Temperature control system for controlling the temperature of workpieces, and method for controlling the temperature of workpieces

Abstract

The present invention relates to a temperature control system (100) for controlling the temperature of workpieces, in particular for heating vehicle bodies, wherein the temperature control system (100) comprises the following: - at least two temperature control modules (104) which are located one behind the other in a direction of travel (102); and - at least one power module (105) for circulating and controlling the temperature of recirculation air, said power module being placed at least in part between the at least two temperature control modules (104), wherein the at least two temperature control modules (104) and the at least one power module (105) form a temperature control chamber (106) through which the workpieces can be conveyed along the direction of travel (102) in order for their temperature to be controlled by recirculation air. The present invention also relates to a corresponding method for controlling the temperature of workpieces, in particular for heating vehicle bodies.

Description

[0001] Tempering system for tempering workpieces and process for tempering workpieces

[0002] The present invention relates to a tempering system for tempering workpieces, in particular for heating vehicle bodies. Furthermore, the invention relates to a corresponding method for tempering workpieces.

[0003] Temperature control systems designed as continuous dryers for heating vehicle bodies are known from practice. These typically feature either intermittent or continuous conveying of the vehicle bodies.

[0004] Tempering systems for heating vehicle bodies can also be referred to as dryers, whereby the tempering chamber of the system, through which the vehicle bodies are conveyed, is also referred to as the dryer tunnel.

[0005] The air in the known systems is circulated and tempered by means of recirculation units or temperature control devices. Separate or integrated devices for this purpose are known from the prior art.

[0006] For example, the separate units or devices can be positioned above, below or to the side of the dryer tunnel or the temperature control room.

[0007] With regard to the heat sources used to heat the circulating air, direct or indirect burner heating, electrical heating or clean gas heating using one or more heat exchangers are possible.

[0008] In comparison, in an integrated arrangement, the temperature control device or the recirculation unit is located on the same level as the temperature control room or the drying tunnel.

[0009] The fan used for recirculating air can be positioned on either side of the dryer tunnel, relative to the air flow direction. Alternatively, the fan can be inserted into the dryer tunnel from above, so that in the case of a radial fan, the impeller axis is aligned vertically.

[0010] In the case of integrated recirculation units or temperature control devices, it has been preferred to arrange the heat source for tempering the recirculation air on both sides of the temperature control room or dryer tunnel, whereby in addition to a combustion chamber, a clean gas duct can also be used as a radiation source for heating the recirculation air.

[0011] The recirculation air supply in the temperature control room or dryer tunnel can be arranged on either side of the conveying direction. In the latter case, a portion of the recirculation air is transferred from the side of the temperature control system where the recirculation unit or temperature control device is located to the other side of the temperature control system via a connecting duct or a throw-over duct, or via a connecting chamber or a throw-over ceiling.

[0012] The recirculation air from the temperature control room or the dryer tunnel can be recirculated on both sides or on one side.

[0013] With a two-way recirculation system, the recirculation air from the temperature control room can be taken in at the beginning or end of the temperature control room or a section of the room, for example, via the side walls or the floor or ceiling. Recirculation air can also be taken in or out of the center of the temperature control room.

[0014] With regard to a one-sided recirculation air return, a return at the bottom or at least close to the bottom in the middle of the temperature control room is preferred, based on the conveying direction.

[0015] The arrangement of the previously described recirculation units or temperature control devices on a temperature control system is accompanied by a corresponding space requirement of the temperature control system, in particular in a width direction of the system, which is aligned horizontally and perpendicular to the conveying direction.

[0016] The present invention is therefore based on the object of providing a temperature control system which has a small space requirement and is designed in a resource-optimized manner.

[0017] This object is achieved according to the invention by a tempering system for tempering workpieces having the features according to claim 1.

[0018] The tempering system is specifically a system for heating vehicle bodies.

[0019] The tempering system comprises the following: at least two tempering modules arranged one behind the other in a conveying direction; and at least one power module for circulating and tempering circulating air, which is arranged at least partially between the at least two tempering modules, wherein the at least two tempering modules and the at least one power module form a tempering chamber through which the workpieces can be conveyed along the conveying direction for tempering with circulating air.

[0020] The invention is based on the idea that a narrow width of the temperature control system or the temperature control modules makes it possible to set up two temperature control systems next to each other within a standard 12-meter hall grid, i.e. to set up a double dryer. In addition, the lateral integration of the temperature control device is easy to maintain. For this purpose, a power module with a preferably lateral temperature control device is integrated as an intermediate segment between two temperature control modules - related to the conveying direction of the workpieces - and thus connects the temperature control modules. It is advantageous if the temperature control device does not protrude, or at least protrudes only slightly, beyond the width of the temperature control modules. In addition, the arrangement of the temperature control device on one side of the temperature control system makes it possible to achieve a low installation height for the entire temperature control system within one building level.

[0021] A characteristic feature of the temperature control system according to the invention is the single-sided arrangement of a fan, whose axis is aligned horizontally to the hall floor and perpendicular to the conveying direction, and to which a heating gas is supplied in addition to the recirculating air, on one side of the temperature control system, the so-called operating side. This characteristic is also a necessary prerequisite for the construction of a double dryer line or for installation against adjacent hall walls or other similar interference contours.

[0022] A further advantage of the temperature control system according to the invention is that by using temperature control modules in conjunction with a central power module, the entire temperature control system can be modularized into a few standardized modules or segments.

[0023] Accordingly, standardized temperature control modules with a fixed length in the conveying direction (longitudinal length) can be combined with a power module with a variable length. The variable length of the power module makes it possible to implement a body-specific cycle length. Conversely, the power module can also have a fixed length, while the temperature control modules can be designed with a variable length.

[0024] It is also conceivable that the longitudinal extent of the tempering system could be extended for longer workpieces by using intermediate modules.

[0025] This results in a cost-effective concept for a temperature control system in which, on the one hand, the workpieces conveyed through can be supplied with circulating air homogeneously and symmetrically and, on the other hand, the circulating air from the temperature control room of the temperature control system can be removed centrally or centrally, relative to the conveying direction, via an extraction system in the floor area.

[0026] The temperature control modules, which together with the power module form the temperature control chamber or dryer tunnel, enable the provision of standard cycle lengths for the temperature control of workpieces. This can also be referred to as the provision of so-called cycle stations, which preferably correspond to the usual lengths or longitudinal extensions of workpieces designed as vehicle bodies.

[0027] The cycle stations, which are each formed by a tempering module and / or a tempering module and the power module, are dimensioned in their longitudinal extent so that a workpiece can preferably be accommodated completely.

[0028] Advantageously, at least one cycle location of the temperature control chamber, i.e., in particular, a temporary position of a workpiece during the conveying of the workpieces in the conveying direction, extends at least partially into the power module, thereby reducing the extension of the temperature control modules adjacent to the power module in the conveying direction. In other words, each temperature control module directly adjacent to a power module is preferably shorter than the cycle location of a workpiece to be temperature-controlled, such as a vehicle body to be heated, since the corresponding cycle location extends at least partially into the power module.

[0029] The cyclical operation or cyclical operation of the tempering system has the advantage over continuous operation, in which the workpieces are continuously conveyed through the system, i.e. without temporary pauses, that the workpieces can be specifically blown or flowed onto with tempered circulating air in their temporary rest position.

[0030] For example, a temperature control system with two temperature control modules and a power module arranged between them has a total longitudinal extension of 11 m in order to provide two cycle stations for workpieces designed as vehicle bodies with a length of up to 5 m.

[0031] It should be understood that the temperature control system according to the invention is not limited to the number of two temperature control modules arranged one behind the other, but that further combinations of temperature control modules are possible. Accordingly, two to six or more temperature control modules can be arranged one behind the other, with all possible combinations being designed as a heating zone, a holding zone, or a cooling zone. The power module can be arranged or integrated between any two adjacent temperature control modules, but preferably the power module is arranged in the center of the respective zone. Furthermore, the power module can be arranged at the beginning or end of the temperature control system, relative to the conveying direction.

[0032] The tempering device is in particular a heating and / or cooling device or is integrated therein.

[0033] It may be advantageous if the temperature control system has at least one system housing that separates the temperature control modules and / or the power module from the environment of the temperature control system or encloses them.

[0034] The temperature control modules and the power module preferably form a common system housing.

[0035] It can further be provided that the at least one power module comprises at least one temperature control device.

[0036] It is advantageous if the at least one temperature control device is arranged laterally on the temperature control chamber with respect to the conveying direction, and preferably, the at least one temperature control device is arranged approximately in the center of the temperature control chamber with respect to the conveying direction. It is also advantageous if the at least one power module comprises a connecting channel and / or a connecting chamber.

[0037] In the case of a one-sided arrangement of the tempering device, i.e. an arrangement on only one side of the tempering chamber or the tempering system, it is necessary for a homogeneous and symmetrical flow of the workpieces in the tempering chamber that a part of the tempered circulating air can be conveyed to the other side of the tempering chamber.

[0038] It can be advantageous if the power module and two tempering modules directly connected to the power module form two cycle stations for preferably two workpieces, with each of these cycle stations extending at least partially into the power module in relation to the conveying direction.

[0039] It can further be provided that the temperature control system has at least two zones of different temperatures along the conveying direction.

[0040] In a further embodiment of the invention, it can be provided that the temperature control system has at least one heating zone and / or at least one holding zone.

[0041] It may be advantageous if the zones can be atmospherically and / or thermally separated from one another and / or from the surroundings of the temperature control system by a) one or more barrier elements and / or b) one or more airlocks.

[0042] A blocking element can in particular be a physical barrier such as a sliding door, a vertically movable door leaf or the like.

[0043] Furthermore, a blocking element can be at least partially thermally insulated.

[0044] In the open position of a blocking element, this can preferably be located in a recess, chamber, niche or interim position provided for this purpose above, below or to the side of the temperature control chamber and from there can be moved into the temperature control chamber to separate the zones.

[0045] A locking element can be a single-part or multi-part locking element. With multi-part locking elements, the components can be moved either in opposite directions or parallel to each other.

[0046] One or more blocking elements are preferably provided between at least two zones when the cycle time is sufficiently long, wherein the cycle time is in particular the time during which a workpiece is treated in a zone.

[0047] This is the case, for example, if the cycle time is greater than or equal to the time required for the closing and opening of the locking elements. It is particularly preferred if the cycle time for the workpiece treatment is equal to or greater than five times the time required for the closing and opening of the locking elements.

[0048] It is also advantageous if an airlock is designed as a flow barrier for atmospheric and / or thermal separation between two zones or process areas of a temperature control system.

[0049] Furthermore, it can be advantageous if the airlock is designed vertically and contoured to the workpiece.

[0050] Preferably, the airlock is designed in the form of a vertical and workpiece-contoured double silhouette.

[0051] The two silhouettes can be the same or different in terms of their temperature and / or their proportion of fresh air and recirculated air.

[0052] The airlock is arranged in particular between two cycle stations, in each of which preferably one workpiece is treated.

[0053] An air curtain or a silhouette of an airlock preferably extends across the entire width of the temperature control room.

[0054] In the case of temperature-graded process areas, which can be configured, for example, as a pre-dryer, a main dryer, or a cooling zone and have different temperature levels, the airlock is preferably provided between each two temperature zones. The airlock can be formed from the ceiling, one or both side walls, or the floor of the temperature control chamber; in particular, the lock air is introduced into the temperature control chamber from these positions.

[0055] It may be advantageous if the lock air from a slotted nozzle located on the ceiling of the temperature control chamber is directed toward the warmer atmosphere at an angle to the direction of gravity in the range of 20 degrees to 40 degrees, preferably approximately 30 degrees, i.e., toward the adjacent zone with the higher temperature. Such an airlock thus creates a pulse against the thermal pressure of the adjacent zone with the higher temperature.

[0056] It is advisable to keep the area of ​​the airlock clear or to move it clear using a conveyor-based quick-release system so that the lock air jet is not disturbed by a workpiece remaining there.

[0057] In this case, airlock is introduced into the tempering chamber, for example, between two sheets that follow the contour of the workpiece moving longitudinally or transversely. The airlock flows vertically from top to bottom and is then removed from the tempering chamber via a floor extraction system.

[0058] The air of the airlock preferably flows downwards and can be extracted, for example, in the floor area of ​​the temperature control chamber via two floor extraction openings arranged one behind the other in the conveying direction, which can be designed as floor extraction slots and extend over the entire width of the temperature control chamber, ie transversely to the conveying direction.

[0059] It is also conceivable that the lock air flows from bottom to top against the direction of gravity and is extracted in the ceiling area of ​​the temperature control room.

[0060] The lock air can also flow through the temperature control chamber in a horizontal direction, ie it flows into the temperature control chamber from one side wall and is discharged or extracted in the area of ​​the opposite side wall.

[0061] The resulting air curtain or air silhouette preferably runs essentially perpendicular to the conveying direction of the workpieces. Airlocks can be operated with fresh air, recirculated air, or a mixture of recirculated air and fresh air.

[0062] It may further be provided that the airlock upstream of the temperature control room has at least one electric heating register in order to a) bring preheated lock air (fresh air or recirculated air or a mixture of both) to the desired temperature; or b) bring fresh air from the surroundings of the temperature control system or the hall in which the temperature control system is installed to the desired temperature near the lock.

[0063] This avoids the need for complex air ducts from a central airlock heating system to the airlock.

[0064] It can further be provided that two heating gas ducts and one fresh air duct are arranged on and / or at the modules of the temperature control system.

[0065] The heating gas ducts are preferably routed on and / or at and / or above the pressure chambers.

[0066] The fresh air duct is preferably arranged between the heating gas ducts, ie in particular substantially above the temperature control chamber.

[0067] One heating gas channel is preferably designed as a heating gas supply channel, whereas the other heating gas channel is preferably designed as a heating gas discharge channel.

[0068] The two heating gas channels are in particular connected directly or indirectly, e.g. via one or more heat exchangers, to a heating gas source or a heat source.

[0069] The fresh air duct is used in particular to supply fresh air to an inlet airlock in the inlet or entrance of the temperature control room and / or to an outlet airlock in the outlet or exit of the temperature control room.

[0070] The hot gas ducts are preferably routed through the connecting duct, which carries circulating air from the pressure chamber on the side of the temperature control device to the opposite side without a temperature control device. For the crossing, the hot gas ducts preferably have a reduced cross-section in the sections where they pass through the connecting duct, ensuring that sufficient circulating air can be guided or directed through the connecting duct to the other side of the temperature control system.

[0071] The heating gas guided in the heating gas ducts and the circulating air guided in the connecting duct are preferably fluidically separated from each other, ie in particular there is no mixing of heating gas and circulating air in the area of ​​the duct crossing.

[0072] In the transitions from the pressure chambers, on and / or at and / or above which the hot gas channels are arranged, to its horizontal section above the tempering chamber, the connecting channel can each have a widening or expansion in the direction of the tempering chamber, which corresponds to the shape of the cross-sectional reduction of the two hot gas channels in this area and at least approximately compensates for the volume reduction by the two hot gas channels.

[0073] Alternatively or additionally, the connecting channel in these transition sections can have a slope or run diagonally, preferably at an angle of 45 degrees to the side wall of the temperature control chamber and / or the ceiling wall of the temperature control chamber.

[0074] It may also be advantageous if the heating gas ducts are not led through the connecting duct, but are led past it with a cross-sectional reduction.

[0075] Preferably, the hot gas ducts do not protrude beyond the power module at the sides.

[0076] Alternatively or in addition, the heating gas ducts preferably do not exceed the connecting duct of the power module in height.

[0077] The fresh air duct, which is arranged between the two hot gas ducts, is preferably led over the connecting duct of the power module in the section in which it crosses the latter.

[0078] For this purpose, the fresh air duct preferably also has a sectionally reduced cross-section so that the fresh air duct does not protrude above the adjacent hot gas ducts. Such integration or arrangement of the described air ducts results in the respective duct loads being dissipated via the system casing, meaning no additional duct suspensions are required.

[0079] In addition, such integration makes such air ducts part of the modules, making separate thermal insulation unnecessary.

[0080] It can further be provided that at least one compensation device is provided for each two modules to absorb the thermal expansion in the conveying direction.

[0081] It can be advantageous to use a metal compensator with a bellows or a textile compensator that is welded or screwed between the two zones or modules.

[0082] It may be advantageous if at least one temperature control module and / or at least one power module is or are mounted on at least one fixed base, wherein the fixed base is preferably arranged below the respective module.

[0083] For a controlled expansion behavior of the modules of a temperature control system at operating temperature with the aim of avoiding mechanical overloading of the sheet metal construction or the welded joints, it can be advantageous to provide fixed feet or fixed points.

[0084] It can be advantageous if the individual modules can be extended in the conveying direction and transversely to it.

[0085] The fixed points or fixed feet of modules arranged one behind the other are preferably aligned along a common line in the conveying direction. In the transverse direction, i.e., perpendicular to the conveying direction, the fixed feet of a module are also preferably aligned along a common line.

[0086] In the case of the power module, it is advantageous if the fixed base is located below the fan of the temperature control device and thus below the area with the greatest surface load. In this case, the at least one heating zone can comprise two temperature control modules and a power module, with the at least one heating zone optionally comprising at least two intermediate modules to extend the temperature control chamber.

[0087] In addition, it can be provided that the at least one holding zone comprises four temperature control modules and a power module, which, with respect to the conveying direction, is preferably arranged centrally of the at least one holding zone, wherein optionally the at least one holding zone comprises at least two intermediate modules for extending the temperature control space.

[0088] It is advantageous if the at least one heating zone has an extension of a) 9 m to 12 m, preferably 11 m, or b) 12 m to 14 m, preferably 13 m, in the conveying direction.

[0089] It is further advantageous if the at least one holding zone has an extension of a) 20 m to 24 m, preferably 22 m, or b) 24 m to 28 m, preferably 26 m, in the conveying direction.

[0090] In addition, the temperature control system can also include a cooling zone, which preferably does not have a power module.

[0091] However, it is also conceivable that the respective power module is used as a cascade fan in several cooling zones arranged one behind the other, whereby the power module in this case essentially comprises a fan and a connecting duct, but no heat source or supply.

[0092] In cascade ventilation between several cooling zones, for example, fresh air is fed into the respective pressure chambers of the first cooling zone in the conveying direction. This fresh air is conveyed via these pressure chambers into the temperature control chamber section of the first cooling zone and from there is extracted by the fan of the power module of the first cooling zone in the floor area of ​​the corresponding temperature control chamber section. The extracted circulating air from the first cooling zone is then introduced into the pressure chambers of the second cooling zone downstream in the conveying direction and via these reaches the temperature control chamber section of the second cooling zone, from which the circulating air is also extracted in the floor area by the fan of the power module of the second cooling zone and fed to the pressure chambers of the next cooling zone downstream in the conveying direction. The corresponding circulating air is discharged from the temperature control chamber of the last cooling zone in this sequence, i.e. the cascade network of cooling zones, as exhaust air from the temperature control system.

[0093] It can further be provided that the at least one temperature control device comprises at least one fan.

[0094] The fan axis is preferably aligned horizontally and / or perpendicular to the conveying direction.

[0095] The fan is preferably arranged in the lower half, in particular in the lower third, of the temperature control device or the temperature control system.

[0096] The low position of the fan makes it easier to remove.

[0097] The fan's installation depth is defined by the distance from the side wall of the temperature control chamber to the outer wall of the temperature control device or system. In other words, the fan's installation depth is defined by the width of the pressure chamber of the temperature control system in which the fan is integrated. For a fan, this dimension corresponds to the distance from the fan nozzle to the inside of the fan's insulation cassette; that is, the intake nozzle and fan impeller are located in the pressure chamber.

[0098] The fan's intake nozzle can be set back from the side wall of the temperature control chamber, i.e., spaced apart along the width of the temperature control modules. In this case, a transition duct element is arranged between the side wall of the temperature control chamber and the frame housing of the intake nozzle, through which the circulating air discharged from the temperature control chamber is guided from the side wall of the temperature control chamber to the intake nozzle. This transition duct element is also referred to below as the intake chamber.

[0099] The space radially surrounding the fan within the pressure chamber forms a conditioning chamber for the recirculating air flowing from the fan. It is conceivable that the conditioning chamber is spatially delimited within the corresponding pressure chamber. The distance from the bottom edge of the fan's impeller to the bottom of this conditioning chamber is preferably 10% and particularly preferably 75% of the fan's impeller diameter.

[0100] In a further embodiment of the invention, it can be provided that the fans of the heating zones and the holding zone are at least approximately the same size.

[0101] In view of a uniform design, it can be advantageous if the fans integrated in the heating zones and the holding zones are of the same size, i.e. in particular if they use the same fan.

[0102] The fans preferably correspond in their impeller size, their fan chamber and / or their fan flange plate.

[0103] Since the different zones of the temperature control system require different air volumes, they are preferably operated at different speeds, with the speed of the fan motor preferably being controlled and / or regulated via a frequency converter.

[0104] For example, the recirculating air volume flow is 40,000 m 3 / h up to 60,000 m3 / h, preferably 45,000 m 3 / h, and the speed 45 Hz to 55 Hz, preferably 50 Hz, for fans of temperature control devices in a heating zone.

[0105] In contrast, for example, the recirculating air volume flow is 45,000 m 3 / h up to 70,000 m 3 / h, preferably 60,000 m 3 / h, and the speed 55 Hz to 70 Hz, preferably 63 Hz, for fans of temperature control devices in a holding zone.

[0106] Since different shaft powers of the fans are required to achieve these volume flows, either all motors of the recirculation fans can be designed for the largest shaft power or different sized motors can be used for the fans in different zones.

[0107] For example, the power of a fan motor for a heating zone can be 15 kW to 25 kW, preferably 18.5 kW, and the power of a fan motor for a holding zone can be 30 kW to 45 kW, preferably 37 kW. It can also be provided that an intake chamber is arranged upstream of the fan.

[0108] The intake chamber is preferably formed when the frame housing of the intake nozzle of the fan is spaced apart from the corresponding side wall of the temperature control chamber and a transition channel element is arranged in the intermediate space for bridging purposes.

[0109] It is also advantageous if a heating gas can be supplied to the intake chamber.

[0110] The temperature control, in particular the heating, of the temperature control room is thus achieved by adding heating gas to the circulating air passing through the temperature control system.

[0111] Introducing heating gas into the fan's intake chamber is particularly advantageous due to the favorable pressure conditions on the fan's intake side; moreover, the heating gas in the fan can be optimally mixed with the circulating air by the fan impeller.

[0112] However, it is also possible to supply the heating gas downstream of the fan, i.e. on the pressure side of the fan.

[0113] A possible intake point for the hot gas could be the upper point of the fan's intake hopper housing. It is advantageous if the hot gas is mixed into the drawn-in recirculating air stream as centrally as possible in the area of ​​the intake nozzle. For this purpose, the branch line can be extended to the center of the intake nozzle.

[0114] The heating gas is preferably heated at a central location outside the temperature control system, making the system universally applicable and flexible in terms of the heat source. Heating outside the temperature control system is preferably carried out to a temperature approximately 100 K higher than the temperature of the circulating air within the temperature control system. Furthermore, changing the heat source is possible without interfering with the temperature control system.

[0115] The heating gas is, in particular, the dryer atmosphere, which is extracted from the temperature control chamber by the fan and fed to a central heating point. In special cases, it is advisable to provide several heating gas circuits with a central heat exchanger, allowing different sections of the temperature control system to be atmospherically separated from each other. For example, one section of the system can be designed as a pre-dryer and a section downstream in the conveying direction can be designed as the main dryer. Both sections can then be exposed to different heating gas temperatures due to different solvent loads, which arise in particular from differences in the presence of high-boiling and low-boiling solvents.

[0116] In a further embodiment of the invention, it can be provided that the heating gas can be supplied to the intake chamber by means of a branch line, preferably a vertical branch line.

[0117] The branch line preferably runs outside the temperature control chamber along the corresponding side wall of the temperature control chamber, wherein the branch line can be insulated at least in sections in order to avoid local heat input into the temperature control chamber.

[0118] It can further be provided that the branch line is fluidly connected to a heating gas supply line, in particular a horizontal heating gas supply line, by means of which heating gas from a heat source can be supplied to the temperature control system.

[0119] Various energy sources can be considered as heat sources, such as electricity, gas, hydrogen, thermal oil, solar thermal energy, etc., whereby the thermal energy of these sources can be introduced directly into the heating gas or transferred indirectly to the heating gas by means of a heat exchanger.

[0120] It is also advantageous if the heating gas supply line can be arranged inside the temperature control chamber or outside the temperature control chamber.

[0121] The heating gas supply line can, for example, be designed as a horizontal channel running above the fan, wherein the channel is preferably arranged in the region of the side wall of the temperature control chamber which is adjacent to the fan or the temperature control device.

[0122] In one possible embodiment, such a channel can be arranged in an upper corner area of ​​the temperature control chamber, particularly in the form of an airtight triangular channel that is insulated from the temperature control chamber. Other geometries for the channel cross-section, such as a circular or rectangular shape, are also conceivable.

[0123] In a further possible embodiment, the heating gas supply line can be arranged as an airtight channel, which preferably has a rectangular or round cross-section, on the temperature control chamber, wherein the channel can be insulated from the temperature control chamber.

[0124] It may also be advantageous if a throttle device is provided in the branch line to control and / or regulate the volume flow of the heating gas.

[0125] The throttle device can be a valve or a damper. The throttle device can be used to control and / or regulate the volume flow of the heating gas that is mixed with the recirculating air, thereby adjusting the recirculating air temperature.

[0126] Preferably, it can further be provided that the throttle device is adjustable by means of a servo motor which is arranged outside the at least two temperature control modules and / or outside the at least one power module.

[0127] For this purpose, the externally arranged servo motor and the throttle device are preferably connected to each other via a drive shaft.

[0128] In a further embodiment of the invention, it can be provided that the temperature control system has a heating gas return line, in particular a horizontal heating gas return line, by means of which heating gas from the temperature control system can be returned to the heat source.

[0129] It may be advantageous if the heating gas return line can be arranged inside the temperature control room or outside the temperature control room.

[0130] The heating gas return line can, for example, be designed as a horizontal channel running above the fan, wherein the channel is preferably arranged in the region of the side wall of the temperature control chamber which is further away from the fan or the temperature control device.

[0131] In one possible embodiment, such a channel can be arranged in an upper corner area of ​​the temperature control chamber, particularly in the form of an airtight triangular channel that is insulated from the temperature control chamber. Other geometries for the channel cross-section, such as a circular or rectangular shape, are also conceivable.

[0132] In a further possible embodiment, the heating gas return line can be arranged as an airtight channel, which preferably has a rectangular or round cross-section, on the temperature control chamber, wherein the channel can be insulated from the temperature control chamber.

[0133] In both possible designs of the heating gas return line, a throttle device, which is designed, for example, as a rotary slide valve, is preferably arranged in the line in order to be able to control and / or regulate that a gas volume which is comparable to the gas volume supplied via the heating gas supply line is discharged from the temperature control system for reheating.

[0134] It is advantageous if the associated actuator for this throttle device is mounted on the temperature control system, and the connecting drive shaft is routed upwards out of the temperature control system. This leaves the side of the temperature control system without a temperature control device unobstructed, and the width of the temperature control system is not increased.

[0135] It can further be provided that a pressure chamber is formed on each side of the temperature control chamber, through which the circulating air can be introduced into the temperature control chamber.

[0136] Each pressure chamber is thus formed by the tempering modules arranged one behind the other as an at least approximately continuous space to the side of the tempering chamber.

[0137] It may be advantageous if the at least one temperature control device is arranged at least partially in a pressure chamber.

[0138] By integrating the temperature control device into a pressure chamber of the temperature control system, the width of the temperature control system can be significantly reduced. Further details on which components or parts of the temperature control device are preferably arranged in the pressure chamber will be explained below.

[0139] It is also advantageous if the pressure chambers are fluidly connected to one another by means of the connecting channel and / or the connecting chamber. The connecting channel or the connecting chamber, through which the circulating air is guided to the other pressure chamber, can be arranged on the temperature control modules. However, an arrangement in or as an intermediate thickness within the temperature control modules is also conceivable.

[0140] It is conceivable that holding zones only have a pressure chamber on the side of the temperature control device and therefore do not require a connecting channel.

[0141] In a further embodiment of the invention, it can be provided that the at least one tempering device projects beyond a width of the tempering modules, which is preferably aligned horizontally and perpendicular to the conveying direction, by less than approximately 25%, preferably 20% and particularly preferably 10% of the width of the tempering modules.

[0142] By allowing the temperature control device to protrude slightly in the direction of the width of the temperature control modules or the temperature control system, it is possible to arrange two temperature control systems next to each other in a standard hall grid to create a double temperature control system or a double dryer.

[0143] It can be beneficial if both pressure chambers are supplied with at least a similar proportion of tempered circulating air.

[0144] In a further embodiment of the invention, it can be provided that a spatially defined recirculating air distribution space is formed around the fan, which is arranged in the adjacent pressure chamber and which enables an adjustment of the recirculating air volume flows upwards into the connecting duct and into the adjacent pressure chamber.

[0145] The adjacent printing room is thus divided into two sections.

[0146] It is also advantageous if guide elements are arranged in the corner areas of the recirculating air distribution chamber or if the recirculating air distribution chamber as a whole is separated from the surrounding pressure chamber by a flow-optimized housing.

[0147] Throttle elements can be provided to adjust the recirculating air flow rates. Preferably, three throttle elements are provided, two of which adjust the recirculating air flow rates in the conveying direction and counter to the conveying direction into the adjacent pressure chamber. The third throttle element consequently adjusts the recirculating air flow rate into the connecting duct or into the other pressure chamber.

[0148] The throttle elements have a distance from the fan impeller of, for example, 0% to 20% of the impeller diameter of the fan or from 20% to 40% of the impeller diameter or from 40% to 80% of the impeller diameter.

[0149] It follows that the fan ejects the recirculating air radially into the recirculating air distribution chamber and the recirculating air is guided into the pressure chambers through the throttle elements acting as air outlets, whereby preferably approximately 50% of the recirculating air is guided into the connecting duct and approximately 25% of the recirculating air is guided into each of the two pressure chamber sections adjacent to the recirculating air distribution chamber.

[0150] The distribution of recirculation air to the pressure chambers can vary depending on the recirculation air requirements in the temperature control modules.

[0151] It may also be advantageous to provide fittings such as throttle and / or baffles in the recirculation air distribution chamber for optimised recirculation air distribution

[0152] Alternatively, the fan discharge into the adjacent pressure chamber and into the connecting duct can also be free, ie no recirculation air distribution space is provided.

[0153] Optionally, it can be provided that an undercut space is arranged between the recirculating air distribution space and the adjacent side wall of the temperature control space, wherein the branch line preferably runs through this undercut space.

[0154] This undercut chamber has additional inlet openings or nozzles by means of which the front and / or rear of workpieces designed as vehicle bodies, which have been conveyed into the tempering chamber for tempering, can be exposed to circulating air. The inlet openings of the undercut chamber therefore direct the circulating air, based on the longitudinal extent of the workpieces, to the front section of the workpiece, which is arranged in the tempering module at the rear in the conveying direction, and to the rear section of the workpiece, which is arranged in the tempering module at the front in the conveying direction. The undercut chamber is preferably spatially separated from the circulating air distribution chamber in the direction of the width of the tempering system and is supplied or exposed to, for example, filtered circulating air from the two adjacent pressure chamber sections.

[0155] The inlet openings or nozzles of the undercut chamber are preferably designed as nozzle cassettes, which are accessible and can be fastened from the temperature control chamber via fastening elements such as sash locks.

[0156] In a further embodiment of the invention, it can be provided that the temperature control device comprises a motor, in particular an electric motor, which drives the fan, wherein it is preferably provided that the motor is arranged at least approximately completely outside the temperature control modules.

[0157] As a result, for example, the extension of the motor in the direction of the width of the temperature control system or the temperature control modules determines the width of the entire temperature control system.

[0158] It can be advantageous if the circulating air can be discharged from the floor of the temperature control room.

[0159] It is also advantageous if the circulating air from the temperature control chamber can be discharged from the temperature control chamber by means of a return duct, wherein the return duct is preferably designed to be funnel-shaped at least in sections on the outlet side in order to increase the flow cross-section.

[0160] The recirculating air return or the recirculating air extraction preferably begins in the area between the two temperature control modules, i.e. between two workpieces to be tempered, which supports a homogeneous and symmetrical flow of the workpieces.

[0161] It is also advantageous if the suction opening or the return channel inlet is arranged between the two strands of the conveying device, which will be described later, thereby supporting a symmetrical flow of the workpieces.

[0162] The circulating air can preferably be discharged from the temperature control chamber to both sides of the conveying device or to one side of the conveying device.

[0163] Alternatively or additionally, the circulating air can be discharged centrally from the temperature control chamber and / or between two conveying devices arranged one behind the other in the direction of conveyance in the temperature control chamber.

[0164] By centrally extracting the recirculated air from the tempering chamber between two workpieces to be treated or between two cycles and / or, with respect to the conveying direction, at the level of the power module's tempering device, a homogeneous and symmetrical air flow to the workpieces is possible, as the recirculated air flowing into the tempering chamber is not deflected, as can occur with extraction or extraction close to the side walls. Furthermore, any dirt and dust is extracted close to the floor, ensuring that treated workpieces are not contaminated by revolving dirt and dust.

[0165] Furthermore, with a central discharge system, there is no risk that the doors of workpieces designed as vehicle bodies will be sucked up and possibly damaged in the tempering room.

[0166] In a further embodiment of the invention, it can be provided that the circulating air from the return duct can be discharged at least in sections diagonally upwards.

[0167] It can be advantageous if the intake chamber is located between the fan and the return duct.

[0168] It can further be provided that the return channel is designed as an intake box.

[0169] The intake box preferably connects the round fan intake opening with the cuboid intake opening, which is arranged in the temperature control room in the area of ​​the conveying devices, in order to achieve a low flow velocity at the extraction or discharge point as well as low pressure losses.

[0170] The intake box comprises in particular two shaped elements.

[0171] The first shaped element is preferably a wedge-shaped box element with a double slope, which borders the round fan intake opening.

[0172] The first slope preferably has an angle of approximately 20 degrees to the vertical, which lies in a vertical plane perpendicular to the conveying direction. Furthermore, the first slope extends from just above the round fan intake opening in the direction of the temperature control chamber, wherein the first slope is preferably spaced 10 cm to 20 cm, preferably 15 cm, from the associated side wall. The first slope is, in particular in an upper region, sufficiently spaced from a side or door of a workpiece designed as a vehicle body, for example 5 cm to 15 cm, preferably 10 cm. In the lower region, the first slope is preferably sufficiently spaced from the workpiece carrier or skid.

[0173] The second slope preferably has an angle of 45 degrees to the vertical, which lies in a vertical plane in the direction of the conveyor system.

[0174] The second slope expands the box element downwards, both in and against the direction of the conveyor system. The expansion, which preferably begins at the height of the fan axis, expands the box element, for example, from one-third of the power module width to two-thirds of the power module width, whereby the power module width here is preferably understood as the extension or extent of the power module in the conveying direction.

[0175] The second shaped element is preferably a cuboid-shaped box element, which adjoins the wedge-shaped box element.

[0176] The second forming element preferably extends from the side wall of the temperature control chamber to the conveyor device and has approximately the same width as the power module. In height, the second forming element preferably extends from the floor or floor wall of the power module to the lower edge of the workpiece carrier or skid, on which the workpieces are preferably conveyed through the temperature control chamber.

[0177] A roller conveyor or a hybrid conveyor with a chain and a roller conveyor is particularly suitable for an intake box due to the lack of a slack side, as this provides a sufficiently large cross-section for air intake and exhaust below the support profile of the conveyor or conveyor without having to raise the entire conveyor system in the temperature control chamber and / or in the area of ​​the interface to an external conveyor system. It is also advantageous if the connecting duct and / or the connecting chamber have a width, taken horizontally and parallel to the conveying direction, that at least approximately corresponds to the extension of the fan in the conveying direction.

[0178] This is intended to achieve a uniform flow of the circulating air from one side of the temperature control system to the other.

[0179] It is advantageous if guide elements are provided in the deflection areas at the transition from one pressure chamber to the connecting channel and from the connecting channel to the other pressure chamber, which prevent or at least minimize flow separation or backflow when changing between vertical and horizontal flow.

[0180] It can also be provided that the workpieces can be conveyed through the tempering chamber by means of a conveying device.

[0181] In one embodiment of the invention, it can be provided that the at least one conveying device has at least one section with an incline.

[0182] The conveying device is preferably only inserted or integrated into the temperature control system after the temperature control modules and the power module have been connected to each other, wherein the conveying device preferably extends through all connected modules.

[0183] In the case of a long temperature control chamber, the conveying device can also be segmented, i.e. consist of several separate sections or strands, each of which has a separate drive and, for example, a separate tensioning station.

[0184] The conveying device enables a synchronized conveying of the workpieces, in which the workpieces are optimally aligned with the circulating air introduced into the tempering chamber.

[0185] The conveying device enables the workpieces to be conveyed in the conveying direction from cycle station to cycle station.

[0186] Between two cycles, i.e. during further conveyance from one tempering module to the tempering module following in the conveying direction, each workpiece passes the laterally arranged tempering device of the power module, provided that the tempering modules are those which are directly adjacent to the power module or are connected to it.

[0187] The conveying device preferably comprises at least two conveying devices or conveying lines which are aligned at least approximately parallel to one another and parallel to the conveying direction.

[0188] The conveying device is preferably designed such that the return channel is guided below the conveying device, which is arranged closer to the temperature control device or the fan.

[0189] It may also be advantageous if the conveying device comprises a chain conveyor and / or a roller conveyor.

[0190] It may also be advantageous if at least one conveyor device is accessible.

[0191] It may be advantageous if a chain conveyor and / or a roller conveyor is provided in the heating zones and / or in the holding zones, whereas a roller conveyor may be provided in the cooling zones.

[0192] For example, one conveyor can be provided per zone or module. However, it is also possible to configure a conveyor to transport the workpieces through at least two zones or modules.

[0193] In particular, in the case of an atmospheric and / or thermal separation of two adjacent zones by one or more barrier elements, a conveying device is arranged upstream and downstream of the barrier element(s) with respect to the conveying direction.

[0194] The conveying device is therefore interrupted in the area of ​​the blocking element(s) and a transfer from the upstream conveying device to the downstream conveying device takes place when the blocking elements are in their open position.

[0195] Alternatively, a hybrid conveyor system can be provided, which is designed as a roller conveyor with a continuous conveyor chain, thus eliminating the need to change the conveyor system, especially the chain, between two zones or modules. This is particularly possible if the atmospheric and / or thermal separation between the zones is achieved by one or more airlocks.

[0196] The essentially vertical air curtain is therefore preferably formed between two cycle stations or workpieces to be treated and it is therefore not necessary to clear the area of ​​the airlock.

[0197] In the event that the free cross-sectional area below the conveyor device or the conveyor technology is not sufficient to realize a recirculating air discharge or recirculating air recirculation from the temperature control chamber between the two strands of the conveyor device, it is advantageous to achieve the required conveyor device height by guiding the conveyor chain and / or the conveyor rollers along a ramp in the area of ​​the entrance or inlet into the temperature control chamber and in the area of ​​the exit or outlet from the temperature control chamber.

[0198] This inclined travel eliminates the need for a complex lifting station at the interfaces to the preceding and subsequent conveyor device or conveyor technology.

[0199] Since one of the pressure chambers is interrupted by the temperature control device and it is therefore not possible to enter this pressure chamber unhindered for maintenance or adjustment work in the conveying direction, pressure chamber doors are provided in the housing walls and / or in the side walls of the temperature control chamber.

[0200] In the latter case, it is advantageous if the conveyors within the temperature control room are accessible. This can be achieved, for example, by using cover plates and / or gratings.

[0201] In the case of a long temperature control chamber, the conveying device can be segmented, i.e. it can consist of several separate sections or strands, each of which has a separate drive and, for example, a separate tensioning station.

[0202] A conveying device, in particular, enables the synchronized conveying of workpieces, in which the workpieces are optimally aligned with the circulating air introduced into the temperature control chamber. A conveying device thus enables the workpieces to be conveyed in the conveying direction from one cycle station to another. The conveying device preferably comprises at least two conveyor lines, which are aligned at least approximately parallel to each other and parallel to the conveying direction.

[0203] The conveying device is preferably designed such that the return channel is guided below the conveying line, which is arranged closer to the temperature control device or the fan.

[0204] By providing two different conveyors, the overall conveyor system is asymmetrical. It is preferable for the roller conveyor to be positioned closer to the temperature control device or fan, as this has a flatter overall height due to the lack of a chain on the empty side. The return channel can therefore be routed underneath the roller conveyor.

[0205] The inlet of the circulating air extraction or return, i.e. the inlet of the return channel, is preferably arranged between the roller conveyor and the chain conveyor, wherein this inlet is preferably arranged, with respect to the conveying direction, at the height of the tempering device.

[0206] In addition, it is advantageous if the chain conveyor system has so-called trolleys, which absorb the normal force when conveying the workpieces, in order to ensure low-friction and wear-free conveying, whereas the tensile force is provided via the chain of the conveyor system.

[0207] It may be advantageous if a) between the at least one conveying device and at least one side wall of the tempering chamber, preferably on the floor side on both sides of the conveying device, and / or b) between two conveying devices arranged one behind the other in the conveying direction, preferably on the floor side, and / or c) in or on the tempering chamber above the workpieces, one or more additional inlet openings, which preferably comprise nozzles or are designed as such, are arranged.

[0208] The additional inlet openings between the side walls and the conveyor system preferably comprise sill nozzles or floor nozzles for the sills of the workpieces designed as vehicle bodies, or are designed as such. Furthermore, floor nozzles can be arranged between the two strands of the conveyor system. The recirculation air is supplied by alternating pressure to opposing pressure chambers.

[0209] In the case of a conveyor device with a one-sided or two-sided conveyor chain, recesses or depressions in the floor area below the conveyor chain(s) may be required for the floor nozzles.

[0210] Alternatively, it may be necessary to raise the height of the conveyor device.

[0211] Additional inlet openings or nozzles in the ceiling or in the ceiling area of ​​the temperature control room preferably introduce recirculated air from the connecting duct between the pressure rooms into the temperature control room.

[0212] It may be advantageous if nozzles for introducing tempered circulating air are installed in the ceiling area of ​​the temperature control room, which direct or guide this circulating air towards the windscreen and / or rear window opening of a workpiece designed as a vehicle body.

[0213] Preferably, the recirculated air flows from these nozzles at an angle of approximately 45 degrees to a vertical in the direction of the windshield and / or rear window opening.

[0214] It can also be provided that a so-called sandwich ceiling is arranged below the ceiling of the temperature control room, which allows free placement of additional inlet openings or nozzles above the workpieces to be treated.

[0215] In one embodiment of the invention, it can be provided that at least one additional temperature control unit is arranged upstream of the additional inlet openings.

[0216] By placing additional temperature control units upstream of the additional inlet openings in the floor area, the heating behavior of heavy workpiece areas, such as the sills or certain floor structures of a treated vehicle body, can be accelerated. It is also advantageous if the temperature control chamber has two side walls that are aligned at least approximately parallel to each other and to the conveying direction. The side walls of the temperature control chamber have a plurality of inlet openings through which the circulating air from the pressure chambers can be introduced into the temperature control chamber.

[0217] In one embodiment of the invention, it can be provided that the inlet openings comprise nozzles or are designed as such.

[0218] The shape, size and spacing of the inlet openings to each other and / or to the edge of the side walls are preferably adaptable to the workpieces to be tempered.

[0219] Preferably, the nozzles can be aligned to predetermined areas of the workpieces.

[0220] The nozzles are particularly movable and can therefore be individually aligned.

[0221] For example, the nozzles have an outlet diameter or flow cross-section of 100 mm and can be pivoted by up to 15 degrees in one spatial direction relative to a main nozzle axis or an axis perpendicular to the respective side wall of the temperature control chamber.

[0222] Alternatively, the nozzles can also be designed as inclined nozzles with a fixed angle of, for example, 25 degrees, wherein the inclination is related in particular to the plane of the respective side wall of the temperature control chamber.

[0223] The nozzles can also be arranged in groups on the respective side wall of the temperature control chamber.

[0224] For example, four inclined nozzles can form a nozzle grouping or nozzle arrangement, which are preferably aligned to a predetermined area of ​​the workpiece to be treated.

[0225] The nozzles of such a grouping can have the same angle or different angles.

[0226] By grouping inclined nozzles, a jet or flow characteristic almost identical to that achieved with movable nozzles can be achieved without a significant increase in length in the axial direction, i.e., perpendicular from the side wall toward the temperature control chamber. Consequently, there is no need to widen the corresponding pressure chamber.

[0227] The nozzles of the opposite side walls of a cycle or zone are preferably arranged in such a way that, for example, when vehicle bodies are the workpieces to be treated, jet or flow equalization does not occur inside the vehicle body.

[0228] In this context, the cyclical operation of the temperature control system is advantageous, since this allows individual areas of the workpieces designed as vehicle bodies to be exposed to tempered circulating air in a targeted manner within a time cycle during the temporary downtime or rest period of the workpieces.

[0229] The inlet openings can have the same or different flow cross-sections.

[0230] In addition to the inlet openings in the side walls of the temperature control chamber, nozzle arrangements for the sill area of ​​workpieces designed as vehicle bodies can be arranged, for example, between the conveying device and the side walls in the floor area of ​​the temperature control chamber in order to supply the sill areas of the vehicle bodies with tempered circulating air.

[0231] Furthermore, additional floor nozzles can be arranged between the roller conveyor and the chain conveyor in order to supply the floor area and / or the interior of the vehicle bodies with tempered circulating air.

[0232] In a further embodiment of the invention, it can be provided that a plurality of filter elements are arranged upstream of the inlet openings for filtering the circulating air to be introduced into the temperature control chamber.

[0233] It may also be advantageous if at least one pressure chamber is accessible via at least one pressure chamber door for maintenance and / or adjustment work.

[0234] Due to the at least partial arrangement of the power module's temperature control device in one of the pressure chambers, this chamber is partially interrupted and therefore cannot be used as a passageway. One or more pressure chamber doors located on one of the front sides of the temperature control system are therefore not sufficient to provide access to all inlet openings and / or filter elements, for example.

[0235] It can therefore be advantageous if the pressure chamber door is arranged in a side wall of the temperature control chamber or in a housing wall of the system housing.

[0236] Preferably, each printing room is accessible via at least one printing room door.

[0237] For internal pressure chamber doors, i.e. doors in the side walls of the temperature control chamber, the access to the pressure chamber can, for example, be designed in such a way that no inlet openings are provided in the associated side wall in the area or section of the respective pressure chamber door, i.e. the arrangement of the inlet openings or nozzles in the associated side wall is interrupted in this area by a pressure-tight door which, from the perspective of the temperature control chamber, leads into the pressure chamber behind it.

[0238] Alternatively, access via internal pressure chamber doors can also be designed in such a way that the arrangement of the inlet openings or nozzles in the side walls is not interrupted during operation of the system.

[0239] For this purpose, for example, a nozzle cassette or a nozzle panel is removably arranged on the side of a print room door facing the temperature control room.

[0240] The nozzle panel can be releasably attached to the side wall surrounding the print chamber door, preferably by means of sash locks, and removed to provide access to the covered print chamber door.

[0241] The pressure chamber door itself has one or more filter elements, which are, for example, integrated into the pressure chamber door or arranged on the side facing away from the temperature control chamber, whereby they are pivoted out of their operating position when the pressure chamber door is opened.

[0242] External pressure chamber doors, i.e. doors in the housing walls of the system housing, are preferably pressure-tight and insulated.

[0243] In the event that the pressure chambers are so narrow that it is not possible to walk through them, openings are preferably provided in the side walls of the temperature control chamber through which the filter elements can initially be guided from the temperature control chamber in one orientation and then releasably fastened in their orientation for operation on the side of the respective side wall of the temperature control chamber facing away from the temperature control chamber.

[0244] The filter elements are preferably clamped against the respective side wall of the temperature control chamber, wherein a seal is preferably provided between the filter element and the support area of ​​the associated side wall, the sealing effect of which is reinforced by the contact pressure as a result of the clamping on the side wall and / or by the circulating air flow present during operation.

[0245] The mounting openings in the side walls provided for fastening the filter elements are preferably covered by the respective filter element in its operating or filtering position on the side facing away from the temperature control chamber, so that circulating air enters the respective opening at least almost exclusively through the filter element and not past the filter element.

[0246] These mounting openings are preferably covered from the direction of the temperature control chamber with a nozzle panel or a nozzle cassette as an arrangement of inlet openings, wherein these nozzle panels are preferably detachably fastened to the corresponding side wall of the temperature control chamber with sash locks.

[0247] To ensure that as little or at least almost no circulating air as possible can flow past a nozzle panel into the temperature control chamber, a nozzle panel, for example, has a circumferential V-shaped edge which, when inserted in the side wall, points away from the temperature control chamber.

[0248] In addition, the corresponding opening in the side wall of the temperature control chamber has a corresponding circumferential, V-shaped receptacle into which the V-shaped edge of the nozzle panel can engage.

[0249] The circulating air flowing from the pressure chamber against the nozzle panel thus largely gets caught in the edge area of ​​the nozzle panel and does not flow past it into the temperature control chamber.

[0250] A suitably designed seal and / or a sealing lubricant can be arranged between the opening receptacle and the edge of a nozzle panel, or applied to at least one of the contact surfaces. In the case of a pressure chamber that is reduced in width, i.e., perpendicular to the conveying direction, this can lead to unwanted heat input from a temperature control unit into the respective pressure chamber. It can therefore be advantageous if the temperature control unit is thermally insulated, at least in sections, in the direction of the inlet openings to prevent local overheating of the circulating air passing through the pressure chamber.

[0251] Preferably, in the power module, the area between the temperature control units and the fan on the one hand and the temperature control chamber on the other hand is thermally insulated.

[0252] In particular, the area of ​​undercut chambers is thermally insulated in such a way that no circulating air, which is directed to the nozzles of an undercut chamber, is overheated by one or more temperature control units of the power module.

[0253] In the case of narrow, particularly non-accessible pressure chambers of the temperature control modules, the power module protrudes beyond the temperature control modules on both sides in the width direction, i.e. transverse to the conveying direction.

[0254] Given that the temperature control device is located in the power module, the temperature control modules are preferably dimensioned and configured so that each temperature control module can be transported as a flat pack in an open-top container without a conveyor system for sea transport. For this purpose, a temperature control module can be disassembled into two parts by folding or swiveling the module cover onto one of the two pressure chambers and the module base onto the other pressure chamber. The width of these two packages is preferably less than or equal to the maximum clear width of the open-top container.

[0255] In one embodiment of the invention, inlet openings or nozzles can be provided in areas of the side walls of the temperature control chamber where, due to space constraints, no filter elements can be installed upstream of these inlet openings, such as in the area of ​​the fan or in the area of ​​a pressure chamber door in the housing wall of the system housing. In this case, such filter-free inlet openings are supplied with filtered recirculating air from at least one of the adjacent pressure chambers or pressure chamber sections.

[0256] In one embodiment of the invention, it can be provided that all pressure chambers are accessible for maintenance and / or adjustment work via two pressure chamber doors per temperature control device, which are arranged, with respect to the conveying direction, upstream and downstream of the temperature control device.

[0257] This means that all areas of a pressure chamber are accessible, even if a temperature control device is at least partially located in a pressure chamber.

[0258] Preferably, no filter elements are provided in the area of ​​the power module.

[0259] Furthermore, it can be provided that at least one temperature sensor is arranged in the temperature control system, preferably in the temperature control room and / or in the pressure rooms, in order to determine and / or monitor the circulating air temperature.

[0260] The object of the present invention is further achieved by a method for tempering workpieces, in particular for heating vehicle bodies, in a tempering system.

[0261] The method preferably has one or more of the features and / or advantages described in connection with the temperature control system. Furthermore, the temperature control system preferably has one or more of the features and / or advantages described in connection with the method.

[0262] The method according to the invention comprises the following steps:

[0263] Supplying heating gas to an intake chamber upstream of a fan of the at least one temperature control device, wherein the fan is arranged at least partially in a first pressure chamber of the temperature control system;

[0264] Providing tempered recirculating air downstream of the fan;

[0265] Introducing tempered circulating air into the temperature control chamber via the first pressure chamber, which is arranged on one side of the temperature control chamber, and a second pressure chamber of the temperature control system, which is arranged on the other side of the temperature control chamber and is fluidly connected to the first pressure chamber;

[0266] Tempering the workpieces conveyed through the tempering chamber; and extracting the circulating air from the tempering chamber using the fan.

[0267] Further preferred features and / or advantages of the invention are the subject of the following description and the drawings of exemplary embodiments. The figures show:

[0268] Fig. 1 is a schematic, perspective view of a first embodiment of a temperature control system according to the invention;

[0269] Fig. 2 is a further schematic perspective view of the first embodiment of Fig. 1;

[0270] Fig. 3 is a schematic horizontal longitudinal section of the first embodiment of Fig. 1;

[0271] Fig. 4 is a schematic vertical cross-section of the first embodiment of Fig. 1;

[0272] Fig. 5 is a schematic vertical cross-section of a second embodiment of a temperature control system according to the invention;

[0273] Fig. 6 is a schematic representation of a first embodiment of a heating zone;

[0274] Fig. 7 is a schematic representation of a second embodiment of a heating zone;

[0275] Fig. 8 is a schematic representation of a first embodiment of a holding zone; and

[0276] Fig. 9 is a schematic representation of a second embodiment of a holding zone.

[0277] Identical or functionally equivalent elements are provided with the same reference numerals in all figures.

[0278] A first embodiment of a tempering system designated as a whole by 100, shown in Fig. 1 and 2, is used for tempering workpieces (not shown).

[0279] The temperature control system 100 is, in particular, a system for heating vehicle bodies (not shown). The workpieces are conveyed in the temperature control system 100 along a conveying direction 102.

[0280] Preferably, the workpieces designed as vehicle bodies are conveyed in their longitudinal direction along the conveying direction 102 through the tempering system 100.

[0281] The temperature control system 100 comprises at least two temperature control modules 104, which are arranged one behind the other in the conveying direction 102, and at least one power module 105, which is arranged between the two temperature control modules 102 and connects them to one another.

[0282] The temperature control modules 104 and the power module 105 together form a continuous temperature control chamber 106. The workpieces can be conveyed into the temperature control chamber 106, through the temperature control chamber 106, and out of the temperature control chamber 106 again.

[0283] The temperature control modules 104 further form a pressure chamber 108 on each side of the temperature control chamber 106, via which circulating air can be introduced into the temperature control chamber 106.

[0284] The pressure chambers 108 are fluidly connected to one another by means of a connecting channel 110 of the power module 105 or a connecting chamber of the power module 105.

[0285] The connecting channel 110 can be arranged as a cover channel on one or both temperature control modules 104. However, it is also conceivable that the connecting channel 110 is designed as an intermediate ceiling within the power module 105 and / or one of the temperature control modules 104.

[0286] The connecting channel 110 is preferably arranged centrally in the temperature control chamber 106 with respect to the conveying direction 102.

[0287] The power module 105 further comprises a temperature control device 114, by means of which at least a portion of the circulating air guided through the temperature control chamber 106 can be temperature-controlled, ie, in particular, heated and / or cooled. A temperature control device 114 is also arranged on one side of the temperature control chamber 106; the arrangement of the temperature control device 114 is thus asymmetrical.

[0288] The lateral integration of the temperature control device 114 in the power module 105, ie the at least partial arrangement of the temperature control device 114 in one of the pressure chambers 108, enables a particularly compact design of the temperature control system 100.

[0289] The tempering device 114 serves to circulate and temper the circulating air conveyed through the tempering chamber 106.

[0290] In the two side walls 116 of the temperature control chamber 106, a plurality of inlet openings 118 are provided, through which the circulating air is introduced into the temperature control chamber 106.

[0291] The inlet openings 118 may have different and / or identical shapes and sizes.

[0292] The shape, size and spacing of the inlet openings 118 to each other and / or to the edge of the side walls 116 can be adapted to the workpieces to be tempered.

[0293] In the floor area of ​​the temperature control chamber 106, a conveying device 120 is arranged, which conveys the workpieces through the temperature control chamber 106.

[0294] The tempering device 114 comprises a fan 122 (shown in Fig. 4) which is driven by a motor 124.

[0295] The motor 124 is preferably designed as an electric motor 125.

[0296] The motor 124 is arranged at least partially outside the two temperature control modules 104.

[0297] The motor 124 of the temperature control device 124 projects beyond the temperature control modules 104 in the direction of a width 126 of the temperature control modules 104 or the temperature control system 100, wherein the width 126 of the temperature control modules 104 or the temperature control system 100 is preferably oriented horizontally and perpendicular to the conveying direction 102. The motor 124 projects beyond the width 126 of the temperature control modules 104, preferably by less than approximately 25%, preferably 20%, and particularly preferably 10% of the width 126 of the temperature control modules 104, so that the temperature control system 100 is designed to save space in the direction of the width 126.

[0298] The connecting duct 110 is preferably approximately as wide as the diameter of the fan in the conveying direction 102, so that tempered circulating air can be passed over to the other side of the tempering chamber 106 without changing the flow cross-section.

[0299] Fig. 3 shows a schematic horizontal longitudinal section of the first embodiment from Figs. 1 and 2.

[0300] In this longitudinal sectional view, it can be seen in detail that the conveying device 120 is arranged on the floor side of the tempering chamber 106, which comprises a chain conveyor device 128 and a roller conveyor device 130 or can be designed as such.

[0301] The roller conveyor 130 is arranged on the side of the conveyor device 120 that is closer to or facing the temperature control device 114 or the fan 122. Consequently, the chain conveyor 128 is arranged on the side of the conveyor device 120 that is farther away from the temperature control device 114 or the fan 122.

[0302] The circulating air is discharged from the temperature control chamber 106 via a return duct 132, wherein a return duct inlet 134 is arranged, with respect to the conveying direction 102, centrally between the temperature control modules 104 and between the chain conveyor device 128 and the roller conveyor device 130.

[0303] The return channel 132 is preferably arranged on the bottom side and is preferably guided under the roller conveyor device 130.

[0304] The return channel 132 comprises an outlet section 136, which connects the return channel 132 to the pressure chamber 108, in which the temperature control device 114 is integrated.

[0305] The flow cross-section of the outlet section 136 of the return channel 132 increases in the direction of the temperature control device 114, preferably at least approximately to the inlet flow cross-section of the fan 122, whereby an improved flow to the fan 122 is achieved.

[0306] In the pressure chambers 108, filter elements 138 are also arranged upstream of the inlet openings 118, which filter the circulating air before it is introduced into the temperature control chamber 106.

[0307] In Fig. 4, which shows a schematic, vertical cross-section of the first embodiment of a temperature control system 100 according to the invention, it can also be seen that upstream of the fan 122, which is preferably designed as a radial fan 140, an intake chamber 142 is arranged, which adjoins the outlet section 136 of the return channel 132.

[0308] The intake chamber 142 is formed by a transition duct element 144, since the fan 122 is set back with respect to the direction of the width 126. This transition duct element 144 is connected to an intake nozzle 146 of the fan 122.

[0309] Heating gas 150 is supplied to the intake chamber 142 via a branch line 148, which in turn is supplied to the temperature control system 100 from a heat source via a heating gas supply line 152.

[0310] The heating gas supply line 152 is arranged as a channel with a triangular cross-section in an upper corner of the temperature control chamber 106, which is closer to the fan, and is further insulated from the temperature control chamber 106 in order to prevent any heat energy from the heating gas 150 from being introduced directly into the temperature control chamber 106.

[0311] The branch line 148 preferably introduces the heating gas 150 up to the height of the center of the intake nozzle 146.

[0312] The heating gas 150 is mixed with the circulating air in the fan 122.

[0313] The tempered or heated circulating air is then radially discharged by the fan 122 into a circulating air distribution chamber 154, which divides the surrounding pressure chamber 108 into two sections. From there, the tempered circulating air is directed firstly into the two adjacent pressure chamber sections and secondly into the connecting duct 110. The volume flow of the heating gas 150 supplied to the fan 122 is controlled and / or regulated via a throttle device 156 arranged in the branch line 148.

[0314] The throttle device 156 is connected via a drive shaft 158 ​​to a servo motor 160, which adjusts the throttle device 156.

[0315] The servo motor 160 is preferably arranged outside the temperature control modules 104 and above the motor 124, whereby it does not project outwards beyond the motor 124 in the direction of the width 126.

[0316] The heating gas 150 passed through the temperature control system 100 is preferably led out of the temperature control system 100 by means of a heating gas return line 162 for reheating back to the heat source.

[0317] The heating gas return line 162 is preferably also designed as a triangular channel and arranged in the other upper corner of the temperature control chamber 106.

[0318] The volume flow of the returned heating gas 150 is also controlled and / or regulated by means of a further throttle device (not shown).

[0319] Fig. 4 also shows the annular guidance of the circulating air through the temperature control system 100, which will be described again in detail below.

[0320] The fan is surrounded by a recirculation air distribution chamber 164, which divides the surrounding pressure chamber 108 into two pressure chamber sections, from which the tempered recirculation air ejected radially from the fan 122, i.e. the recirculation air mixed with the heating gas 150, is guided into the two adjacent pressure chamber sections and the connecting duct 110.

[0321] A portion of the circulating air, preferably approximately 50% of the circulating air, is conveyed into the pressure chamber 108, in which the temperature control device 114 is at least partially integrated, whereas the other portion, preferably approximately 50% of the circulating air, is conveyed via the connecting channel 110 into the pressure chamber 108, which is arranged on the other side of the temperature control chamber 106. From the pressure chambers 108, the circulating air, after being filtered in the filter elements 138, is introduced into the temperature control chamber 106 via the inlet openings 118, which are arranged in the side walls 116 of the temperature control chamber 106, in order to temperature control, in particular to heat, the workpieces conveyed through the temperature control chamber 106 along the conveying direction 102.

[0322] From the temperature control chamber 106, the circulating air is sucked in by the fan 122 via the return duct 132; the sucked-in circulating air passes via the return duct 132 into the outlet section 136 of the return duct 132.

[0323] From the outlet section 136 of the return duct 132, the circulating air is led into the intake chamber 142, where heating gas 150 from the heating gas supply line 152 is added via the branch line 148 in order to increase the temperature of the intake circulating air.

[0324] Intaken circulating air and added heating gas 150 are mixed in the fan 122 and then guided or ejected radially into the circulating air distribution chamber 164.

[0325] Fig. 5 shows a schematic, vertical cross-section of a second embodiment of a temperature control system 100 according to the invention, which differs from the first embodiment in that the heating gas supply line 152 and the heating gas return line 162 are arranged above the temperature control chamber 106, preferably between the temperature control chamber 106 and the connecting channel 110. The two lines 152, 162 have a rectangular cross-section and can be insulated from the environment of the temperature control system 100.

[0326] Fig. 6 schematically shows a first embodiment of a heating zone 166 of the tempering system 100, which is preferably intended for workpieces designed as vehicle bodies with a length of up to 5 m.

[0327] The schematic heating zone 166 comprises two cycle stations 168, on which the vehicle bodies are temporarily positioned or remain for tempering with circulating air before they are conveyed to the next cycle station 168 or to the next zone of the tempering system 100 in the conveying direction 102.

[0328] A cycle station for vehicle bodies of up to 5 m preferably has an extension in the conveying direction 102 of 5.5 m, whereby the heating zone 166 shown in Fig. 6 has a total longitudinal extension of 11 m. Fig. 7 schematically shows a second embodiment of the heating zone 166, which is intended for longer workpieces, in particular for vehicle bodies with a length of up to 6 m.

[0329] In order to avoid having to modify the power module 105 and the adjacent tempering modules 104 for the longer vehicle bodies, an intermediate module 170 is added at the beginning and end of the heating zone 166 to realize sufficiently long cycle stations 168, relative to the conveying direction 102.

[0330] An intermediate module 170 for a heating zone 166 preferably has a longitudinal extension of 1 m.

[0331] The cycle stations 168 thus each have an extension in the conveying direction 102 of 6.5 m and the heating zone 166 is thereby extended to a total longitudinal extension of 13 m.

[0332] In Fig. 8, a first embodiment of a holding zone 172 is also shown schematically, which is intended in particular for vehicle bodies with a length of up to 5 m.

[0333] A holding zone 172 preferably has four temperature control modules 104 and a power module 105.

[0334] The two outer temperature control modules 104 each provide a clock position 168, whereas the temperature control modules 104 adjacent to the power module 105 each provide a clock position 168 together with the power module 105.

[0335] Consequently, the extension of the two outer temperature control modules 104 in the conveying direction 102 is 5.5 m each and that of the two inner temperature control modules 104 together with the power module 105 is 11 m, whereby the holding zone 172 shown in Fig. 8 has a total longitudinal extension of 22 m.

[0336] In Fig. 9, a second embodiment of a holding zone 172 is schematically shown, comparable to the second embodiment of a heating zone 166 according to Fig. 7. The second embodiment of a holding zone 172 of a temperature control system 100 is intended in particular for vehicle bodies with a length of up to 6 m.

[0337] To extend the cycle stations 168, an intermediate module 170 is also added at the beginning and at the end of the holding zone 172, relative to the conveying direction 102, wherein an intermediate module 170 for a holding zone 172 preferably has an extension in the conveying direction 102 of 2 m.

[0338] This also results in cycle stations 168 each having an extension in the conveying direction 102 of 6.5 m. Thus, the second embodiment of a holding zone 172 for vehicle bodies of up to 6 m has a total extension in the conveying direction 102 of 26 m.

[0339] From the first and second embodiments of a heating zone 166 and a holding zone 172, respectively, according to Figs. 6 to 9, it can be seen that the temperature control system 100 is preferably modulatable such that two temperature control modules 104 or two temperature control modules 104 and one power module 105 do not exceed a length of 11 m, whereby these module combinations can preferably be transported with a 40' flat rack or a 40' open top container or a 40' high cube container.

[0340] List of reference symbols

[0341] Temperature control system Conveying direction Temperature control module Power module Temperature control chamber Pressure chamber Connecting channel Temperature control device Side wall Inlet opening Conveying device Fan Motor Electric motor Width

[0342] Chain conveyor system Roller conveyor system Return channel

[0343] Return duct inlet Outlet section Filter element Radial fan Intake chamber Transition duct element Intake nozzle Branch line Heating gas Heating gas supply line Recirculation air distribution chamber Throttle device Drive shaft Actuator

[0344] Heating gas return line Recirculating air distribution room Heating zone Cycle station Intermediate module Holding zone

Claims

Patent claims 1. A tempering system (100) for tempering workpieces, in particular for heating vehicle bodies, wherein the tempering system (100) comprises: at least two tempering modules (104) arranged one behind the other in a conveying direction (102); and at least one power module (105) for circulating and tempering circulating air, which is arranged at least in sections between the at least two tempering modules (104), wherein the at least two tempering modules (104) and the at least one power module (105) form a tempering chamber (106) through which the workpieces can be conveyed along the conveying direction (102) for tempering with circulating air.

2. Temperature control system (100) according to claim 1, characterized in that the temperature control system (100) has at least one system housing which delimits the temperature control modules (104) and / or the power module (105) from an environment of the temperature control system (100) or encloses them.

3. Temperature control system (100) according to claim 1 or 2, characterized in that the at least one power module (105) comprises at least one temperature control device (114).

4. Temperature control system (100) according to claim 3, characterized in that the at least one temperature control device (114) is arranged laterally on the temperature control chamber (106) with respect to the conveying direction (102), and wherein it is preferably provided that the at least one temperature control device (114) is arranged approximately in the region of the center of the temperature control chamber (106) with respect to the conveying direction (102).

5. Temperature control system (100) according to one of claims 1 to 4, characterized in that the at least one power module (105) comprises a connecting channel (110) and / or a connecting space.

6. Temperature control system (100) according to one of claims 3 to 5, characterized in that the at least one temperature control device (114) comprises at least one fan (122), which, for example, comprises a fan axis aligned horizontally and / or perpendicular to the conveying direction (102) and / or is designed as a radial fan (140).

7. Temperature control system (100) according to claim 6, characterized in that an intake chamber (142) is arranged upstream of the fan (122).

8. Temperature control system (100) according to claim 7, characterized in that a heating gas (150) can be supplied to the suction chamber (142).

9. Tempering system (100) according to one of claims 1 to 8, characterized in that the tempering system (100) has at least two zones of different temperatures along the conveying direction (102).

10. Tempering system (100) according to one of claims 1 to 9, characterized in that the tempering system (100) has at least one heating zone (166) and / or at least one holding zone (172).

11. Temperature control system (100) according to claim 10, characterized in that the fans (122) of the heating zones (150) and the holding zones (156) are at least approximately equally dimensioned.

12. Temperature control system (100) according to one of claims 9 to 11, characterized in that the zones can be atmospherically and / or thermally separated from one another and / or from an environment of the temperature control system (100) by a) one or more blocking elements and / or b) one or more airlocks.

13. Temperature control system (100) according to one of claims 1 to 12, characterized in that between each two modules (104, 105) at least one compensation device is provided for absorbing the thermal expansion in the conveying direction.

14. Temperature control system (100) according to one of claims 1 to 13, characterized in that at least one temperature control module (104) and / or at least one power module (105) is / are mounted on at least one fixed base, wherein the fixed base is preferably arranged below the respective module (104, 105).

15. Tempering system (100) according to one of claims 10 to 14, characterized in that the at least one heating zone (166) comprises two tempering modules (104) and a power module (105), wherein the at least one heating zone (166) optionally comprises at least two intermediate modules (170) for extending the tempering chamber (106).

16. Temperature control system (100) according to one of claims 10 to 15, characterized in that the at least one holding zone (172) comprises four temperature control modules (104) and a power module (105) which, with respect to the conveying direction (102), is preferably arranged centrally of the at least one holding zone (172), wherein optionally the at least one holding zone (172) comprises at least two intermediate modules (170) for extending the temperature control space (106).

17. Tempering system (100) according to one of claims 10 to 16, characterized in that the at least one heating zone (166) in the conveying direction (102) has an extension of a) 9 m to 12 m, preferably 11 m, or b) 12 m to 14 m, preferably 13 m.

18. Temperature control system (100) according to one of claims 10 to 17, characterized in that the at least one holding zone (172) has an extension of a) 20 m to 24 m, preferably 22 m, or b) 24 m to 28 m, preferably 26 m, in the conveying direction (102).

19. Temperature control system (100) according to one of claims 8 to 18, characterized in that the heating gas (150) can be fed to the suction chamber (142) by means of a branch line (148), preferably a vertical branch line.

20. Temperature control system (100) according to claim 19, characterized in that the branch line (148) is fluidly connected to a heating gas supply line (152), in particular a horizontal heating gas supply line, by means of which heating gas (150) from a heat source can be supplied to the temperature control system (100).

21. Temperature control system (100) according to claim 20, characterized in that the heating gas supply line (152) can be arranged inside the temperature control chamber (106) or outside the temperature control chamber (106).

22. Temperature control system (100) according to one of claims 19 to 21, characterized in that a throttle device (156) for controlling and / or regulating the volume flow of the heating gas (150) is provided in the branch line (148), wherein it is preferably provided that the throttle device (156) is adjustable by means of a servo motor (160) which is arranged outside the at least two temperature control modules (104) and outside the at least one power module (105).

23. Temperature control system (100) according to one of claims 20 to 22, characterized in that the temperature control system (100) has a heating gas return line (162), in particular a horizontal heating gas return line, by means of which heating gas (150) from the temperature control system (100) can be returned to the heat source.

24. Temperature control system (100) according to claim 23, characterized in that the heating gas return line (162) can be arranged inside the temperature control chamber (106) or outside the temperature control chamber (106).

25. Temperature control system (100) according to one of claims 1 to 24, characterized in that a pressure chamber (108) is formed on each of the two sides of the temperature control chamber (106), via which the circulating air can be introduced into the temperature control chamber (106).

26. Temperature control system (100) according to claim 25, characterized in that the at least one temperature control device (114) is arranged at least in sections in a pressure chamber (108).

27. Temperature control system (100) according to claim 25 or 26, characterized in that the pressure chambers (108) are fluidly connected to one another by means of the connecting channel (110) and / or the connecting chamber.

28. Tempering system (100) according to one of claims 3 to 27, characterized in that the at least one tempering device (114) projects beyond a width (126) of the tempering modules (104), which is preferably aligned horizontally and perpendicular to the conveying direction (102), by less than approximately 25%, preferably 20% and particularly preferably 10% of the width (126) of the tempering modules (104).

29. Temperature control system (100) according to one of claims 16 to 28, characterized in that the at least one temperature control device (114) comprises a motor (124), in particular an electric motor, which drives the fan (122), wherein it is preferably provided that the motor (124) is arranged at least approximately completely outside the temperature control modules (104).

30. Temperature control system (100) according to one of claims 1 to 29, characterized in that the circulating air can be discharged from the temperature control chamber (106) on the floor side, wherein the circulating air can preferably be discharged on one or both sides of the temperature control chamber (106) and / or, with respect to the conveying direction (102), centrally from the temperature control chamber (106).

31. Temperature control system (100) according to claims 1 to 30, characterized in that the circulating air from the temperature control chamber (106) can be discharged from the temperature control chamber (106) by means of a return channel (132), wherein the return channel (132) is preferably designed to be funnel-shaped at least in sections on the outlet side in order to increase the flow cross-section.

32. Temperature control system (100) according to claim 31, characterized in that the circulating air from the return channel (132) can be discharged at least in sections obliquely upwards.

33. Temperature control system (100) according to claim 31 or 32, characterized in that the suction chamber (142) is arranged between the fan (122) and the return duct (132).

34. Temperature control system (100) according to one of claims 16 to 33, characterized in that the connecting channel (110) and / or the connecting space has a width taken in the horizontal direction and parallel to the conveying direction (102), which at least approximately corresponds to the extension of the fan (122) in the conveying direction (102).

35. Tempering system (100) according to one of claims 1 to 34, characterized in that the workpieces can be conveyed through the tempering chamber (106) by means of a conveying device (120).

36. Temperature control system (100) according to claim 35, characterized in that the at least one conveying device (120) has at least one section with an incline.

37. Tempering system (100) according to claim 35 or 36, characterized in that the conveying device (120) comprises a chain conveyor device (128) and / or a roller conveyor device (130).

38. Temperature control system (100) according to one of claims 35 to 37, characterized in that the at least one conveying device (120) is walkable.

39. Temperature control system (100) according to one of claims 25 to 38, characterized in that the temperature control chamber (106) has two side walls (116) which are aligned at least approximately parallel to one another and to the conveying direction (102), wherein the side walls (116) of the temperature control chamber (106) have a plurality of inlet openings (118) via which the circulating air from the pressure chambers (108) can be introduced into the temperature control chamber (106).

40. Tempering system (100) according to claim 39, characterized in that the inlet openings (118) comprise nozzles or are designed as such, wherein the nozzles are preferably alignable to predetermined areas of the workpieces.

41. Temperature control system (100) according to one of claims 35 to 40, characterized in that a) between the at least one conveying device (120) and at least one side wall (122) of the temperature control chamber (106), preferably at the bottom on both sides of the conveying device (120), and / or b) between each two conveying devices (120) arranged one behind the other in the conveying direction (102), preferably at the bottom, and / or c) in or on the tempering chamber (106) above the workpieces, one or more additional inlet openings, which preferably comprise nozzles or are designed as such, are arranged.

42. Temperature control system (100) according to claim 41, characterized in that at least one additional temperature control unit is arranged upstream of the additional inlet openings.

43. Temperature control system (100) according to one of claims 39 to 42, characterized in that a plurality of filter elements (138) for filtering the circulating air to be introduced into the temperature control chamber (106) are arranged upstream of the inlet openings (118).

44. Temperature control system (100) according to one of claims 25 to 43, characterized in that at least one pressure chamber (108) is accessible via at least one pressure chamber door for maintenance and / or adjustment work.

45. Temperature control system (100) according to claim 44, characterized in that the pressure chamber door is arranged in a side wall (122) of the temperature control chamber (106) or a housing wall of the system housing (124).

46. ​​Temperature control system (100) according to claim 44 or 45, characterized in that all pressure chambers (108) are accessible for maintenance and / or adjustment work via two pressure chamber doors per temperature control device (114), which, with respect to the conveying direction (102), are arranged upstream and downstream of the temperature control device (114).

47. Method for tempering workpieces, in particular for heating vehicle bodies, in a tempering system (100), in particular a tempering system (100) according to one of claims 1 to 46, wherein the tempering system (100) comprises the following: at least two tempering modules (104) which are arranged one behind the other in a conveying direction (102); and at least one power module (105) for circulating and tempering circulating air, which is arranged at least in sections between the at least two Tempering modules (104) are arranged and have at least one tempering device (114), wherein the at least two tempering modules (104) and the at least one power module (105) form a tempering chamber (106) through which the workpieces can be conveyed for tempering with circulating air along the conveying direction (102), and wherein the method comprises the following steps: Supplying heating gas (150) to an intake chamber (142) upstream of a fan (122) of the at least one temperature control device (114), wherein the fan (122) is arranged at least in sections in a first pressure chamber (108) of the temperature control system (100); Providing tempered circulating air downstream of the fan (122); Introducing tempered circulating air into the tempering chamber (106) via the first pressure chamber (108), which is arranged on one side of the tempering chamber (106), and a second pressure chamber (108) of the tempering system (100), which is arranged on the other side of the tempering chamber (106) and is fluidly connected to the first pressure chamber (108); Tempering the workpieces conveyed through the tempering chamber (106); and extracting the circulating air from the tempering chamber (106) by means of the fan (122).

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