device in order to be able to position closure elements of valves or ejectors installed in a refrigeration system according to the method explained. The control device can include a CPU (Central Processing Unit) and/or a microcontroller.

By designing the control device for positioning the closure element according to the method explained, thermally induced expansions or contractions of the valve or ejector of the valve and/or ejector system can be compensated for while the flow opening of the valve or ejector is closed by the closure element. This can, for example, ensure that the flow opening remains reliably closed or released despite any thermal expansion of the valve or ejector, but on the other hand, any thermal stresses that build up do not lead to the closure element becoming wedged or jammed and the flow opening can be reliably opened or closed. In addition, any incorrect positioning of the closure element in one end position can be compensated for.

In some embodiments, the drive may include a stepper motor. For example, the stepper motor can be part of a spindle drive, the spindle or spindle nut of which is connected to the closure element. The closure element can also be movable in particular translationally between the first end position and the second end position.

Furthermore, in some embodiments the closure element can be designed as a valve needle. For example, the closure element can be intended to selectively close or release a valve seat of a seat valve or an ejector.

In some embodiments, the at least one valve and/or the at least one ejector can further be designed according to one of the embodiments of a valve or ejector explained above, which has an elastic ver has a malleable compensation element, which is arranged in a force transmission path from a housing of the valve to the closure element. In some embodiments, the valve and/or ejector system can thus comprise at least one valve and/or at least one ejector according to one of these embodiments.

The invention also relates to a refrigeration system, a refrigeration cabinet or a heating system with a valve or an ejector system of the type explained above and / or with a valve and / or an ejector according to one of the embodiments explained above, in which an elastically deformable compensation element is provided is.

In a refrigeration system, a refrigeration cabinet or a heating system, in particular a refrigeration or heat circuit can be provided, for example a liquid coolant can be supplied to an evaporator in order to extract the heat required to evaporate the coolant from the environment. The vaporized refrigerant can then be fed to a compressor and compressed to condense in a condenser and thereby release heat. The liquefied coolant can be fed back into the evaporator. Furthermore, an expansion valve can be connected between the condenser and the evaporator in order to reduce the pressure of the liquid refrigerant supplied. An ejector can be provided in such a circuit, for example, to suck in coolant that has not evaporated and to carry out pre-compression in order to relieve the load on the compressor. Depending on the arrangement of the evaporator and the condenser, such a circuit can be used in particular in a refrigeration or heating system. In addition, such a refrigeration circuit can be used, for example, in refrigeration units, such as a refrigerator.

A refrigeration system with a refrigeration circuit that includes an ejector and several valves is, for example, in DE 10 2016 123 277 A1 described, the content of which is explicitly included in the present disclosure with regard to the design of such a refrigeration circuit, the formation of an ejector and a refrigeration/heating system.

In principle, a large number of valves or ejectors with respective closure elements can be provided in refrigeration or heat circuits in order to be able to influence the operation of the evaporator, the compressor, the condenser or the expansion valve and/or to be able to stop the operation if necessary. In addition, in such circuits or the corresponding systems, relatively large temperature differences can arise between individual sections, which can lead to the thermal stresses explained. Changing ambient temperatures can also result in such tensions. The valve and/or ejector system disclosed herein and/or the valve disclosed herein or the ejector disclosed herein with mechanical compensation for thermal stresses are therefore particularly suitable for use in such refrigeration systems, refrigeration cabinets or heating systems in order to compensate for such stresses and achieve reliable operation to be able to.

The invention therefore also relates to the use of a valve and/or ejector system of the type explained above and/or a valve or ejector according to one of the embodiments explained above with an elastically deformable compensation element in a refrigeration system, in a refrigeration cabinet or in a heating system.

• 1A bis 1 D eine jeweilige schematische Darstellung eines Ventils mit einem zwischen einer ersten Endlage und einer zweiten Endlage bewegbaren Verschlusselement in der zweiten Endlage, einer Zwischenstellung, einer Sperrstellung bzw. der ersten Endlage,
• 2A und 2B eine schematische Darstellung eines Ejektors mit einem zwischen einer ersten Endlage und einer zweiten Endlage bewegbaren Verschlusselement in der zweiten Endlage bzw. der ersten Endlage,
• 3 ein Blockdiagramm zur Veranschaulichung eines Verfahrens zum Positionieren eines Verschlusselements eines Ventils oder Ejektors,
• 4A bis 4C schematische Darstellungen eines Ventils zur Veranschaulichung eines Ausgleichens einer Verkürzung des Ventils aufgrund thermischer Spannungen durch Anwenden des Verfahrens,
• 5A bis 5D schematische Darstellungen eines Ventils zur Veranschaulichung eines Ausgleichens von Ausdehnungen des Ventils infolge thermischer Spannungen durch Anwenden des Verfahrens,
• 6 eine schematische Darstellung einer Kälteanlage mit einem Ventil- und/oder Ejektorsystem, bei welchem Verschlusselemente eines Ejektors und mehrerer Ventile des Ventil- und/oder Ejektorsystem gemäß dem beschriebenen Verfahren positionierbar sind,
• 7A bis 7C schematische Darstellungen eines Ventils mit einem zwischen einer ersten Endlage und einer zweiten Endlage bewegbaren Verschlusselement, bei welchem in einem Kraftübertragungspfad von einem Gehäuse des Ventils zu dem Verschlusselement ein elastisch verformbares Kompensationselement angeordnet ist, zur Veranschaulichung einer mechanischen Kompensation von Ausdehnungen und Verkürzungen des Gehäuses, wenn das Verschlusselement in der ersten Endlage positioniert ist, und
• 8A bis 8C schematische Darstellungen einer weiteren Ausführungsform eines Ventils mit einem elastisch verformbaren Kompensationselement, welches in einem Kraftübertragungspfad von einem Gehäuse des Ventils zu einem Verschlusselement angeordnet ist.

The invention is explained below purely by way of example using exemplary embodiments with reference to the drawings. Show it:

• 1A to 1D a respective schematic representation of a valve with a closure element that can be moved between a first end position and a second end position in the second end position, an intermediate position, a blocking position or the first end position,
• 2A and 2 B a schematic representation of an ejector with a closure element that can be moved between a first end position and a second end position in the second end position or the first end position,
• 3 a block diagram illustrating a method for positioning a closure element of a valve or ejector,
• 4A to 4C schematic representations of a valve to illustrate compensation for a shortening of the valve due to thermal stresses by applying the method,
• 5A to 5D schematic representations of a valve to illustrate compensation for expansion of the valve as a result of thermal stresses by using the method,
• 6 a schematic representation of a refrigeration system with a valve and/or ejector system, in which closure elements of an ejector and several valves of the valve and/or ejector system can be positioned according to the method described,
• 7A to 7C schematic representations of a valve with a closure element movable between a first end position and a second end position, in which an elastically deformable compensation element is arranged in a force transmission path from a housing of the valve to the closure element, to illustrate mechanical compensation of expansions and contractions of the housing, if the closure element is positioned in the first end position, and
• 8A to 8C schematic representations of a further embodiment of a valve with an elastically deformable compensation element, which is arranged in a force transmission path from a housing of the valve to a closure element.

The 1A to 1D schematically show a valve 13 which has an inlet 55 and an outlet 57, so that an input stream E of a fluid or gas can flow in through the inlet 55 and leave the valve 13 as an output stream F through the outlet 57. The input stream E of fluid or gas enters a housing 59 through a flow opening 17, which the output stream F leaves through an outlet opening 19 of the outlet 57. In the embodiment shown, the input current E changes its direction within the housing 59, so that the output current F is aligned perpendicular to the input current E. However, this is not mandatory, rather a deflection within a valve 13 can basically take place at any angle or an input flow E can be guided in a straight line through a valve 13. Furthermore, a valve 13 can also have more than one input 55 and/or more than one output 57.

In order to be able to regulate the flow of fluid or gas through the housing 59, the valve 13 also has an in 1A shown second end position O, which can also be referred to as the open position, and one in 1D shown first end position G, which can also be referred to as the closed position, movable closure element 11 and a drive 23 for moving the closure element 11. In the embodiment shown schematically, the closure element 31 is movable in translation between the second end position O and the first end position G and is designed as a valve needle 31, which is shown with an extension 29 to illustrate the functionality. To drive the closure element 11, the drive 23 has an electric motor 25, which can have a stator and a rotor (not shown) and which can in particular be a stepper motor. The motor 25 is connected to the closure element 11 via a spindle 27 (shown only in simplified form here), wherein a rotation of a motor shaft of the motor 25 can be converted into a translational (axial) movement of the closure element 11.

In the in 1A In the second end position 0 shown, the closure element 11 is located at the maximum distance from the flow opening 17 and the flow opening 17 is released for a flow of fluid or gas. Therefore, the input current E can enter the housing 59 and leave it as the output current F through the output opening 19 and the output 57.

However, starting from the second end position O, the closure element 11 can be moved by the drive 23 towards the flow opening 17 and into various intermediate positions Z in order to regulate the flow of fluid or gas through the valve 13. 1B shows such an intermediate position Z, in which the flow opening 17 is still opened and the input flow E can enter the housing 59, but the closure element 11 already limits the space available for the entry of fluid or gas. By moving the closure element 11 into the intermediate position Z, a strength of the output current F can therefore be reduced compared to a positioning of the closure element 11 in the second end position O, whereby this strength can be further reduced by increasingly moving the closure element 11 towards the flow opening 17.

By further moving the closure element 11 in the direction of the flow opening 17, the closure element 11 can also be converted into an in 1C illustrated blocking position B can be moved, in which the extension 29 covers the flow opening 17 and thereby prevents the input current E from entering the housing 59. Already in this position of the closure element 11, the flow opening 17 is thus blocked and closed against penetration of the input stream E, so that a flow of fluid or gas is blocked in the blocking position B and no output stream F emerges from the output 57.

However, the closure element 11 is in the in 1C The blocking position B shown is not yet in an end position with respect to a movement in the direction of the flow opening 17, so that the closure element 11 extends even further into an in 1D shown first end position G can be moved, in which the flow opening 17 is completely closed by the closure element 11. In particular, the closure element 11 lies in the first end position G at a limitation 83 of the flow opening 17, wherein the closure element 11 can exert a first closing force C1 on the boundary 83 as a result of moving into the first end position G and can close the flow opening 17 with the first closing force C1. The limitation 83 can in particular be a seal of the flow opening 17, such a seal being able to be deformed in particular by moving the closure element 11 into the first end position G and exerting the first closing force C1.

In the present schematic representations, the closure element 11 is shown as an example with the extension 29 in order to illustrate the individual positions of the closure element 11 and in particular the blocking position B as a position that already blocks the flow opening 17 and the first end position G as an end position of the movement of the closure element 11 to be able to. However, in valves 13 it can be provided that the closure element 11 has no extension 29 and the first end position G and the blocking position B are defined primarily by a respective force exerted by the closure element 11 on a boundary 83 or a seal of the flow opening 17.

In addition, the flow opening 17 in the first end position G can also be blocked against a flow of fluid or gas by abutment of conical surfaces 84 of the closure element 11 on correspondingly shaped inner surfaces 86 of the housing 59, so that there is not necessarily an axial stop for the valves 13 Closure element 11 must be provided, but the flow opening 17 can also be blocked solely by the contact of the conical surfaces 84 on the inner surfaces 86. Even in such embodiments, further movement of the closure element 11 is prevented by the contact of the conical surfaces 84 on the inner surfaces 86.

The blocking position B can therefore generally be defined by the position of the closure element 11 in which the flow opening 17 is blocked against a flow of fluid or gas and no output flow F emerges from the valve 13. The first end position G, on the other hand, can be defined by the position in which the closure element 11 exerts a first closing force C1 on the boundaries 83 or seals of the flow opening 17, which is a force that can be transmitted by the drive 23 for moving the closure element 11 into the first end position G corresponds. The first end position G and the blocking position B further define a blocking area 85 of the valve 13, with no fluid or gas entering the housing 59 through the flow opening 17 when the closure element 11 is positioned in the blocking area 85.

In some embodiments, the motor 25 can be designed as a stepper motor and the motor can be controlled to move the closure element 11 into the first end position G in such a way that the motor 25 is controlled to carry out further steps after reaching the first end position G and step losses learns. Such control can ensure that the closure element 11 actually reaches the first end position G. Furthermore, for example, a motor current of the motor 25 and thus the force that can be transmitted from the drive 23 to the closure element 11 can be adjustable, so that the first closing force C1, with which the closure element 11 closes the flow opening 17 in the first end position G, than that of Motor 25 transmittable force can be adjustable. In addition, the absolute position of the first end position G can also depend on the set force that can be transmitted by the drive 23, since, for example, if a larger force is set after hitting a seal of the flow opening 17, another step can be carried out and the seal can be further compressed, whereas if a lower force is set, this step can no longer be carried out and the first end position G has already been reached one step earlier.

The 2A and 2 B further illustrate schematically an ejector 15, which also has a closure element 11 which can be moved in translation between a second end position O and a first end position G, and a drive 23 for moving the closure element 11. Again, the drive 23 has a motor 25, which is connected to the closure element 11, for example via a spindle 27, in order to be able to move the closure element 11 translationally. Illustratively, the closure element 11 is again shown with an extension 29, although such an extension 29 does not necessarily have to be provided.

The ejector 15 has a drive connection 49 through which a drive current T can enter the ejector 15. The driving stream T is guided through a driving nozzle 51 and thereby accelerated in order to leave the driving nozzle 51 through a flow opening 17. Due to the negative pressure resulting from the acceleration of the driving flow T, a suction flow U of a suction medium is sucked in through a suction connection 53, so that the driving flow T and the suction flow U leave the ejector 15 as an output flow F through an output 57 and an output opening 19 of the ejector 15.

In the in 2A shown second end position O of the closure element 11, the flow opening 17 is released for a flow of fluid or gas and in particular of the driving flow T. How 2 B shows, the flow opening 17 can, however, be closed by moving the closure element 11 into the first end position G with a first closing force C1, so that the driving current T cannot flow through the flow opening 17. Due to the lack of negative pressure, the suction flow U is not sucked in and no output flow F leaves the ejector 15, so that the output flow F ultimately, as already based on 1A to 1D explained for the valve 13, can be influenced and in particular prevented by positioning the closure element 11.

In the first end position G, in particular, conical surfaces 84 of the closure element 15 rest on correspondingly shaped inner surfaces 86 of the driving nozzle 51 in order to thereby block the flow opening 17 against a flow of fluid or gas, so that there is no axial end stop or a circumferential limitation in the ejector 15 83 of the flow opening 17 is provided, on which the closure element 15 abuts axially in the first end position G. Nevertheless, as a result of the movement into the first end position G, the closure element 15 can abut on the inner surfaces 86 of the driving nozzle 51, so that further movement away from the second end position O is blocked due to this abutment and the first end position G is again defined as a position of the closure element 15 can be, in which a force transmitted from the drive 23 to the closure element 15 is compensated and further movement away from the second end position O is prevented.

In summary, a closure element 11 that can be moved between a second end position O and a first end position G can be provided in the ejector 15 or the valve 13 in order to regulate a flow of fluid or gas through a respective flow opening 17 and in particular to be able to selectively release or block it , whereby in the first end position G a flow through the valve 13 or the ejector 15 is blocked and no output flow F leaves the valve 13 or the ejector 15. In the first end position G of the closure element 11, there is therefore no mass flow through the valve 13 or the ejector 15, although this lack of mass flow can lead to thermal changes in components of the valve 13 or the ejector 15, which affect the closure element 11 and/or or the housing 59 acting thermal stresses can be reflected. In particular, these stresses can arise due to different thermal expansion coefficients of individual components of the valve 13 or the ejector 15 when the valve 13 or the ejector 15 cools or heats up due to the lack of mass flow.

For example, a lack of flow of warm medium can result in the valve 13 or the ejector 15, in particular the housing 59 of the valve 13 or ejector 15, shortening as a result of cooling and transmitting a tension force to the closure element 11. However, due to such tensions, the closure element 11 can possibly jam in the first end position G, so that the closure element 11 can no longer be released from the first end position G in order to be moved into an intermediate position Z or the second end position O and at a later point in time to allow a flow of fluid or gas. Conversely, however, a lack of mass flow can also result in an expansion of the valve 13 or the ejector 15 or the respective housing 59, due to which the closing force C1 exerted by the closure element 11 can be reduced, which can possibly lead to an unwanted leak. Furthermore, even after moving the closure element 11 into the second end position O, tensions may occur which jam the closure element 11, so that the closure element 11 may no longer move into the first end position G to close the flow opening 17 and the valve 13 or the ejector 15 can no longer be operated.

However, in order to compensate for such mechanical stresses and to be able to achieve a reliable closure of the respective flow opening 17 of the valve 13 or ejector 15 after the closure element 11 has been moved into the first end position G, provision can be made for the closure element 11 according to one based on 3 to position the illustrated procedure. In addition, the method can be used in an analogous manner after moving the closure element 11 into the second end position O in order to prevent the closure element 11 from jamming and to enable tension forces to be reduced.

In the method described here, the closure element 11 is first moved into the first end position G or the second end position O, in the method according to 3 For example, in the first end position G, so that the flow opening 17 is closed and a flow of gas or fluid through the flow opening 17 is blocked. To move the closure element 11 into the first end position G, the motor 25 can in particular be operated with a first motor current M1 in order to close the flow opening 17 with the already mentioned to close the first closing force C1. If necessary, the valve 13 or the ejector 15 can then be opened in a step 63 by moving the closure element 11 into an intermediate position Z or the second end position O. Based on this, step 61 can be repeated if necessary and the closure element 11 can be moved to the first end position G.

However, if the closure element 11 is not moved out of the first end position G within a waiting time ΔT, for example a waiting time of 10 seconds, after the waiting time ΔT it can be checked in a step 71 whether the closure element 11 is still in the first end position G and this positioning can be recognized in a step 65. This can be done in particular by not detecting a command to move the closure element 11 during the waiting time ΔT. If the closure element 11 is still in the first end position G after the waiting time ΔT or if the flow opening 17 is still closed, a compensation cycle R can be carried out in steps 67 and 69, during which the closure element 11 is used to carry out a first compensation movement R1 in the direction the second end position O and thus the other end position O compared to the first end position G and to carry out a second compensation movement R2 in the direction of the first end position G and thus the one end position G into which the closure element 11 was originally moved.

In particular, the closure element is, for example, first controlled in step 67 to carry out the first compensation movement R1 in the direction of the second end position O, wherein the closure element 11 can be moved in particular by a first distance W1 in the direction of the second end position O. This first compensation movement R1 enables the valve 13 or the ejector 15 to release any thermal stress that may have built up by carrying out a shortening. The motor 25 can also be controlled to move the closure element 11 in the direction of the first end position O with a motor current M2, which can in particular be greater than the motor current M1. This can ensure that the closure element 11 can be released from the first end position G even if any tension builds up due to shortening of the valve 13 or the ejector 15 during the waiting time ΔT.

After moving the closure element 11 by the distance W1 in the direction of the second end position O, the closure element 11 can be controlled in the step 69 to carry out the second compensation movement R2 in the direction of the first end position G. In particular, the drive 23 can be controlled to move the closure element 11 by a second distance W2 in the direction of the first end position G, wherein the second distance W2 can be greater than the first distance W1. By choosing the distance W2 in this way, it can be achieved that any expansions of the valve 13 or the ejector 15 can be compensated for, in that the closure element 11 can, as it were, track such expansions and the resulting removal of the flow opening 17. However, if the valve 13 or the ejector 15 is shortened, the closure element 11 cannot cover the entire second distance W2, but a motor shaft of the motor 25 blocks before the second distance W2 has been covered. In addition, the closure element 11 can be moved increasingly further into the mechanical first end position G by such a choice of the distances W1 and W2 through the compensation cycle R if the closure element 11 does not completely reach the first end position G, for example during step 61 due to step losses of the motor 25 has achieved, so that any incorrect positioning of the closure element 11 can be compensated for.

In particular, the first distance W1 and the second distance W2 can be defined by respective step numbers S1 and S2, by a motor 25 designed as a stepper motor for driving the first compensation movement R1 in the direction of the second end position O for carrying out a first number of steps S1 and for driving the second compensation movement R2 can be controlled in the direction of the first end position G to carry out a second number of steps S2. The second number of steps S2 can be larger than the first number of steps S1, in particular by exactly one step, so that by carrying out steps 67 and 96 in particular expansions of the valve 13 or the ejector 15 by the distance of the closure element to be covered in one step of the stepper motor 25 11 to be able to compensate. For example, it can be provided to move the closure element 11 by two steps in the direction of the second end position O and by three steps in the direction of the first end position G. In addition, the closure element 11 can be moved by less than 10 μm, in particular by approximately 7 μm, by one step of the stepper motor 25.

In principle, the closure element 11 can be moved back into the first end position G by step 69. However, it is possible that expansions of the valve 13 or the ejector 15 occur during the waiting time ΔT, which cannot be completely compensated for by carrying out the compensation cycle R and steps 67 and 69 once, so that the closure element 11 In step 69, the first end position G, in which the flow opening 17 is closed with the force that can be transmitted from the drive 23 to the closure element 11, is not necessarily reached again. Nevertheless, by tracking the closure element 11 in this way, expansions can be compensated for and it can be achieved that the closure element 11 remains at least in the blocking area 85 in order to prevent leakage. In addition, larger expansions can be completely compensated for by cyclically repeating steps 67 and 69.

The closure element 11 can also be moved in step 69 with a third motor current M3 in the direction of the first end position G and in particular up to the first end position G. The motor current M3 can in particular be smaller than the motor current M1 and/or, for example, be 80% of the motor current M1, so that the flow opening 17 can be closed as a result of step 69 with a second closing force C2 that is reduced compared to the first closing force C1. In particular, loads on components of the valve 13 or the ejector 15 as a result of the movements of the closure element 11 can be minimized by reducing the closing force and a more clearly defined and constant closing force can also be set. However, it is also possible for the motor current M3 to correspond to the motor current M1 and for the flow opening 17 to be closed again with the first closing force C1 as a result of the second compensation movement R2.

By carrying out steps 67 and 69, any thermal stresses and both shortenings and expansions of the valve 13 or the ejector 15 that occur during the waiting time ΔT can be compensated for. In order to be able to compensate for any further thermal stresses that may occur even if the closure element 11 remains in the first end position G for a longer period of time, the compensation cycle R can be repeated cyclically and after carrying out step 69 and moving the closure element 11 in the direction of the first end position G After a cycle time ΔT1, which can correspond in particular to the waiting time ΔT, it is checked again in a step 73 whether the closure element 11 is in the first end position G or in any case has not been transferred to an intermediate position Z. If this is the case, the compensation cycle R can be repeated with steps 67 and 69 in order to be able to resolve further tensions built up during the cycle time ΔT1. The control of the closure element 11 to carry out the first compensation movement R1 in the direction of the second end position O and to carry out the first compensation movement R2 in the direction of the first end position G can thus be repeated cyclically, with the cycle time ΔT1 being selected in particular to be constant or, for example, after each execution steps 67 and 69 can be increased.

In addition, it can also be provided that during the compensation cycle R first the second compensation movement R2 and then the first compensation movement R1 is carried out, i.e. the closure element 11 is first controlled to move towards the first end position G and then to move away from the first end position G becomes. Such an approach can also reduce mechanical stresses, and by moving the closure element 11 only within the locking section 85 it can be ensured that no leakage occurs.

As an alternative to the closure element 11 remaining in the first end position G, after carrying out step 69 during the cycle time ΔT1, a control command for moving the closure element 11 into the second end position O or an intermediate position Z and step 63 can also take place, whereupon the method when the closure element 11 is moved again into the first end position G in a subsequent step 61 can be carried out again. As already mentioned, however, the method can also be carried out in an analogous manner after reaching the second end position O in order to prevent the closure element 11 from jamming and/or to be able to compensate for any incorrect positioning. In this respect, step 69 and reaching the second end position O can be followed by steps 67 and 69 and the compensation cycle R, provided that the closure element 11 is not moved out of the second end position O during the waiting time ΔT. Even after reaching the second end position O, the compensation cycle R can be carried out, for example, in such a way that first the first compensation movement R1 and thus step 67 and then the second compensation movement R2 and step 69 are carried out. Alternatively, step 69 can also take place first and then step 67.

An example was given using: 3 an embodiment is explained in which the compensation cycle R is carried out after a waiting time ΔT after reaching the first end position G or the second end position O. However, in some embodiments it can also be provided that a first compensation cycle R is carried out immediately after reaching one of the end positions G or O, so that the closure element 11 is activated to carry out the compensation movements R1 and R2 immediately after reaching an end position G or O can be. After When an end position G or O is reached, a first compensation cycle R can therefore take place immediately, whereby after the first compensation cycle R has been completed, further compensation cycles R can optionally be carried out and the compensation cycle R can be repeated cyclically. In this regard, it can be provided, for example, that after the first compensation cycle R carried out immediately after reaching an end position G or O, further compensation cycles R are carried out with the cycle time ΔT1 between respective compensation cycles R, so that a further compensation cycle R can only be carried out if After the completion of a respective compensation cycle R, the closure element 11 is not moved out of the respective end position G or O during the cycle time ΔT1, for example within 10 seconds. Alternatively, however, the further compensation cycles R can also be started immediately after the completion of a respective compensation cycle R, so that in some embodiments the closure element 11 can be permanently moved within the scope of the compensation movements R1 and R2, as long as the closure element 11 is not required to move into the respective other end position O or G or one of the intermediate positions Z mentioned is controlled.

In addition, in some embodiments, compensation cycles R can only be carried out until a predetermined maximum number of consecutive compensation cycles R is reached, for example five or ten compensation cycles R. As soon as the maximum number has been reached, the closure element 11 can remain stationary in such embodiments and another Compensation cycle R can only be carried out when the closure element 11 has first been moved from the respective end position G or O into the respective other end position O or G or one of the intermediate positions Z and then back into one of the end positions G and O.

The 4A to 4C illustrate the compensation of shortenings of the valve 13 due to thermal stresses by the method described after the closure element 11 has been moved into the first end position G or into the closed position.

In 4A the valve 13 is shown with the closure element 11 positioned in the first end position G, although a tension force K is shown, which acts on the closure element 11 as a result of thermal stresses in the housing 59. If the closure element 11 is now moved in the method step 67 after the waiting time ΔT in the direction of the second end position O and the first compensation movement R1 is carried out, the valve 13 experiences a shortening V due to this tension force K, which is no longer compensated by the closure element 11, and follows the movement, so to speak of the closure element 11 (cf. 4B) . Since the shortening V corresponds to the first distance W1 in the situation shown as an example, the closure element 11 does not move away from the flow opening 17 despite the movement by the first distance W1 and the first number of steps S1 in the direction of the second end position O, but remains in the first End position G. The following explains how 4C illustrates, the closure element 11 is indeed activated to carry out the second compensation movement R2 in the direction of the first end position G, but since the closure element 11 is already in the first end position G, the corresponding movement is not carried out and the motor 25 experiences step losses of the activated second number of steps S2. If further tension forces K then arise or the tension force K has not yet been completely compensated for by the shortening V, these tension forces can be adjusted by cyclically repeating the compensation cycle R and process steps 67 and 69 (cf. 3 ) be balanced.

Based on 5A to 5D Conversely, the compensation of an expansion A is illustrated, which the valve 13 carries out when the closure part 11 is positioned in the first end position G, for example due to the changing thermal conditions and/or pressure conditions. In 5A the closure element 11 is again shown in the first end position G, with the housing 59 in the in 5B situation shown has experienced an expansion A due to thermal stresses, so that the flow opening 17 is removed from the closure element 11 and a closing force exerted by the closure element 11 is reduced.

Once again, after the waiting time ΔT, the closure element 11 is moved by the first distance W1 and the first number of steps S1 in the direction of the second end position O (cf. 5C ). However, the distance W1 is chosen to be so short that the closure element 11 remains in the blocking section 85 of the valve 13 and is only moved between the first end position G and the blocking position B, so that leakage is prevented. After moving the closure element 11 in the direction of the second end position O, the closure element 11 becomes like 5D shows to move the second distance W2 and the second number of steps S2 in the direction of the first end position G and in particular into the first end position G, the second distance W2 being greater than the first distance W1 and the second number of steps S2 being greater than the first number of steps S1 is. Due to this choice of the distances W2 and W1 or the number of steps S2 and S1, the closure element 11 ultimately tracks the expansion A of the valve 13 through the two opposite movements, so that the flow opening 17 is reliably closed again after carrying out the method steps 67 and 69 . Due to the setting of the third motor current M3, the flow opening 17 is also closed with the second closing force C2, which is reduced in comparison to the first closing force C1. Any further or larger expansions A of the valve 13 can be compensated for by cyclically repeating method steps 67 and 69 as explained.

Regarding the explained embodiments of a closure element 11 with an extension 29, it should also be noted that when the closure element 11 is moved from the first end position G (closed position) in the direction of the second end position O, the extension 29 initially prevents a flow of fluid or gas. Without the extension 29, however, moving the closure element 11 from the first end position G towards the second end position O almost immediately causes a flow of fluid or gas (continuously increasing leakage). This effect can be reduced or even avoided by a compensation element 87, as will be explained below.

The 7A to 7C illustrate a valve 13, which enables mechanical compensation of thermal stresses that build up in the first end position G or a closed position. The valve 13 is basically like that, for example based on the 1A to 1D illustrated valve 13 is formed so that the same components are designated by the same reference numerals.

In particular, the valve 13 thus has a drive 23, by means of which a closure element 11 can be moved between the first end position G and the second end position O, with a motor 25 of the drive 23 being axially immovable on the housing 59 relative to a housing 59 of the valve 13 is held. In the 7A to 7C the closure element 11 is shown in the first end position G, in which a flow opening 17 of the valve 13 is blocked by the closure element 11 against a flow of fluid or gas. However, the closure element 11, in contrast to that based on 1A to 1D shown embodiment does not have an extension 29, so that the flow opening 17 is blocked in particular by the closure element 11 resting against a boundary 83 of the flow opening 17 when the closure element 11 is moved into the first end position G.

In order to enable mechanical compensation of thermal stresses, the valve 13 also has an elastically deformable compensation element 87, which is arranged in a force transmission path from the housing 59 to the closure element 11. The compensation element 87 makes it possible to absorb changing forces transmitted from the boundary 83 to the closure element 11, for example as a result of an expansion A or a shortening V of the housing 59, and to thereby compensate for such changes in force when the closure element 11 is positioned in the first end position G . In this way, leakage and/or jamming of the closure element 11 can be largely prevented. This is explained in more detail below.

7A shows the valve 13 after the closure element 11 has been moved into the first end position G. In particular, the compensation element 87 arranged, for example, on the closure element 11, which can be made of an elastically deformable material and, for example, rubber and/or designed as a spring, can already be in this position due to the position between the closure element 11 and the boundary 83 of the flow opening 17 acting and thus transmitted to the compensation element 87 closing force C1 can be elastically deformed, so that the closure element 11 can be biased by the compensation element 87 in the direction of a further movement towards the flow opening 17. However, such a movement is prevented due to the closure element 11 striking the boundary 83.

If the housing 59 experiences, for example, a shortening V after moving the closure element 11 into the first end position G, a force is exerted from the limitation 83 on the closure element 11 and on the compensation element 87 due to this shortening V. How 7B shows, the compensation element 87 can absorb this force through an elastic deformation, so that the closure element 11 can, so to speak, avoid the shortening V and be moved against the preload exerted by the compensation element 87. Although the shortening V can increase a preload exerted by the compensation element 87 on the closure element 11, so that the closure element 11 can also close the flow opening 17 with an increased force compared to the closing force C1, jamming of the closure element 11 can occur can be avoided due to the absorption of the force by an elastic deformation of the compensation element 87. If the closure element 11 is then controlled to move into the second end position O, the compensation element can first move ment 87 relax due to the reducing force between the motor 25 and the closure element 11 and the closure element 11 can then be removed from the flow opening 17 as soon as the compensation element 87 has reached an installed state.

7C illustrates a situation in which the housing 59 experiences an expansion A after moving the closure element 11 into the first end position G. Since the compensation element 87 has already been elastically deformed by moving the closure element 11 into the first end position G and therefore exerts a preload on the closure element 11 in the direction of the flow opening 17, the closure element 11 can be adjusted to a certain extent to the expansion A of the housing 59 by the elastically deformed compensation element 87 relaxes and also expands. As a result, the closure element 11 can be held in contact with the boundary 83 despite the expansion A in order to avoid unwanted leakage.

In principle, any thermal changes in length of the housing 59 can also be reliably compensated for by such a mechanical solution. In particular, the valve 13 or its drive 23 can be controllable and the valve 13 can be equipped with a control device 79 (see also 6 ) be connected, which is designed to position the closure element 11 according to the method explained above, so that both mechanical and control compensation for changes in length of the housing 59 can be provided.

With regard to carrying out the positioning method explained in a valve 13 with an elastically deformable compensation element 87 arranged in a force transmission path from the housing 59 to the closure element 11, there is also the special feature that the control is activated during a compensation cycle R after reaching the first end position G first compensation movement R1 can be compensated for by an elastic deformation of the compensation element 87. In this respect, a force exerted by the closure element 11 on the boundary 83 can be reduced by the first compensation movement R1 in order to reduce mechanical stresses, but the closure element 11 does not have to be moved for this and the flow opening 17 can remain reliably closed.

The control of the first compensation movement is basically done using a 7C illustrated expansion A of the housing 59 is comparable, in that a force exerted by the closure element 11 on the boundary 83 is reduced even when the closure element 11 is controlled to be removed from the flow opening 17 by the drive 23. Therefore, the elastically deformed compensation element 87 can also expand as a result of such a controlled movement and thereby compensate for the controlled first compensation movement R1 so that the closure element 11 does not move away from the flow opening 17.

The 8A to 8C show a further embodiment of a valve 13 with an elastically deformable compensation element 87 arranged in a force transmission path between a housing 59 of the valve 13 and a closure element 11.

In this embodiment, the drive 23 for the closure element 11 is designed as a spindle drive 101 and has a drive shaft 99 that can be set in rotation by an electric motor 25, in particular a stepper motor. The drive shaft 99 is designed to set a spindle nut 93 in rotation, the spindle nut 93 being connected to the drive shaft 99 in a rotationally fixed manner but axially displaceable relative to the drive shaft 99. Alternatively, the spindle nut 93 could be rigidly connected to the drive shaft 99 and the drive shaft 99 could form a rotor of the motor 25 that is axially displaceable relative to a stator. A spindle 27 with an external thread is also guided within an internal thread 91 of the spindle nut 93 and is mounted in the housing 59 in a rotationally fixed but axially movable manner. The spindle 27 is thus in threaded engagement with the spindle nut 93 and can be set in translational motion due to the rotation of the spindle nut 93. This translational movement is transferred to the closure element 11.

In this embodiment, the compensation element 87 is designed as a spring 89, in particular a plate spring, through which a bearing 95 of the spindle nut 93 and thus (via the spindle 27) the closure element 11 is biased in the direction of the first end position G. The spring 89 is supported on the motor 25, which is axially fixed to the housing 59, so that ultimately the spindle nut 93 and the closure element 11 are also supported on the housing 59 via the spring 89 or the compensation element 87.

8A first shows a situation after the closure element 11 has been moved into the first end position G. In this position, the compensation element 87 is already elastically deformed and the spring 89 is compressed, so that the bearing 85 of the spindle nut 93 is supported by a stop 103 for the Bearing 95 is positioned remotely and the compensation element 87 exerts a bias on the closure element 11 directed in the direction of the flow opening 17.

If the housing 59 now experiences an expansion A, the force transmitted from the closure element 11 to the compensation element 87 is reduced, so that the spring 89 can unfold and the closure element 11 can track the expansion A (cf. 8B) . An example is in 8B a maximum expansion A to be compensated is shown, in which the bearing 95 rests against the stop 103 due to the unfolding of the spring 89.

Since the spring 89 is also in the in 8A illustrated situation is not fully compressed after reaching the first end position, the spring 89 can also be further compressed as a result of a shortening V of the housing 59, so that the closure element 11 can avoid the shortening V and jamming of the closure element 11 can be prevented. This is in 8C illustrated. Once again, both expansions A and contractions V of the housing 59 can be compensated mechanically by the elastically deformable compensation element 87.

The drive 23 is also based on 8A to 8C The illustrated valve 13 can in particular be controllable and the valve 13 can be connected to a control device 79 in order to be able to position the closure element 11 according to one of the methods explained above. In particular, such additional control-technical compensation of expansions A and contractions V can also make it possible to compensate for larger expansions A or larger contractions V by closing the closure element 11, for example by carrying out a compensation cycle R starting from the in 8B shown position can be transferred back into a position in which the bearing 95 of the spindle nut 93 is removed from the stop 103 (cf. 8A) , so that any subsequent expansions A can be compensated again mechanically by expanding the spring 89. Even in the event of complete compression of the spring 89 as a result of a shortening V of the housing 59, the original closing force C1 or a reduced closing force C2 can be adjusted by carrying out a compensation cycle R, so that the spring 89 unfolds again and mechanical compensation for further shortening V can be made possible.

In general, it should also be noted that when using an elastically deformable compensation element 87, the drive 23 or the motor 25 can be designed to be weaker - and therefore more cost-effective - than without a compensation element 87, since force peaks are avoided or at least reduced by the compensation element 87.

Based on the figures, only embodiments of valves 13 were explained above, in which an elastically deformable compensation element 87 is arranged in a force transmission path from the housing 59 to the closure element 11. However, this can also be done in an analogous manner with an ejector 15, for example that based on 2A and 2 B illustrated ejector 15, can be implemented.

6 shows schematically and by way of example a refrigeration or heating system 33 with a valve and/or ejector system 75, which has an ejector 15, two expansion valves 45 and a shut-off or control valve 46. In addition, a control device 79 is provided, which is designed to control respective drives for moving closure elements of the valves 45 and 46 and the ejector 15 via control lines 81 in accordance with the method explained above. The control device 79 can in particular be part of a control device which is intended to control the cooling or heating system 33 as a whole. Furthermore, the valves 45 and 46 and/or the ejector 15 can also be designed with an elastically deformable compensation element 87 in order to enable mechanical compensation of changes in length of a housing 59 of the valves 45 and 46 and/or the ejector 15, as explained above.

The illustrated refrigeration or heating system 33 includes a container 43 for collecting refrigerants, an evaporator 39, a compressor 41 and a condenser 37 and the refrigerant is passed through lines 47, with arrows indicating the flow direction of the refrigerant. Refrigerant supplied to the evaporator 39 via an expansion valve 45 from the container 43 can evaporate in the evaporator 39 and thereby remove heat from the environment, the evaporator 39 producing a mixture of gaseous and liquid refrigerant, which is sucked out by the ejector 15 via its suction connection 53 and can be brought to a higher pressure level. A gaseous portion of the refrigerant present in the container 43 can also be sucked in by the compressor 41 via the line 47 and fed to the liquefier 37, where the refrigerant is liquefied and sent to the container via a throttle valve 45 or via the shut-off or control valve 46 as a driving medium can be fed to the ejector 15. The shut-off or control valve 46 can also be used, for example in 2A and 2 B shown, be integrated into the ejector 15.

In order to adapt the operation of the refrigeration or heating system 33, the control device 79 can in particular be designed to control movements of closure elements 11 of the valves 45 and 46 and of the ejector 15 or their drives 23. Since, particularly in such heating or cooling systems 33, there can be relatively high temperature differences between individual sections of the system and the system can also be exposed to changing ambient temperatures, especially with valves 45, 46 or ejectors 15 that are used in such a system 33, the thermal stresses explained occur. Therefore, the control device 79 as part of the valve and/or ejector system 75 is set up to control the drives 23 of the ejector 15 or the valves 45 and 46 in order to carry out the explained method for positioning the closure elements 11 and to be able to compensate for any thermal stresses . In particular, the use of valve and/or ejector systems 75 can thus be provided in a refrigeration or heating system 33, with at least one valve 45 or 46 or an ejector 15 and a control device 79 being provided in such a valve and/or ejector system 75 can be in order to be able to position the respective closure element 11 according to the method explained here. In addition, such a refrigeration system can also be used in a refrigeration cabinet, for example a refrigerator. The valves 45 and 46 and/or the ejector 15 can also be designed with an elastically deformable compensation element 87 arranged in a force transmission path from a housing 59 to a closure element 11 in order to also enable mechanical compensation for thermally caused changes in length of the housing 59.

• Ausführungsform 1:
  • Verfahren zum Positionieren eines mittels eines Antriebs (23) zwischen einer ersten Endlage (G) und einer zweiten Endlage (O) bewegbaren Verschlusselements (11) eines Ventils (13) oder Ejektors (15),
  • wobei das Verschlusselement (11) eine Durchflussöffnung (17) des Ventils (13) oder Ejektors (15) in der ersten Endlage (G) gegen einen Durchfluss von Fluid oder Gas blockiert und die Durchflussöffnung (17) in der zweiten Endlage (O) für einen Durchfluss von Fluid oder Gas freigibt,
  • bei welchem:
    • - das Verschlusselement (11) in eine von der ersten Endlage (G) und der zweiten Endlage (O) bewegt wird und
    • - nach dem Bewegen des Verschlusselements (11) in die eine Endlage (G, O) ein Kompensationszyklus (R) durchgeführt wird,
  • wobei das Verschlusselement (11) während des Kompensationszyklus (R) zum Ausführen einer ersten Kompensationsbewegung (R1) in Richtung der anderen Endlage (O, G) und zum Ausführen einer zweiten Kompensationsbewegung (R2) in Richtung der einen Endlage (G, O) angesteuert wird.
• Ausführungsform 2:
  • Verfahren nach Ausführungsform 1,
  • wobei das Verschlusselement (11) translatorisch zwischen der ersten Endlage (G) und der zweiten Endlage (O) bewegbar ist.
• Ausführungsform 3:
  • Verfahren nach Ausführungsform 1 oder 2,
  • wobei das Verschlusselement (11) zunächst zum Ausführen der ersten Kompensationsbewegung (R1) und daraufhin zum Ausführen der zweiten Kompensationsbewegung (R2) angesteuert wird; oder umgekehrt.
• Ausführungsform 4:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei das Verschlusselement (11) zum Ausführen der ersten Kompensationsbewegung (R1) um eine erste Wegstrecke (W1) und zum Ausführen der zweiten Kompensationsbewegung (R2) um eine zweite Wegstrecke (W2) angesteuert wird,
  • wobei die zweite Wegstrecke (W2) größer ist als die erste Wegstrecke (W1).
• Ausführungsform 5:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei das Verschlusselement (11) schrittweise bewegbar ist und wobei das Verschlusselement (11) zum Ausführen der ersten Kompensationsbewegung (R1) um eine erste Anzahl von Schritten (S1) und zum Ausführen der zweiten Kompensationsbewegung (R2) um eine zweite Anzahl von Schritten (S2) angesteuert wird,
  • wobei die zweite Anzahl von Schritten (S2) größer ist als die erste Anzahl von Schritten (S1).
• Ausführungsform 6:
  • Verfahren nach Ausführungsform 5,
  • wobei die zweite Anzahl von Schritten (S2) um genau einen Schritt größer ist als die erste Anzahl von Schritten (S1).
• Ausführungsform 7:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei das Verschlusselement (11) zum Ausführen der ersten Kompensationsbewegung (R1) zu einer Bewegung um weniger als 50 Mikrometer, insbesondere um weniger als 20 Mikrometer, in Richtung der anderen Endlage (O, G) angesteuert wird.
• Ausführungsform 8:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei die angesteuerte erste Kompensationsbewegung (R1) durch eine elastische Verformung eines elastisch verformbaren Kompensationselements (87) kompensiert wird, welches in einem Kraftübertragungspfad von einem Gehäuse (59) des Ventils (13) oder des Ejektors (15) zu dem Verschlusselement (11) angeordnet ist.
• Ausführungsform 9:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei der Kompensationszyklus (R) nach einer vorgegebenen oder vorgebbaren Wartezeit (ΔT) nach dem Erreichen der einen Endlage (G, O) durchgeführt wird.
• Ausführungsform 10:
  • Verfahren nach Ausführungsform 9,
  • wobei die Wartezeit (ΔT) kleiner als 120 Sekunden ist, insbesondere kleiner als 60 Sekunden und/oder kleiner als 30 Sekunden; und/oder wobei die Wartezeit (ΔT) etwa 10 Sekunden beträgt.
• Ausführungsform 11:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei das Verschlusselement (11) in die erste Endlage (G) bewegt wird und wobei der Kompensationszyklus (R) nach dem Bewegen des Verschlusselements (11) in die erste Endlage (G) durchgeführt wird.
• Ausführungsform 12:
  • Verfahren nach Ausführungsform 11,
  • wobei der Durchfluss des Fluids oder Gases durch die Durchflussöffnung (17) durch Positionieren des Verschlusselements (11) innerhalb eines Sperrabschnitts (85) des Ventils (13) oder Ejektors (15) blockierbar ist, welcher durch die erste Endlage (G) und eine gegenüber der ersten Endlage (G) in Richtung der zweiten Endlage (O) versetzte Sperrstellung (B) begrenzt ist, wobei das Verschlusselement (11) durch das Ausführen der zweiten Kompensationsbewegung (R2) in Richtung der zweiten Endlage (O) lediglich innerhalb des Sperrabschnitts (85) bewegt wird.
• Ausführungsform 13:
  • Verfahren nach Ausführungsform 11 oder 12,
  • wobei die Durchflussöffnung (17) durch das Bewegen des Verschlusselements (11) in die erste Endlage (G) mit einer ersten Schließkraft (C1) verschlossen wird.
• Ausführungsform 14:
  • Verfahren nach Ausführungsform 13,
  • wobei die erste Schließkraft (C1) einer durch den Antrieb (23) auf das Verschlusselement (11) übertragbaren Kraft entspricht.
• Ausführungsform 15:
  • Verfahren nach Ausführungsform 13 oder 14,
  • wobei die Durchflussöffnung (17) durch das Ausführen der zweiten Kompensationsbewegung (R2) mit einer zweiten Schließkraft (C2) verschlossen wird,
  • wobei die zweite Schließkraft (C2) geringer ist als die erste Schließkraft (C1).
• Ausführungsform 16:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei der Antrieb (23) dazu angesteuert wird, das Verschlusselement (11) bei der zweiten Kompensationsbewegung (R2) mit einer geringeren Kraft als bei dem Bewegen in die eine Endlage (G, O) anzutreiben.
• Ausführungsform 17:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei die durch den Antrieb (23) auf das Verschlusselement (11) übertragbare Kraft einstellbar ist, insbesondere durch Einstellen eines Motorstroms (M1, M2, M3) eines Motors (25) des Antriebs (23).
• Ausführungsform 18:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei die von dem Antrieb (23) bei dem Bewegen in die eine Endlage (G, O) auf das Verschlusselement (11) übertragene Kraft vor einem erwarteten Erreichen der einen Endlage (G, O) reduziert wird.
• Ausführungsform 19:
  • Verfahren nach einer der vorhergehenden Ausführungsformen,
  • wobei der Antrieb dazu angesteuert wird, das Verschlusselements (11) bei der ersten Kompensationsbewegung (R1) mit einer größeren Kraft als bei der zweiten Kompensationsbewegung (R2) und/oder als bei dem Bewegen in die eine Endlage (G, O) anzutreiben.
• Ausführungsform 20:
  • Verfahren nach einer der vorhergehenden Ausführungsformen, wobei der Kompensationszyklus (R) zyklisch wiederholt wird.
• Ausführungsform 21:
  • Verfahren nach Ausführungsform 20,
  • wobei eine Zykluszeit (ΔT1) zwischen zwei aufeinanderfolgenden Durchführungen des Kompensationszyklus (R) konstant ist oder sukzessive zunimmt.
• Ausführungsform 22:
  • Verfahren nach Ausführungsform 20 oder 21,
  • wobei das zyklische Wiederholen des Kompensationszyklus (R) nach einem Durchführen einer vorgegebenen oder vorgebbaren maximalen Anzahl von aufeinanderfolgenden Kompensationszyklen (R) beendet wird.
• Ausführungsform 23:
  • Ventil (13) oder Ejektor (15),
  • umfassend
    • - ein zwischen einer ersten Endlage (G) und einer zweiten Endlage (O) bewegbares Verschlusselement (11), welches dazu ausgebildet ist, eine Durchflussöffnung (17) des Ventils (13) oder Ejektors (15) in der ersten Endlage (G) gegen einen Durchfluss von Fluid oder Gas zu blockieren und die Durchflussöffnung (17) in der zweiten Endlage (O) für einen Durchfluss von Fluid oder Gas freizugeben, und
    • - ein elastisch verformbares Kompensationselement (87), wobei das elastisch verformbare Kompensationselement (87) in einem Kraftübertragungspfad von einem Gehäuse (59) des Ventils (13) oder Ejektors (15) zu dem Verschlusselement (11) angeordnet ist.
• Ausführungsform 24:
  • Ventil (13) oder Ejektor (15) nach Ausführungsform 23,
  • wobei das Verschlusselement (15) über das Kompensationselement (87) an dem Gehäuse (59) abgestützt ist.
• Ausführungsform 25:
  • Ventil (13) oder Ejektor (15) nach Ausführungsform 23 oder 24,
  • wobei das Verschlusselement translatorisch zwischen der ersten Endlage (G) und der zweiten Endlage (O) bewegbar ist.
• Ausführungsform 26:
  • Ventil (13) oder Ejektor (15) nach einer der Ausführungsformen 23 bis 25, wobei das Verschlusselement (11) über das Kompensationselement (87) in Richtung der ersten Endlage (G) vorgespannt ist.
• Ausführungsform 27:
  • Ventil (13) oder Ejektor (15) nach einer der Ausführungsformen 23 bis 26, wobei das Kompensationselement (87) dazu ausgebildet ist, infolge einer Bewegung des Verschlusselements (11) in die erste Endlage (G) elastisch verformt zu werden.
• Ausführungsform 28:
  • Ventil (13) oder Ejektor (15) nach einer der Ausführungsformen 23 bis 27, wobei das Kompensationselement (87) durch eine auf das Verschlusselement (11) ausgeübte und in Richtung der zweiten Endlage (O) gerichtete Kraft elastisch verformbar ist, wenn das Verschlusselement (11) in der ersten Endlage (G) positioniert ist.
• Ausführungsform 29:
  • Ventil (13) oder Ejektor (15) nach einer der Ausführungsformen 23 bis 28, wobei das Kompensationselement (87) an dem Verschlusselement (11) oder einem gemeinsam mit dem Verschlusselement (11) translatorisch bewegbaren Verbindungsabschnitt angeordnet ist.
• Ausführungsform 30:
  • Ventil (13) oder Ejektor (15) nach einer der Ausführungsformen 23 bis 29, ferner umfassend einen Spindeltrieb (101) zum Antreiben des Verschlusselements (15), mit einer zu einer Drehbewegung antreibbaren Spindelmutter (93) oder Spindel (27),
  • wobei die Spindelmutter (93) oder Spindel (27), insbesondere über ein Lager (95), durch das Kompensationselement (87) an dem Gehäuse (59) abgestützt ist.
• Ausführungsform 31:
  • Ventil (13) oder Ejektor (15) nach Ausführungsform 30,
  • wobei die Spindelmutter (93) oder Spindel (27), insbesondere über ein Lager (95), durch das Kompensationselement (87) in Richtung der ersten Endlage (G) vorgespannt ist.
• Ausführungsform 32:
  • Ventil (13) oder Ejektor (15) nach Ausführungsform 30 oder 31,
  • wobei die Spindelmutter (93) oder Spindel (27) und eine Antriebswelle (99) starr miteinander verbunden sind und die Antriebswelle (99) relativ zu einem zugeordneten Antrieb (23) axial beweglich ist; oder
  • wobei die Spindelmutter (93) oder Spindel (27) und eine Antriebswelle (99) drehfest, jedoch relativ zueinander axial verschieblich miteinander verbunden sind.
• Ausführungsform 33:
  • Ventil (13) oder Ejektor (15) nach einer der Ausführungsformen 23 bis 32,
  • wobei das Kompensationselement (87) als eine Feder (89), insbesondere eine Tellerfeder, ausgebildet ist.
• Ausführungsform 34:
  • Ventil- und/oder Ejektorsystem (75),
  • umfassend:
    • - zumindest ein Ventil (13) und/oder zumindest einen Ejektor (15),
    • - ein zwischen einer ersten Endlage (G) und einer zweiten Endlage (O) bewegbares Verschlusselement (11), welches dazu ausgebildet ist, eine Durchflussöffnung (17) des Ventils (13) oder Ejektors (15) in der ersten Endlage (G) gegen einen Durchfluss von Fluid oder Gas zu blockieren und die Durchflussöffnung (17) in der zweiten Endlage (O) für einen Durchfluss von Fluid oder Gas freizugeben;
    • - einen Antrieb (23) zum Bewegen des Verschlusselements (11); und
    • - eine Steuereinrichtung (79), welche dazu eingerichtet ist, das Verschlusselement (11) gemäß einem Verfahren nach einer der Ausführungsformen 1 bis 22 zu positionieren.
• Ausführungsform 35:
  • Ventil- und/oder Ejektorsystem (75) nach Ausführungsform 34, wobei der Antrieb (23) einen Schrittmotor (25) umfasst.
• Ausführungsform 36:
  • Ventil- und/oder Ejektorsystem (75) nach Ausführungsform 34 oder 35, wobei das Verschlusselement (11) als Ventilnadel (31) ausgebildet ist.
• Ausführungsform 37:
  • Ventil- und/oder Ejektorsystem (75) nach einer der Ausführungsformen 34 bis 36,
  • wobei das zumindest eine Ventil (13) und/oder der zumindest eine Ejektor (15) nach einer der Ausführungsformen 23 bis 33 ausgebildet sind/ist.
• Ausführungsform 38:
  • Kälteanlage (33), Wärmeanlage (33) oder Kühlmöbel mit einem Ventil- und/oder Ejektorsystem (75) nach einer der Ausführungsformen 34 bis 37 und/oder mit einem Ventil (13) und/oder einem Ejektor (15) nach einer der Ausführungsformen 23 bis 33.
• Ausführungsform 39:
  • Verwendung eines Ventil- und/oder Ejektorsystems (75) nach einer der Ausführungsformen 34 bis 37 und/oder eines Ventils (13) und/oder eines Ejektors (15) nach einer der Ausführungsformen 23 bis 33 in einer Kälteanlage (33), in einer Wärmeanlage (33) oder in einem Kühlmöbel.

Finally, various embodiments of the invention are summarized again as follows, with reference to the above-mentioned elements in brackets by way of example - but not restrictively:

• Embodiment 1:
  • Method for positioning a closure element (11) of a valve (13) or ejector (15) which can be moved by means of a drive (23) between a first end position (G) and a second end position (O),
  • wherein the closure element (11) blocks a flow opening (17) of the valve (13) or ejector (15) in the first end position (G) against a flow of fluid or gas and the flow opening (17) in the second end position (O) for releases a flow of fluid or gas,
  • in which:
    • - the closure element (11) is moved into one of the first end position (G) and the second end position (O) and
    • - after moving the closure element (11) into one end position (G, O), a compensation cycle (R) is carried out,
  • wherein the closure element (11) is controlled during the compensation cycle (R) to carry out a first compensation movement (R1) in the direction of the other end position (O, G) and to carry out a second compensation movement (R2) in the direction of one end position (G, O). becomes.
• Embodiment 2:
  • Method according to embodiment 1,
  • wherein the closure element (11) is translationally movable between the first end position (G) and the second end position (O).
• Embodiment 3:
  • Method according to embodiment 1 or 2,
  • wherein the closure element (11) is first controlled to carry out the first compensation movement (R1) and then to carry out the second compensation movement (R2); or the other way around.
• Embodiment 4:
  • Method according to one of the preceding embodiments,
  • wherein the closure element (11) is controlled to carry out the first compensation movement (R1) by a first distance (W1) and to carry out the second compensation movement (R2) by a second distance (W2),
  • where the second distance (W2) is greater than the first distance (W1).
• Embodiment 5:
  • Method according to one of the preceding embodiments,
  • wherein the closure element (11) can be moved step by step and wherein the closure element (11) is used to carry out the first compensation movement (R1) by a first number of steps (S1) and for carrying out the second compensation movement (R2) by a second number of steps (S2 ) is controlled,
  • where the second number of steps (S2) is greater than the first number of steps (S1).
• Embodiment 6:
  • Method according to embodiment 5,
  • where the second number of steps (S2) is exactly one step larger than the first number of steps (S1).
• Embodiment 7:
  • Method according to one of the preceding embodiments,
  • wherein the closure element (11) is controlled to move by less than 50 micrometers, in particular by less than 20 micrometers, in the direction of the other end position (O, G) in order to carry out the first compensation movement (R1).
• Embodiment 8:
  • Method according to one of the preceding embodiments,
  • wherein the controlled first compensation movement (R1) is compensated for by an elastic deformation of an elastically deformable compensation element (87), which is arranged in a force transmission path from a housing (59) of the valve (13) or the ejector (15) to the closure element (11). is.
• Embodiment 9:
  • Method according to one of the preceding embodiments,
  • wherein the compensation cycle (R) is carried out after a predetermined or predeterminable waiting time (ΔT) after reaching one end position (G, O).
• Embodiment 10:
  • Method according to embodiment 9,
  • wherein the waiting time (ΔT) is less than 120 seconds, in particular less than 60 seconds and/or less than 30 seconds; and/or wherein the waiting time (ΔT) is approximately 10 seconds.
• Embodiment 11:
  • Method according to one of the preceding embodiments,
  • wherein the closure element (11) is moved into the first end position (G) and wherein the compensation cycle (R) is carried out after moving the closure element (11) into the first end position (G).
• Embodiment 12:
  • Method according to embodiment 11,
  • wherein the flow of the fluid or gas through the flow opening (17) can be blocked by positioning the closure element (11) within a blocking section (85) of the valve (13) or ejector (15), which is through the first end position (G) and one opposite the first end position (G) is limited in the direction of the second end position (O) offset blocking position (B), the closure element (11) being carried out by executing the second compensation movement (R2) in the direction of the second end position (O) only within the blocking section ( 85) is moved.
• Embodiment 13:
  • Method according to embodiment 11 or 12,
  • wherein the flow opening (17) is closed by moving the closure element (11) into the first end position (G) with a first closing force (C1).
• Embodiment 14:
  • Method according to embodiment 13,
  • wherein the first closing force (C1) corresponds to a force that can be transmitted to the closure element (11) by the drive (23).
• Embodiment 15:
  • Method according to embodiment 13 or 14,
  • wherein the flow opening (17) is closed with a second closing force (C2) by executing the second compensation movement (R2),
  • wherein the second closing force (C2) is less than the first closing force (C1).
• Embodiment 16:
  • Method according to one of the preceding embodiments,
  • wherein the drive (23) is controlled to drive the closure element (11) with a lower force during the second compensation movement (R2) than when moving into one end position (G, O).
• Embodiment 17:
  • Method according to one of the preceding embodiments,
  • wherein the force that can be transmitted to the closure element (11) by the drive (23) can be adjusted, in particular by adjusting a motor current (M1, M2, M3) of a motor (25) of the drive (23).
• Embodiment 18:
  • Method according to one of the preceding embodiments,
  • wherein the force transmitted by the drive (23) to the closure element (11) when moving into one end position (G, O) is reduced before the one end position (G, O) is expected to be reached.
• Embodiment 19:
  • Method according to one of the preceding embodiments,
  • wherein the drive is controlled to drive the closure element (11) during the first compensation movement (R1) with a greater force than during the second compensation movement (R2) and / or than when moving into one end position (G, O).
• Embodiment 20:
  • Method according to one of the preceding embodiments, wherein the compensation cycle (R) is repeated cyclically.
• Embodiment 21:
  • Method according to embodiment 20,
  • where a cycle time (ΔT1) between two successive executions of the compensation cycle (R) is constant or increases successively.
• Embodiment 22:
  • Method according to embodiment 20 or 21,
  • wherein the cyclic repetition of the compensation cycle (R) is ended after a predetermined or predeterminable maximum number of consecutive compensation cycles (R) has been carried out.
• Embodiment 23:
  • Valve (13) or ejector (15),
  • full
    • - A closure element (11) which is movable between a first end position (G) and a second end position (O) and which is designed to counteract a flow opening (17) of the valve (13) or ejector (15) in the first end position (G). to block a flow of fluid or gas and to release the flow opening (17) in the second end position (O) for a flow of fluid or gas, and
    • - an elastically deformable compensation element (87), wherein the elastically deformable compensation element (87) is arranged in a force transmission path from a housing (59) of the valve (13) or ejector (15) to the closure element (11).
• Embodiment 24:
  • Valve (13) or ejector (15) according to embodiment 23,
  • wherein the closure element (15) is supported on the housing (59) via the compensation element (87).
• Embodiment 25:
  • Valve (13) or ejector (15) according to embodiment 23 or 24,
  • wherein the closure element is translationally movable between the first end position (G) and the second end position (O).
• Embodiment 26:
  • Valve (13) or ejector (15) according to one of embodiments 23 to 25, wherein the closure element (11) is biased towards the first end position (G) via the compensation element (87).
• Embodiment 27:
  • Valve (13) or ejector (15) according to one of embodiments 23 to 26, wherein the compensation element (87) is designed to be elastically deformed as a result of a movement of the closure element (11) into the first end position (G).
• Embodiment 28:
  • Valve (13) or ejector (15) according to one of embodiments 23 to 27, wherein the compensation element (87) is elastically deformable by a force exerted on the closure element (11) and directed in the direction of the second end position (O) when the closure element (11) is positioned in the first end position (G).
• Embodiment 29:
  • Valve (13) or ejector (15) according to one of embodiments 23 to 28, wherein the compensation element (87) is arranged on the closure element (11) or on a connecting section which can be moved in translation together with the closure element (11).
• Embodiment 30:
  • Valve (13) or ejector (15) according to one of embodiments 23 to 29, further comprising a spindle drive (101) for driving the closure element (15), with a spindle nut (93) or spindle (27) which can be driven to rotate,
  • wherein the spindle nut (93) or spindle (27), in particular via a bearing (95), is supported on the housing (59) by the compensation element (87).
• Embodiment 31:
  • Valve (13) or ejector (15) according to embodiment 30,
  • wherein the spindle nut (93) or spindle (27), in particular via a bearing (95), is biased by the compensation element (87) in the direction of the first end position (G).
• Embodiment 32:
  • Valve (13) or ejector (15) according to embodiment 30 or 31,
  • wherein the spindle nut (93) or spindle (27) and a drive shaft (99) are rigidly connected to one another and the drive shaft (99) is axially movable relative to an associated drive (23); or
  • wherein the spindle nut (93) or spindle (27) and a drive shaft (99) are connected to one another in a rotationally fixed manner, but are axially displaceable relative to one another.
• Embodiment 33:
  • Valve (13) or ejector (15) according to one of embodiments 23 to 32,
  • wherein the compensation element (87) is designed as a spring (89), in particular a plate spring.
• Embodiment 34:
  • Valve and/or ejector system (75),
  • full:
    • - at least one valve (13) and/or at least one ejector (15),
    • - A closure element (11) which is movable between a first end position (G) and a second end position (O) and which is designed to counteract a flow opening (17) of the valve (13) or ejector (15) in the first end position (G). to block a flow of fluid or gas and to release the flow opening (17) in the second end position (O) for a flow of fluid or gas;
    • - a drive (23) for moving the closure element (11); and
    • - A control device (79), which is set up to position the closure element (11) according to a method according to one of embodiments 1 to 22.
• Embodiment 35:
  • Valve and/or ejector system (75) according to embodiment 34, wherein the drive (23) comprises a stepper motor (25).
• Embodiment 36:
  • Valve and/or ejector system (75) according to embodiment 34 or 35, wherein the closure element (11) is designed as a valve needle (31).
• Embodiment 37:
  • Valve and/or ejector system (75) according to one of embodiments 34 to 36,
  • wherein the at least one valve (13) and/or the at least one ejector (15) are designed according to one of embodiments 23 to 33.
• Embodiment 38:
  • Refrigeration system (33), heating system (33) or refrigeration cabinet with a valve and/or ejector system (75) according to one of embodiments 34 to 37 and/or with a valve (13) and/or an ejector (15) according to one of the embodiments 23 to 33.
• Embodiment 39:
  • Use of a valve and/or ejector system (75) according to one of embodiments 34 to 37 and/or a valve (13) and/or an ejector (15) according to one of embodiments 23 to 33 in a refrigeration system (33), in a Heating system (33) or in a refrigerator.

Reference symbol list

11

Closure element

13

Valve

15

ejector

17

Flow opening

19

Exit opening

21

Suction opening

23

drive

25

engine

27

spindle

29

appendage

31

Valve needle

33

Refrigeration system/heating system

35

compressor

37

liquefier

39

Evaporator

41

compressor

43

container

45

Expansion valve

46

Shut-off or control valve

47

Line

49

Drive connection

51

Propulsion nozzle

53

Suction connection

55

Entrance

57

Exit

59

Housing

61

Procedural step

63

Procedural step

65

Procedural step

67

Procedural step

69

Procedural step

71

Check

73

Check

75

Valve system

79

Control device

81

Control line

83

Limitation

84

conical surface

85

Barrier section

86

Inner surface

87

Compensation element

89

Feather

91

inner thread

93

spindle nut

95

camp

99

drive shaft

101

Spindle drive

103

attack

A

expansion

b

Blocking position

C1

first closing force

C2

second closing force

E

Input current

F

Output current

G

first end position

K

Tension

M1

first motor current

M2

second motor current

M3

third motor current

O

second end position

R

Compensation cycle

R1

first compensation movement

R2

second compensation movement

S1

first number of steps

S2

second number of steps

T

motive power

U

suction flow

v

Shortening

W1

first route

W2

second route

Z

Intermediate position

ΔT

waiting period

ΔT1

Cycle time

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102016123277 A1 [0111]

Claims (21)

Method for positioning a closure element (11) of a valve (13) or ejector (15) which can be moved by means of a drive (23) between a first end position (G) and a second end position (O), wherein the closure element (11) has a flow opening (17 ) of the valve (13) or ejector (15) in the first end position (G) blocks against a flow of fluid or gas and opens the flow opening (17) in the second end position (O) for a flow of fluid or gas, in which: - the closure element (11) is moved into one of the first end position (G) and the second end position (O) and - after moving the closure element (11) into one end position (G, O), a compensation cycle (R) is carried out, wherein the closure element (11) is controlled during the compensation cycle (R) to carry out a first compensation movement (R1) in the direction of the other end position (O, G) and to carry out a second compensation movement (R2) in the direction of one end position (G, O). becomes. Procedure according to Claim 1 , wherein the closure element (11) is first controlled to carry out the first compensation movement (R1) and then to carry out the second compensation movement (R2); or the other way around. Procedure according to Claim 1 or 2 , wherein the closure element (11) is controlled to carry out the first compensation movement (R1) by a first distance (W1) and to carry out the second compensation movement (R2) by a second distance (W2), the second distance (W2) being larger as the first route (W1). Method according to one of the preceding claims, wherein the closure element (11) can be moved step by step and wherein the closure element (11) is used to carry out the first compensation movement (R1) by a first number of steps (S1) and for carrying out the second compensation movement (R2) by a second number of steps (S2 ) is controlled, where the second number of steps (S2) is greater than the first number of steps (S1). Method according to one of the preceding claims, wherein the controlled first compensation movement (R1) is compensated for by an elastic deformation of an elastically deformable compensation element (87) which is in a force transmission path from a housing (59) of the valve (13) or the ejector (15). to the closure element (11) is arranged. Method according to one of the preceding claims, wherein the compensation cycle (R) is carried out after a predetermined or predeterminable waiting time (ΔT) after reaching one end position (G, O). Method according to one of the preceding claims, wherein the closure element (11) is moved into the first end position (G) and wherein the compensation cycle (R) is carried out after moving the closure element (11) into the first end position (G). Procedure according to Claim 7 , wherein the flow of the fluid or gas through the flow opening (17) can be blocked by positioning the closure element (11) within a blocking section (85) of the valve (13) or ejector (15), which is through the first end position (G) and a The locking position (B) offset from the first end position (G) in the direction of the second end position (O) is limited, the closure element (11) only being within the locking section by executing the second compensation movement (R2) in the direction of the second end position (O). (85) is moved. Procedure according to Claim 7 or 8th , wherein the flow opening (17) is closed by moving the closure element (11) into the first end position (G) with a first closing force (C1), wherein the flow opening (17) is closed by executing the second compensation movement (R2) with a second Closing force (C2) is closed, the second closing force (C2) being less than the first closing force (C1). Method according to one of the preceding claims, wherein the drive (23) is controlled to drive the closure element (11) during the second compensation movement (R2) with a lower force than when moving into one end position (G, O); and or wherein the force transmitted by the drive (23) to the closure element (11) when moving into one end position (G, O) is reduced before the one end position (G, O) is expected to be reached; and or wherein the drive is controlled to drive the closure element (11) during the first compensation movement (R1) with a greater force than during the second compensation movement (R2) and / or than when moving into one end position (G, O). Method according to one of the preceding claims, wherein the compensation cycle (R) is repeated cyclically, a cycle time (ΔT1) between two successive implementations of the compensation cycle (R) being in particular constant or successively increasing. Valve (13) or ejector (15), comprising - A closure element (11) which is movable between a first end position (G) and a second end position (O) and which is designed to counteract a flow opening (17) of the valve (13) or ejector (15) in the first end position (G). to block a flow of fluid or gas and to release the flow opening (17) in the second end position (O) for a flow of fluid or gas, and - an elastically deformable compensation element (87), wherein the elastically deformable compensation element (87) is arranged in a force transmission path from a housing (59) of the valve (13) or ejector (15) to the closure element (11). Valve (13) or ejector (15). Claim 12 , wherein the closure element (15) is supported on the housing (59) via the compensation element (87); and/or wherein the closure element is translationally movable between the first end position (G) and the second end position (O). Valve (13) or ejector (15). Claim 12 or 13 , wherein the closure element (11) is biased towards the first end position (G) via the compensation element (87). Valve (13) or ejector (15) according to one of the Claims 12 until 14 , wherein the compensation element (87) is designed to be elastically deformed as a result of a movement of the closure element (11) into the first end position (G); and/or wherein the compensation element (87) is elastically deformable by a force exerted on the closure element (11) and directed in the direction of the second end position (O) when the closure element (11) is positioned in the first end position (G). Valve (13) or ejector (15) according to one of the Claims 12 until 15 , wherein the compensation element (87) is arranged on the closure element (11) or on a connecting section which can be moved in translation together with the closure element (11). Valve (13) or ejector (15) according to one of the Claims 12 until 16 , further comprising a spindle drive (101) for driving the closure element (15), with a spindle nut (93) or spindle (27) which can be driven to a rotary movement and which, in particular via a bearing (95), through the compensation element (87) on the Housing (59) is supported. Valve (13) or ejector (15) according to one of the Claims 12 until 17 , wherein the compensation element (87) is designed as a spring (89), in particular a plate spring. Valve and/or ejector system (75), comprising: - at least one valve (13) and/or at least one ejector (15), - a closure element (11) movable between a first end position (G) and a second end position (O). , which is designed to block a flow opening (17) of the valve (13) or ejector (15) in the first end position (G) against a flow of fluid or gas and the flow opening (17) in the second end position (O) to allow for a flow of fluid or gas; - a drive (23) for moving the closure element (11); and - a control device (79) which is set up to control the closure element (11) according to a method according to one of Claims 1 until 11 to position, wherein the at least one valve (13) and / or the at least one ejector (15) in particular according to one of Claims 12 until 18 are/is trained. Valve and/or ejector system (75). Claim 19 , wherein the drive (23) comprises a stepper motor (25). Refrigeration system (33), heating system (33) or refrigeration cabinet with a valve and/or ejector system (75). Claim 19 or 20 and/or with a valve (13) and/or an ejector (15) according to one of Claims 12 until 18 .

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