DE102010001321A1 - Refrigerant circuit for combustion engine of car, has closure element resilient in relation to section fixed relative to conductor, where supplementary units are provided for depressive curve of resilient bias force - Google Patents

Abstract

The refrigerant circuit (1) has a closure element resilient in relation to a section fixed relative to conductor (130). The supplementary units are provided for a depressive curve of resilient bias force over aperture way of the closure element. A flow body is arranged at the closure element.

Description

The invention relates to a coolant circuit for an internal combustion engine of a vehicle according to the preamble of claim 1.

Such a coolant circuit has a supply line and a thermostat valve arranged in or on the supply line for controlling a coolant flow through the supply line. Here, the thermostatic valve for controlling the refrigerant flow may occupy a closed state in which no refrigerant flow flows through the supply line, and an opened state in which a refrigerant flow flows through the supply line, and is changeable between these states. In this way, a thermostatic valve can reverse the flow of coolant by the coolant flow when the thermostat valve is closed, for example, by a first circuit and when the thermostatic valve is open through a second circuit (and possibly also through the first circuit).

The thermostatic valve may be designed so that it may also assume intermediate positions and thus also be partially open, in order to regulate the volume flow of the coolant flow through the thermostatic valve in this way. It is also conceivable that the thermostatic valve can only be switched between an open and a closed state.

Thermostatic valves are conventionally used for temperature-dependent control of fluid circuits in internal combustion engines. Differently designed thermostatic valves control, for example, the temperature of the coolant or the engine and transmission oil. For example, a thermostatic valve may be part of a coolant circuit and regulates depending on the temperature of coolant flows, whether coolant exclusively by a radiator (in the context of a so-called small coolant circuit for delivering heat to a vehicle interior heating) or additionally by a coolant radiator (in such a said large coolant circuit for additional cooling of the coolant) is passed.

Conventional thermostatic valves are temperature-controlled. Known from the DE 35 02 817 A1 and the DE 38 17 952 A1 are, for example, so-called Dehnstoffthermostate (also known as wax thermostats), in which a pressure-resistant housing is filled with an expansion material, for example in the form of a wax. After starting an internal combustion engine to be cooled, the coolant heats up and the wax liquefies at a given temperature. The expansion material expands and acts on a working piston, which is pressed out of the housing and opens a coolant flow, so that a coolant flow can flow. If the temperature of the coolant falls below the predetermined opening temperature during further operation, then the coolant flow is in turn closed, so that no coolant flow can flow anymore.

In modern expansion thermostats can be realized in this way a control range from 0 ° C to 120 ° C.

A further development of such conventional Dehnstoffthermostate represent heated Dehnstoffthermostate, as for example from the DE 103 60 169 A1 are known. By electrically heating a Dehnstoffs at a Dehnstoffthermostat the working range of a thermostatic valve can be extended by the electric heating, for example, an early opening of the thermostatic valve and thus the coolant circuit is achieved in particular in situations with greatly increased power requirement.

Also known are purely electrically driven thermostats using an electric drive motor for adjusting the thermostatic valve.

The well-known thermostatic valves, in particular the frequently used Dehnstoffthermostaten has in common that opening and closing of the thermostatic valves in response to fixed set temperatures in predetermined temperature ranges, in order to keep the temperature of a combustion engine to be cooled largely constant. The limits of the temperatures, as a function of which a thermostatic valve opens or closes, are fixed; Pre and post-run effects in coolant circuits can only be considered insufficiently.

In addition, thermostatic valves regularly represent a high flow resistance in the coolant circuit and thus also require high-performance coolant pumps in the coolant circuit.

Object of the present invention is to provide a coolant circuit for an internal combustion engine of a vehicle with a thermostatic valve available, which is streamlined and thus allows a reduction of the flow resistance in the coolant circuit and also in particular in cooperation with an electrically operated coolant pump in a wide operating range adjustable is.

This object is achieved by an article having the features of claim 1.

It is provided that the thermostatic valve is pressure controlled by the thermostatic valve is controlled in response to the pressure of the refrigerant flow in the lead to the closed state and the open state.

In departure from conventional thermostatic valves, in particular in departure from so-called Dehnstoffthermostaten, the presently provided thermostatic valve used as a control variable, the pressure of the coolant flow in a supply line, but not (or only indirectly) the temperature of the coolant. The thermostatic valve is thus pressure-controlled and not (or only indirectly) temperature-controlled. This makes it possible to control the thermostatic valve by controlling a coolant pump and setting the pressure of the coolant flow thereacross, so that the thermostatic valve can be directly controlled via the coolant pump.

The thermostatic valve may have a closure element for closing the supply line in the closed state, wherein the closure element for transferring into the open state of the thermostatic valve is pivotable about a pivot axis or slidable along a sliding guide. By means of the closure element, the volume flow of the coolant is thus adjusted and regulated, wherein when the closure element is closed, no coolant flow flows, with a partially or fully opened closure element, however, a coolant flow flows through the supply line. In its closed position, the closure element bears against a seal, for example, thereby preventing a passage of coolant, while the thermostatic valve is opened by pivoting or pushing the closure element in response to the pressure of the coolant flow and thus the passage for the coolant is fully or partially released.

The closure element may be designed, for example, in the manner of a flap and is pivotably articulated about a pivot axis for this purpose. It is also conceivable to perform the closure element in the manner of a slider along a sliding guide displaceable, so that when a certain pressure is exceeded, the thermostatic valve is released. Regardless of the specific embodiment, the closure element is designed so that it is adjusted in response to the pressure of the coolant flow in the supply line for closing or releasing the thermostatic valve.

To specify a limit pressure, when the thermostat valve is opened, the closure element is advantageously resiliently biased against a fixed relative to the lead portion in the direction of its closed position.

For this purpose, for example, an elastic spring can be provided, which biases the pivotable or displaceable closure element in the direction of its closed position. The elastic spring acts, for example, as a compression spring between the closure element and a wall or other fixed portion of the supply line, so that for opening the thermostatic valve initially the biasing force of the elastic spring must be overcome and only after overcoming this biasing force, the thermostatic valve can be opened.

Advantageously, the example provided on the elastic spring provided elastic biasing force is degressive over the opening path of the closure element pretend. By degressive is to be understood in this context that the spring force does not increase proportionally with the opening path, but behaves disproportionately with the opening path. In other words, the slope of the spring characteristic decreases with increasing opening travel. Conceivable in this context, for example, that the spring characteristic assumes a negative slope with increasing opening path, so that the biasing spring force even decreases with increasing opening path.

By such a degressive elastic biasing force is achieved that for the initial opening of the thermostatic valve, a comparatively large pressure is required (corresponding to the predetermined limit pressure), the further opening of the thermostatic valve but not proportional to the pressure increase, but less than proportional. In this way it can be achieved that when the predetermined limit pressure is exceeded, the closure element snaps, so to speak, d. h., That the thermostatic valve does not open slowly, but even with little further pressure increase moves in a fast, abrupt manner in its fully open position.

The specification of such a degressive characteristic of the elastic biasing force can be achieved, for example, by providing additional means for influencing the spring characteristic.

In a first embodiment, these additional means may be formed by a flow body arranged on the closure element for generating a force on the closure element in the direction of its open position. Such a flow body can in cross section For example, resemble the shape of an aircraft wing and, utilizing the well-known from the fluid mechanics law of Bernoulli, generate a force in the direction of opening when the closure member is controlled by the pressure of the coolant flow is pivoted to its open position.

In another embodiment, the additional means may be formed by a magnet arranged on a flow body of the supply line, which attractively faces an armature of the closure element for generating a force on the closure element in the direction of its open position. The degressive characteristic of the elastic biasing force is thereby generated by the fact that with the opening of the closure element, the armature and the magnet are approached to each other, so that the magnetic attraction increases with the opening path and supports the opening of the closure element. In this way, it is possible that for the initial opening of the closure element, a comparatively large pressure force of the coolant flow is required, but with further increase in pressure, the closure element is then transferred in a comparatively quick manner in its fully open position.

In yet another embodiment, the additional means may be formed by a arranged on the supply line or a flow body of the supply membrane, which is acted upon by a flowing through the supply line coolant flow with a negative pressure for generating a force on the closure element in the direction of its open position. Background of this embodiment is again the law of Bernoulli from the fluid mechanics: Due to the flowing coolant flow in a subspace a negative pressure is generated, which is transmitted via the membrane to the closure element to support the opening movement of the closure element. The negative pressure increases with increasing coolant flow, so that with increasing opening of the thermostatic valve and concomitant increase in the coolant flow and acting on the closure element to support the opening movement force of the negative pressure increases to provide the degressive characteristic.

In yet another embodiment, the additional means is realized by a toggle which holds the closure element in its closed position in an initial position and can be actuated by the action of a coolant flow via a control piece for the activation of the closure element. The idea here is that a control piece is initially acted upon in the manner of a pilot valve exclusively with the pressure of the coolant flow and the control piece acts to release the closure element and the closure element biasing elastic spring on the toggle lever. If the toggle lever is released, the closure element can be moved, thereby compressing an elastic spring formed, for example, as a compression spring, wherein this elastic spring can be designed with a comparatively soft spring constant, so that after the initial movement of the control piece, the further movement of the closure element becomes simpler Way can be done to fully open the closure element.

In yet another embodiment, the additional means is formed by a power spring, which is stretched under the influence of the flow of coolant by the closure element is set in a rotational movement. In such an embodiment, for example, the closure member may be biased comparatively hard for initial opening so that a relatively large compressive force is required to initially open the closure member. If the closure element is opened by a predetermined distance, a flow of coolant can flow past the closure element and, for example via a vane arrangement on the closure element, set the closure element in a rotational movement, which allows a further opening of the closure element in a rapid manner, for example via a threaded connection. By the rotational movement of a mainspring is tensioned, which causes a downward rotation of the closure element and thus closing the thermostatic valve with decreasing pressure of the coolant flow.

In an advantageous embodiment, the coolant circuit has an electrically operated, independent of the internal combustion engine controllable coolant pump. The background here is that conventionally a coolant pump is coupled for control with an internal combustion engine to be controlled directly in dependence on the operating state of the internal combustion engine. With an electrically operated coolant pump, however, it is possible to carry out the control of the coolant pump completely independently of the internal combustion engine, wherein, for example, an engine load and / or a vehicle speed can be included as control variables of the coolant pump.

Via the electric coolant pump, the pressure of the coolant flow is adjusted to control the thermostatic valve. Thus, regardless of the temperature of the coolant, the thermostatic valve can be controlled by the choice of pump speed to open the thermostatic valve to release a coolant circuit or to close a circuit. For example, can be provided at high outside temperature or to specify the pump speed of the coolant pump in a desired manner during a highway drive of a vehicle and to control the thermostatic valve, wherein any number of parameters or maps of a vehicle and an internal combustion engine or other suitable parameters, such as the outside temperature, can be included for control.

The coolant circuit preferably has a first circuit and a second circuit, wherein when the thermostatic valve is closed, a coolant flow flows exclusively through the first circuit and, when the thermostat valve is fully or partially opened, a coolant flow flows both through the first circuit and through the second circuit. The first circuit may be formed, for example, with a heating radiator for emitting heat to a vehicle interior heating and provide a comparatively low cooling capacity available. On the other hand, the second circuit may include a radiator for cooling the coolant and provide a larger cooling capacity than the first circuit. When starting a vehicle, in which usually the internal combustion engine has a low operating temperature, for example, so only the first circuit can be operated and for this purpose the thermostatic valve to be closed. During prolonged operation of the vehicle and correspondingly increasing temperature of the internal combustion engine, the thermostatic valve can be fully or partially opened by controlling the coolant pump, so that a coolant flow also flows through the second circuit and the coolant is cooled in a suitable manner and the temperature of the internal combustion engine is controlled.

The idea underlying the invention will be explained in more detail with reference to the embodiments illustrated in the figures. Show it:

1 a schematic representation of a coolant circuit with a first circuit comprising a heating radiator and with a second circuit comprising a radiator for cooling the coolant;

2 a schematic, perspective view of a first embodiment of a pressure-controlled thermostatic valve;

3 a schematic view of a second embodiment of a pressure-controlled thermostatic valve;

4 a schematic view of a third embodiment of a pressure-controlled thermostatic valve;

5 a schematic view of a fourth embodiment of a pressure-controlled thermostatic valve;

6 a schematic view of a fifth embodiment of a pressure-controlled thermostatic valve;

7 a schematic view of a sixth embodiment of a pressure-controlled thermostatic valve;

8th a schematic view of a seventh embodiment of a pressure-controlled thermostatic valve and

9 a schematic view of an eighth embodiment of a pressure-controlled thermostatic valve.

1 shows first in a schematic overview representation of a circuit diagram of a coolant circuit 1 for cooling and controlling the temperature of an internal combustion engine 10 , The coolant circuit 1 has a first circuit K1 with a heating radiator 12 and a second circuit K2 with a radiator 13 for cooling a coolant. In supply lines 110 . 120 . 130 In the form of pipes or hoses coolant is conveyed and by a coolant pump 11 set in motion, allowing the coolant through the supply lines 110 . 120 and, depending on the position of a thermostatic valve 2 , also through the supply line 130 flows. Accordingly, coolant flows S, S1, S2 flow through the supply lines 110 . 120 . 130 ,

Different embodiments of a pressure-controlled thermostatic valve 2 are in 2 to 9 illustrated, wherein the different embodiments in their basic operation are similar in that a closure element 200A - 200H is biased in an elastic manner and pressure controlled to open or close the thermostatic valve 2 is adjusted. In the embodiments, in each case a degressive characteristic of this elastic biasing force is provided by the opening movement of the respective closure element with different means 200A - 200H being affected.

The embodiments will be described below in detail with reference to the figures. Individual, in their function corresponding components of the embodiments are, where appropriate, provided with the same reference numerals, however, each provided with trailing letters ("A", "B", "C" and s. W.) To identify the individual embodiments.

In the first embodiment of a thermostatic valve 2 according to 2 is on the supply line 130 after branching off the supply line 120 from the supply line 110 (see also 1 ) the thermostatic valve 2 arranged and has a about a pivot axis 202A swiveling closure element 200A on. In the in 2 shown closed position is the closure element 200A on a seal 205A and thus seals the passage through the supply line 130 so that no coolant flow through the supply line 130 can flow.

The closure element 200A is over an elastic spring 204A biased towards the closed position. The feather 204A is designed as a compression spring and has to pivot the closure element 200A around the pivot axis 202A to open the thermostatic valve 2 be compressed. For opening the closure element 200A Therefore, a predetermined spring force must be overcome.

The elastic bias is such that by the elastic spring 204A the closure element 200A held in the closed position until the pressure of the refrigerant flow S in the supply line 110 (and thus also in the supply line 130 ) exceeds a predetermined limit. Only when the pressure force of the coolant flow S is sufficiently large, the spring force of the spring 204A to overcome, the closure element 200A adjusted.

On the closure element 200A is a flow body 201A arranged, which resembles in cross section in its shape a wing of an aircraft. This flow body 201A is over jetties 203A with the closure element 200A connected and serves, when opening the closure element 200A a force supporting the opening movement by utilizing the along the flow body 201A to provide flowing coolant stream S2. This supporting force increases with increasing volume of the coolant flow S2, so that the assisting force in its amount with the opening of the closure element 200A increases.

By superposition of the opening movement counteracting spring force of the spring 204A on the one hand and the force supporting the opening movement of the flow body 201A On the other hand, a degressive characteristic of the elastic biasing force is provided, which causes the opening movement of the closure element 200A only starts when the pressure of the coolant flow S exceeds a predetermined pressure force, for further opening of the closure element 200A but then a comparatively low pressure increase of the coolant flow S is required. This is because the further opening movement of the closure element 200A by the fluidic force on the flow body 201A , due to the flow around the flow body 201A , is supported.

The force supporting the opening movement by flowing around the flow body 201A follows from the laws of fluid mechanics, in particular the law of Bernoulli, according to which flows of a body (such as the flow body 201A ) is accompanied by a speed increase of the circulating fluid with a pressure drop. At the the closure element 200A facing side of the flow body 201A Accordingly, a negative pressure is generated due to the shape of the flow body 201A and the resulting increased flow rate on this side. By this negative pressure is a force on the closure element 200A generated in the direction of the opening movement, which increases in magnitude with increasing volume of the coolant flow S2.

If the pressure of the coolant flow S, S2 drops, the closure element closes 200A automatically under the action of the biasing spring 204A and again enters the closed position according to 2 when the pressure of the refrigerant flow S, S2 by the spring 204A falls below predetermined limit pressure.

A second embodiment of a thermostatic valve 2 is in 3 shown. The operation of the thermostatic valve 2 is largely the thermostatic valve 2 according to 2 identical, wherein in the in 3 illustrated embodiment, the closure element 200B itself is designed as a flow body. The closure element 200B is via a between a feed-fixed attachment point 207B and a point of attachment 208B on the closure element 200B clamped spring 204B elastically biased, the spring 204B is designed as a tension spring and when opening the closure element 200B by pivoting about the pivot axis 202B is tense.

In the closed state of the thermostatic valve 2 lies the closure element 200B on a seal 205B and closes the thermostatic valve 2 , so no coolant flow through the thermostatic valve 2 can occur.

The opened state of the thermostatic valve 2 is in 3 with dashed closure element 200B located. In this state is the lead-fixed attachment point 207B the feather 204B still below a line 206B through the closure element 200B overlapping pivot axis 202B and the attachment point 208B , so that even when open, the spring 204B a force on the closure element 200B in the direction of his closed position.

The degressive characteristic of the elastic biasing force is in the embodiment according to 3 due to the degressive tension of the spring 204B during the opening movement of the closure element 200B provided. At the beginning of the opening movement is namely the spring 204B stretched by a comparatively long length per opening path (large pitch), while with increasing pivoting of the closure element 200B the elongation of the spring 204B decreases per opening path. Initially, therefore, a predetermined compressive force of the coolant flow S, S2 for moving the closure element 200B required while the further opening movement of the closure element 200B then requires a disproportionate increase in pressure.

A third embodiment of a thermostatic valve 2 shows 4 , The embodiment according to 4 corresponds substantially to the embodiment according to 3 , wherein only the closure element 200C via a connecting bridge 203C one outside the line 206C horizontal pivot axis 202C is arranged pivotably. The elastic bias can analogously as in the embodiment according to 3 be provided or via one about the pivot axis 202C acting leg spring 204C , Again closed in the closed state (solid lines) the closure element 200C by contact with a seal 205C the thermostatic valve 2 sealing.

A fourth embodiment of a thermostatic valve 2 is in 5 shown. In contrast to the preceding embodiments, in this embodiment, a closure element 200D provided that not pivotable, but via a sliding guide 202D slidable to a fixed position within the supply line 130 arranged flow body 201D is arranged. The closure element 200D is about a spring 204D in the form of a compression spring relative to the flow body 201D biased, the spring 204D within a hole 203D of the closure element 200D is arranged.

In the in 5 shown closed position is the closure element 200D on a seal 205D and thus closes the thermostatic valve 2 sealing.

At the flow body 201D is protruding into the hole 203D of the closure element 200D , a magnet 206D arranged with a magnetic anchor 207D , For example, of a ferromagnetic steel, on the closure element 200D interacts.

About the magnet 206D and the anchor 207D a degressive elastic biasing force is provided. So must for initial opening of the closure element 200D the pressure of the refrigerant flow S exceeds a predetermined (limit) pressure to the spring force of the spring 204D to overcome. If the pressure then continues to rise, the spring becomes 204D further compressed, thereby simultaneously the anchor 207D the magnet 206D approximates and the magnetic attraction between magnet 206D and anchor 207D rises, so that the further opening movement of the closure element 200D increasingly supported. As a result of the magnetic support, only a comparatively small, underproportional increase in pressure is required for the further opening movement, with the degressivity of the elastic preload force due to the design of the spring 204D and the magnet 206D can be adjusted.

A fifth embodiment of a thermostatic valve 2 shows 6 , In this embodiment, in turn, the laws of fluid mechanics are exploited by the opening movement of a closure element 200E fluidically supported by the generation of a negative pressure, which via a membrane 206E for assisting the opening movement on the closure element 200E is transmitted.

As in 6 can be seen, is the closure element 200E elastic over a pestle 203E and a spring 204E in the form of a compression spring against a wall of the supply line 130 biased. The closure element 200E opens accordingly only when the pressure of the coolant flow S exceeds a predetermined value and thus the biasing spring force of the spring 204E can overcome. By the spring force of the spring 204E In this way, the limit pressure required for opening is specified.

In the closed state lies as if out 6 it can be seen, the closure element 200E sealing against a seal 205E the supply line 130 at.

Will the spring force of the spring 204E overcome and the closure element 200E opened in a pressure-controlled manner, a flow of coolant S2 flows through the thermostatic valve 2 and enters through a constriction 201E , as a result of which the flow velocity of the coolant stream S2 in the region of the line constriction 201E is increased. Accordingly arises in the area of the line constriction 201E a negative pressure, over a channel 207E in the wall of the supply line 130 to a subspace 208E transferred and across the membrane 206E and a connection channel 210E also on a subspace 209E is transmitted. By this negative pressure, a force in the direction U (see 6 ) on the membrane 206E in the area of the plunger 203E exerted, so that the opening movement of the closure element 200E is supported. Accordingly, for further opening of the closure element 200E a comparatively small increase in pressure is required after a first, initial opening of the closure element 200E is done.

As the opening increases, so does the volume of the passed coolant flow S2, so that the assisting force, due to the generated negative pressure, also increases and a degressive characteristic for opening is obtained.

If the pressure of the coolant flow S2 drops, the closure element closes 200E by the action of the spring 204E again, until the thermostatic valve 2 gets into its closed state.

A sixth embodiment shown in FIG 7 , basically uses the same principle as the embodiment according to FIG 6 , In the embodiment according to 7 However, it is a closure element 200F via a sliding guide 202F displaceable at a fixed location within the supply line 130 arranged flow body 201F arranged. The closure element 200F is about one within a hole 203F arranged elastic spring 204F opposite the flow body 201F biased, wherein by the biasing force of the elastic spring 204F the initial pressure to be overcome to open the thermostatic valve 2 is predetermined.

When closed, the closure element is located 200F on a seal 205F sealingly and thus closes the thermostatic valve 2 , But the pressure of the coolant flow S exceeds the biasing spring force of the spring 204F , the closure element shifts 200F on the flow body 201F to, so that a flow of coolant S2 through the thermostatic valve 2 can occur.

The coolant stream S2 flows around the closure element 200F and in particular also the flow body 201F , wherein in the region of the closure element 200F opposite end of the flow body 201F caused by the flow velocity of the coolant flow S2, a negative pressure is generated, which via a channel 207F to a subspace 208F is transmitted and causes one with the closure element 200F connected membrane 206F is attracted. By tightening the membrane 206F becomes a force on the closure element 200F exercised that the further opening movement of the closure element 200F supports and thus creates a degressivity of the characteristic of the elastic biasing force.

A seventh embodiment of a pressure controlled thermostatic valve shows 8th In this embodiment, a closure element 200 G via an elastic spring 204G in the form of a compression spring against one to the supply line 130 stationary flow body 201G is biased. When closed, shown in 8th , is this elastic spring 204G determined by the closure element 200 G opposite the flow body 201G over a toggle 209G is held.

The toggle 209G is on the one hand at an attachment point 211G on the flow body 201G hinged and on the other hand via an attachment point 212G with the closure element 200 G connected. In the closed state according to 8th there is a knee joint 210G of the toggle lever 209G below a connecting line through the attachment points 211G . 212G and lies on a slider 208G a control piece 207G on, so that in the closed state, the closure element 200 G opposite the flow body 201G is held.

The control piece 207G is on the closure element 200 G arranged and acts on the slider 208G on the knee joint 210G of the toggle lever 209G one. The control piece 207G is over a second elastic spring 206G in the form of a compression spring against the closure element 200 G biased and serves as a pilot valve for controlling the opening movement of the closure element 200 G ,

In the embodiment according to 8th is the pressure to be initially overcome by the control piece 207G Preloading spring force of the spring 206G specified. Will this biasing spring force of the spring 206G overcome, the control piece shifts 207G in the direction V into the closure element 200 G and pushes over the slider 208G the knee joint 210G of the toggle lever 209G up. Exceeds the knee joint 210G the connecting line of the attachment points 211G . 212G , the closure element becomes 200 G not over the toggle anymore 209G opposite the flow body 201G recorded. The closure element 200 G can affect the flow body 201G to move under compression of the closure element 200 G opposite the flow body 201G biasing spring 204G ,

The feather 204G For example, in order to provide a degressivity of the elastic biasing force, it may be made soft so that after overcoming the biasing spring force 206G and unlocking of the toggle lever 209G only a comparatively small increase in pressure is required to the closure element 200 G continue to open and transfer to a fully open position.

If the pressure of the coolant flow S2 drops, the closure element moves 200 G in the reverse direction, due to the force of the spring 204G , It also moves the toggle 209G back, powered by a toggle 209G biasing, at the attachment points 212G attacking thigh feather 213g (not shown in detail). The toggle 209G gets back into it again 8th shown position, locks the closure element 200 G opposite the flow body 201G and keep it in the closed position according to 8th ,

An eighth embodiment of a thermostatic valve 2 is finally in 9 shown. In this thermostatic valve is a closure element 200H over an intermediate part 206H relative to a stationary within the supply line 130 arranged flow body 201H biased. The intermediate part 206H is via a sliding guide 202H in a hole 203H of the intermediate part 206H engages, displaceable on the flow body 201H stored.

At the intermediate part 206H is a threaded bolt 207H arranged in a thread 208H the closure element 200H intervenes. Furthermore, the closure element 200H over a mainspring 209H in the form of a wound leaf spring opposite the intermediate part 206H biased.

The operation of the thermostatic valve 2 according to 9 is the following. When closed, shown in 9 , lies the closure element 200H on a seal 205H the supply line 130 and seals the supply line 130 with it. If the pressure of a coolant flow exceeds a predetermined value, the closure element becomes 200H and together with the closure element 200H the intermediate part 206H in the direction of the flow body 201H moved and thereby designed as a compression spring, biasing spring 204H compressed. The thermostatic valve 2 is opened in this way, so that a coolant flow S2 through the thermostatic valve 2 can occur.

This coolant stream S2 acts on the closure element 200H arranged flow wings 211H and causes the closure element 200H in a direction of rotation D relative to the threaded bolt 207H is twisted. This will be the closure element 200H via the thread engagement 207H . 208H relative to the intermediate part 206H bolted and to the intermediate part 206H moved, and the mainspring 209H will be curious.

By the rotational movement of the closure element 200H becomes the thermostatic valve 2 further opened and gets into its fully open state. Characterized in that the mainspring is comparatively soft, the further opening movement requires a comparatively small further increase in pressure until complete opening, after the pressure of the coolant flow, the initial biasing force of the spring 204H has overcome.

If the pressure of the coolant flow S2 decreases, the closure element moves 200H , driven by the tensioned mainspring 209H , back against the direction of rotation D and is thus from the intermediate part 206H removed, leaving the closure element 200H driven by the mainspring 209H returned to its closed position.

The pressure-controlled thermostatic valve 2 is by default of the coolant flow S via the coolant pump 11 (please refer 1 ) controlled. To control the thermostatic valve 2 becomes the coolant pump 11 regulated, with the opening state of the thermostatic valve 2 depending on the through the coolant pump 11 adjusted coolant pressure.

As in 1 indicated by dashed lines, a control loop can be created by, for example, the thermostatic valve 2 a temperature sensor in the supply line 130 is connected downstream and by feedback in dependence on measured values of this temperature sensor, the coolant flow S of the coolant pump 11 is regulated.

The idea underlying the invention is not limited to the above-described embodiments. In particular, it is conceivable to use thermostatic valves of the type mentioned also outside of coolant circuits in vehicles, for example for controlling other fluid circuits. Likewise, entirely different embodiments for pressure control of the thermostatic valve are conceivable and possible, as well as the characteristic of an elastic biasing force can basically be designed arbitrarily.

LIST OF REFERENCE NUMBERS

1

Cooling water circuit

10

internal combustion engine

11

Coolant pump

110

supply

12

Heating radiator

120

supply

13

cooler

130

supply

2

thermostatic valve

200A

closure element

201A

flow body

202A

swivel axis

203A

connecting webs

204A

feather

205A

poetry

200B

closure element

202B

swivel axis

204B

feather

205B

poetry

206B

line

207B

Spring attachment point

208B

Spring attachment point

200C

closure element

202C

swivel axis

203C

connecting web

204C

feather

205C

poetry

206C

line

200D

closure element

201D

flow body

202D

sliding guide

203D

drilling

204D

feather

205D

poetry

206D

magnet

207D

Magnetic anchor

200E

closure element

201E

line narrowing

202E

swivel axis

203E

tappet

204E

feather

205E

poetry

206E

membrane

207E

channel

208E

subspace

210E

connecting channel

200F

closure element

201F

flow body

202F

sliding guide

203F

drilling

204F

feather

205F

poetry

206F

membrane

207F

channel

208F

subspace

209f

subspace

200 G

closure element

201G

flow body

202G

sliding guide

203G

drilling

204G

feather

205G

poetry

206G

feather

207G

control piece

208G

pusher

209G

toggle

210G

knee

211G, 212G

attachment point

213g

Leg spring

200H

closure element

201H

flow body

202H

sliding guide

203H

drilling

204H

feather

205H

poetry

206H

intermediate part

207H

threaded bolt

208H

thread

209H

mainspring

210H

rotor

211H

flow wing

D

direction of rotation

S, S1, S2

Coolant flow

AND MANY MORE

direction

QUOTES INCLUDE IN THE DESCRIPTION

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Cited patent literature

• DE 3502817 A1 [0005]
• DE 3817952 A1 [0005]
• DE 10360169 A1 [0007]

Claims (16)

A coolant circuit for an internal combustion engine of a vehicle, comprising - a supply line and - a arranged in or on the supply line thermostat valve for controlling a flow of coolant through the supply line, wherein the thermostat valve for controlling the flow of coolant a closed state in which flows no coolant flow through the supply line, and an open state in which a flow of coolant flows through the supply line can assume, characterized in that the thermostatic valve ( 2 ) is pressure controlled by the thermostatic valve ( 2 ) as a function of the pressure of the coolant flow (S, S1, S2) in the supply line ( 130 ) is controlled to take the closed state and the opened state. Coolant circuit according to claim 1, characterized in that the thermostatic valve ( 2 ) a closure element ( 200A -H) for closing the supply line ( 130 ) in the closed state, wherein the closure element ( 200A -H) for transfer to the open state of the thermostatic valve ( 2 ) about a pivot axis ( 202A -C, 202E ) pivotable or along a sliding guide ( 202D . 202F -H) is displaceable. Coolant circuit according to claim 2, characterized in that the closure element ( 200A H) is formed as a function of the pressure of the coolant flow (S, S1, S2) in the supply line ( 130 ) between a closed position and a maximum open position to be adjusted. Coolant circuit according to claim 2 or 3, characterized in that the closure element ( 200A -H) elastic with respect to a relative to the supply line ( 130 ) fixed portion is biased toward the closed position. Coolant circuit according to claim 4, characterized by an elastic spring ( 204A -H) for providing the elastic biasing force. Coolant circuit according to claim 4 or 5, characterized in that the provided elastic biasing force degressive over the opening path of the closure element ( 200A -H). Coolant circuit according to one of claims 4 to 6, characterized by additional means ( 206D . 206E . 206F . 209G . 209H ) for providing a degressive characteristic of the elastic biasing force. Coolant circuit according to claim 7, characterized in that the additional means by a on the closure element ( 200A ) arranged flow body ( 201A ) for generating a force on the closure element ( 200A ) are formed in the direction of the maximum open position. Coolant circuit according to claim 7, characterized in that the additional means by a on a flow body ( 201D ) of the supply line ( 130 ) arranged magnets ( 206D ) formed an anchor ( 207D ) of the closure element ( 200D ) attractive for generating a force on the closure element ( 200D ) is opposite in the direction of the maximum open position. Coolant circuit according to claim 7, characterized in that the additional means by a on the supply line ( 130 ) or a flow body ( 201F ) of the supply line ( 130 ) arranged membrane ( 206E . 206F ) formed by a through the supply line ( 130 ) flowing coolant flow (S, S1, S2) with a negative pressure for generating a force on the closure element ( 200E . 200F ) is acted upon in the direction of the maximum open position. Coolant circuit according to claim 7, characterized in that the additional means by a toggle lever ( 209G ) are realized, which in a starting position, the closure element ( 200 G ) in its closed position and by action of a coolant flow (S, S1, S2) via a control piece ( 207G ) for the activation of the closure element ( 200 G ) is operable. Coolant circuit according to claim 7, characterized in that the additional means by a mainspring ( 209H ) are formed, which is stretched under the influence of the coolant flow (S, S1, S2) characterized in that the closure element ( 200H ) is set in a rotary motion. Coolant circuit according to one of the preceding claims, characterized by an electrically operated, independent of the internal combustion engine ( 10 ) controllable coolant pump ( 11 ). Coolant circuit according to claim 13, characterized in that the electrically operated coolant pump ( 11 ) as a function of an engine load, a vehicle speed and / or a temperature of the internal combustion engine ( 10 ) is controllable. Coolant circuit according to claim 13 or 14, characterized in that via the electric coolant pump ( 11 ) the pressure of the coolant flow (S, S1, S2) for controlling the thermostatic valve ( 2 ) is set. Coolant circuit according to one of claims 13 to 15, characterized in that the coolant circuit has a first circuit (K1) and a second circuit (K2), wherein when the thermostatic valve is closed ( 2 ) a coolant flow (S, S1) flows only through the first circuit (K1) and when the thermostatic valve is open ( 2 ) flows through a coolant flow (S, S1, S2) both through the first circuit (K1) and through the second circuit (K2).

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