DE102017103633A1 - heat pump - Google Patents

Abstract

The invention relates to a heat pump (1) with at least one heat exchanger (15) and with at least one channel (3) which is designed to lead away a process air (S) from the heat exchanger (15), wherein the channel (3) has at least one air guide rib (36), which is designed to divide the channel (3) at least in sections into a first sub-channel (30) and into a second sub-channel (33), the first sub-channel (30) being formed, a portion of the process air (S ) via an input (31) of the heat exchanger (15) lead away, and wherein the second sub-channel (33) is adapted to carry away a portion of the process air (S) via an input (34) of the heat exchanger (15). The heat pump (1) is characterized in that the width (Bwü1) of the input (31) of the first sub-channel (30) is at least twice as large as the width (Bwü2) of the input (34) of the second sub-channel (33), and or that the cross-sectional area (Awü1) of the inlet (31) of the first sub-channel (30) is at least twice as large as the cross-sectional area (Awü2) of the inlet (34) of the second sub-channel (33).

Description

The invention relates to a heat pump according to the preamble of patent claim 1 and a heat pump device with such a heat pump according to claim 13.

In many electrical appliances today is paid by the user very much on energy efficiency, so that the energy efficiency of an electrical device in operation can be a major factor in the purchase decision of the user as an end customer. Therefore, many electrical appliances are labeled with the corresponding statutory energy labels, which indicate energy efficiency during operation as an important parameter. This also applies to household appliances in general and in particular household appliances such. Dryers, which may have a comparatively high energy consumption during operation.

In order to achieve the highest possible energy efficiency in operation especially in tumble dryers, these are usually designed as a heat pump dryer, since heat pumps can be operated in principle comparatively energy efficient. Heat pump laundry dryers are therefore widely used on the market.

A heat pump basically consists of a closed heat pump cycle with a compressor (also called a compressor), a condenser (also called a condenser), a throttle such as a compressor. an expansion valve or a capillary and an evaporator. These elements can also be referred to as a refrigeration circuit or heat pump cycle. Through this heat pump cycle, the process air of the clothes dryer can be removed from the moisture that was previously removed from the laundry.

From the point of view of the drying process or the laundry drum, this is considered to be the one previously dehumidified and heated by the heat pump cycle, i. dried and heated process air passed through a rear air duct of a fan of the heat pump cycle through an air supply duct in a laundry drum of the clothes dryer. In the laundry drum, the laundry to be dried is usually moved by means of a drum drive by rotation, so that the process air can reach the laundry as completely and uniformly as possible. The process air absorbs moisture from the laundry and dries it. The moist process air then passes back through an air return duct to a front air duct of the heat pump cycle.

Within the heat pump, the moisture extracted from the process air is condensed in the evaporator and discharged to the outside in liquid form. The energy extracted from the process air is then returned to the process air through the condenser, so that the process air can again dehumidify and, when heated, leave the heat pump cycle in the direction of the laundry drum. The cycle of process air is closed in this way.

The heat pump cycle as a central functional unit of the heat pump usually has fins, which are provided both on the evaporator as evaporator heat exchanger and the condenser as Verflüssigerwärmeübertrager. In the case of both heat exchangers, which can also be referred to as heat exchangers, it is usually possible by design to ensure that a flow of the process air takes place only parallel to the orientation of the lamellae and that there is no exchange perpendicular to the lamellae planes.

Usually, the heat pump cycle, together with other components such as e.g. the drum drive or a condensate pump, disposed on a floor module assembly of the tumble dryer, wherein the base for this assembly is usually formed by a large plastic component with an associated lid. For most manufacturers, the arrangement has prevailed here, that the moist process air fed from the laundry drum by the air return duct through the front air duct flows from the front into the floor module from the user's point of view and then flows first through the evaporator heat exchanger and then through the condenser heat exchanger. The dried and heated process air then passes through a channel to the process air blower, which leads the process air through the rear air duct back to the air supply channel of the laundry drum.

Mainly for cost reasons, the process air blower usually does not have its own drive motor, but is arranged on the extended shaft of the drum drive. The advantage here is that this design principle due to the saving of a separate drive motor for the blower can be cheaper, because material costs and installation costs can be reduced. Also, the space of a separate drive motor can be saved.

The disadvantage here, however, that in such an internally driven process air blower, the impeller can not be arranged in alignment with the heat exchangers but only in the axial direction of the drum drive shaft. Accordingly, the channel of the floor module, which supplies the process air from the condenser heat exchanger to the Process air blower leads, having a curved geometry, which first deflects the process air after the heat exchangers to one side to the process air blower and then leads in an opposite deflection to the impeller back.

The disadvantage here is, on the one hand, that this can lead to additional design complexity and to restrictions in the design of the course of the process air cycle or in the arrangement of the components of the heat pump cycle and the process air cycle.

It is also particularly disadvantageous that pressure differences across the width of the heat exchangers can result due to the deflected course of the channel, which can lead to the heat exchangers not being flowed through uniformly. Thus, depending on the configuration of the refrigeration circuit, it may occur that the highest flow velocity occurs at the fins of the condenser heat exchanger which are closest to the process air blower. The flow rate decreases continuously in width with increasing distance from the fan. This effect can be stronger, the greater the ratio between width and depth of the heat exchanger. The disadvantage here is that an uneven flow of the heat exchanger can have a negative effect on its usable heat transfer performance and thus also on the efficiency of the entire heat pump process.

In order to achieve a further improvement in energy efficiency, especially in high-priced devices, it may be a starting point to further increase the heat exchangers, to allow even better heat transfer between the refrigerant and process air than before. However, the basic dimensions of the devices should or can not usually be changed. Furthermore, the maximum possible heights and depths of the heat exchangers in the existing installation space are usually almost exhausted, so that only by optimizing the component arrangement can there still exist some potential in the width of the heat exchangers. An increase in the width of the heat exchanger, in addition to increasing the possible transmission power have the further advantage that reduced by the larger flow cross-sectional area of the flow resistance and thus less fan power may be needed to promote the same process air volume flow, which may also have a positive effect on energy efficiency ,

The disadvantage here, however, be that the unevenness of the flow of the heat exchanger can be stronger by a larger width of the heat exchanger. This can at least partially offset the targeted increase in energy efficiency.

To make matters worse, in heat pump modules to differentiate the devices increasingly variants are formed. Especially devices in the entry-level segment usually do not have the highest possible energy efficiency, but are equipped for reasons of economy with smaller-sized heat exchangers, which are cheaper to produce due to the lower material usage. In order to keep the flow resistance low, the smaller sized heat exchangers are not reduced in width but in depth, so that even in these variants, the above-described irregularities of flow through the heat exchanger occur and even further by the reduced depth and thus reduced flow resistance can be strengthened.

The EP 2 628 845 A1 relates to a tumble dryer or a washing machine with a drying function, wherein the drying of the laundry takes place via process air. In any case, a heat exchanger is used to dry and then heat the process air. To increase energy efficiency at least two very long Luftleitrippen are arranged in the channel between the heat exchangers and the fan, which run almost the entire length of the channel. This is to achieve a more uniform flow through the heat exchanger and energy efficiency can be increased.

A disadvantage is the at least two air guide ribs of the EP 2 628 845 A1 in that their geometry is problematic from a plastics engineering point of view. The small distance between the Luftleitrippen over a large length can make the tool cooling difficult and expensive while promoting a strong component distortion.

A further disadvantage is that the channel of the heat pump module of EP 2 628 845 A1 due to production is formed from a lower part and an upper part. The Luftleitrippen can either be formed on one side of one of these two parts, but this can further increase the tendency to delay due to the then very large rib height. Alternatively, the Luftleitrippen can be formed in half each of the upper and lower part, which it can make it difficult over the long length of the channel, however, to mount both ribs congruent to each other despite the draft tendency. Alternatively, to realize the air guide ribs as an additional component which is used in an existing floor module, may also be disadvantageous, because in this way an additional component is created, which can lead to additional manufacturing and assembly steps with corresponding costs.

The invention thus provides the problem of providing a heat pump of the type described above, which has a more uniform flow through the heat exchanger than previously known and at the same time easier to manufacture than previously known and / or to assemble. As a result, the process air volume flow is better distributed over the entire cross section of the heat exchanger than previously known, in order to increase the energy efficiency of the heat pump. In particular, the speed peak at the fan closest to the fins should at least be reduced. This should preferably be made possible with heat pumps whose heat exchangers are wider than previously customary.

According to the invention this problem is solved by a heat pump with the features of claim 1 and by a heat pump device with the features of claim 13. Advantageous embodiments and further developments of the invention will become apparent from the following subclaims.

Thus, the present invention relates to a heat pump with at least one heat exchanger and with at least one channel, which is designed to carry away a process air from the heat exchanger. The heat exchanger can also be referred to as a heat exchanger and preferably be designed in the form of a multiplicity of lamellae, which can be flowed around along their surfaces by the process air.

The channel has at least one air guide rib, which is designed to divide the channel at least in sections into a first sub-channel and into a second sub-channel, wherein the first sub-channel is designed to lead away a portion of the process air via an input from the heat exchanger, and wherein the second sub-channel is designed to carry away a portion of the process air via an input from the heat exchanger.

According to the invention, the heat pump is characterized in that the width of the inlet of the first sub-channel is at least twice the width of the inlet of the second sub-channel, and / or that the cross-sectional area of the inlet of the first sub-channel is at least twice as large as the cross-sectional area of the inlet of the second subchannel. In other words, the input of the first sub-channel occupies at least two thirds of the width or the area of the entrance of the channel as a whole or the entrance of the second sub-channel occupies at most one third of the width or the area of the entrance of the channel as a whole. Are the input of the channel and thus the inputs of the two sub-channels rectangular and have the same height, it follows from the aforementioned ratio of the widths of the inputs and the corresponding ratio of the areas of the inputs.

The present invention is based on the finding that in the claimed ratio of the widths or areas of the inputs of the sub-channels to each other or in relation to the total width or the total area of the input as a whole a more uniform flow of the heat exchanger can be effected as previously known , At the same time thereby the production and assembly can be facilitated because this effect can be achieved with at least one Luftleitrippe, whereas so far only less effective measures using at least two Luftleitrippen are known.

According to one aspect of the present invention, the channel has exactly one air guide rib. In this way, the production and assembly compared to the previously known such heat pumps with at least two Luftleitrippen be simplified in any case. Furthermore, this can improve the quality of manufacture of the air guide rib because its shape is e.g. can be performed in an injection molding easier and safer. Also, an increase in the air resistance of the channel can be kept as low as possible. In particular, a lower air resistance of the channel compared to the previously known at least two Luftleitrippen can be achieved. Due to a lower air resistance of the channel, an equal flow of process air can be achieved with a lower blower output, which can increase the energy efficiency of the heat pump.

According to a further aspect of the present invention, the first sub-channel has an output facing away from the heat exchanger and the second sub-channel remote from the heat exchanger output, wherein the cross-sectional area of the output of the first sub-channel is at least twice as large as the cross-sectional area of the output of the second sub-channel. In this way, the advantageous effect of the ratio of the widths or areas at the inputs of the sub-channels can also be achieved at their outputs. As a result, the ratios of the widths or areas to one another or to the total width or to the total area from the entrance to the exit can be maintained in each case continuously. Alternatively, the ratio of the widths or areas of the inputs of the sub-channels to their outputs can also change, ie, in the course of the sub-channels can be wider or narrower.

According to a further aspect of the present invention, the first sub-channel has a heat exchanger remote from the output and the second sub-channel remote from the heat exchanger output, wherein the second sub-channel narrows more from its input to its output than the first sub-channel from its input to its output , Due to the constriction of the second sub-channel in the flow direction of the process air according to the laws of Venturi and Bernoulli, the flow rate from the output of the heat exchanger to the inlet of the fan can increase and the static pressure can drop, while the back pressure can increase by almost the same amount. Since relatively small pressure differences occur in the heat pump cycle, the assumption of an incompressible fluid is applicable to the process air.

Due to the geometry of the introduced air guide rib, which separates the channel at least in sections into two sub-channels, the ratio of the back pressure rise on both sides of the air guide rib can be controlled. Due to the above-described ratios of the individual widths or surfaces and in particular due to the narrowing of the second sub-channel, the process air in the second sub-channel between its input and output can be accelerated more than in the first sub-channel. As a result, a higher back pressure can build up in the second subchannel, which in interaction can throttle the volume flow and thus the flow velocity on this side of the air guide rib. In this way, in particular, a balance of the pressures of the two sub-channels can be adjusted and a larger part of the process air volume flow to the first sub-channel shift, which may be traversed too low without the use of Luftleitrippe. By matching the air guide rib on the specific application, thus a much more uniform flow through the heat exchanger can be achieved.

According to a further aspect of the present invention, the heat pump has a fan, which is designed to convey away the process air through the channel from the heat exchanger, wherein the input of the first sub-channel has a greater distance from the fan than the input of the second sub-channel, and or or wherein the output of the first sub-channel has a greater distance from the fan than the output of the second sub-channel. In this way, the characteristics of the second sub-channel described above can be applied to the sub-channel, which is arranged in the width closer to the fan. This is advantageous because the part of the channel facing the fan can be flowed through more strongly by the process air, in particular in a laterally offset arrangement of the fan relative to the heat exchanger. As a result, the other, the blower remote sub-channel can be flowed through weaker by the process air, which can reduce the energy efficiency of the heat pump, as already described above. This can i.a. be at least partially offset by this aspect of the present invention.

According to a further aspect of the present invention, the heat pump has a fan which is designed to convey away the process air through the channel from the heat exchanger, wherein the channel and / or the air guide rib is tangentially formed from the heat exchanger to the fan, wherein preferably the heat exchanger has a rectangular cross section and the fan has a circular cross section. In this way, a laminar flow can be achieved within the channel at least on its surfaces and / or on the surfaces of the air guide rib, so that turbulence and turbulence of the process air can be prevented, which can lead to pressure fluctuations and pressure losses.

According to a further aspect of the present invention, the channel has a rectangular cross section at least in the region of the air guide rib, wherein the air guide rib, preferably vertically, is formed over the entire height of the channel. In this way, the properties and advantages of the Luftleitrippe can be achieved over its entire height. In this case, forming the air guide rib vertically in height can be advantageous for the production, in particular by means of an injection molding process.

According to another aspect of the present invention, the air guide rib is formed over less than half, preferably over about one third, of the extent of the channel. This aspect of the present invention is based on the finding that a more uniform flow through the heat exchanger can already be achieved by the air guide rib according to the invention only over a part of the channel, preferably in the region of the entrance of the channel, is arranged, so that the effect of Luftleitrippe can be exerted on the flow of process air from there into the heat exchanger into it. Thereafter, it may not be necessary to influence the process air within the channel, so that the air conduction rib only has to be formed over a partial section of the channel. This can simplify manufacturing and make it cheaper. In particular, a component distortion in the formation of the comparatively short air guide rib can be achieved, for example. be reduced or even avoided by means of an injection molding process.

In other words, it is advantageous to arrange the air guide rib as close to the heat exchanger and relatively short form in the flow direction of the process air, provided that the desired retroactive effect on the flow of process air before entering the channel can be achieved, which leads to a more uniform flow through the Heat exchanger can lead.

Furthermore, an increase in the air resistance of the channel can be kept as low as possible by a comparatively short air guide rib. In particular, a lower air resistance of the channel compared to the previously known at least two Luftleitrippen can be achieved, so that an equal flow of process air can be achieved with a lower fan performance, which can increase the energy efficiency of the heat pump.

According to a further aspect of the present invention, the air guiding rib extends from a front edge facing the heat exchanger to a rear edge facing away from the heat exchanger, the front edge of the air guiding rib being oriented approximately perpendicularly to the overall cross-sectional area of the heat exchanger. As a result, the air conduction rib can be arranged as close as possible to the heat exchanger or at its outlet in order to be able to exert its effect as effectively as possible on the process air within the heat exchanger. By aligning the front edge of the air guide rib perpendicular or at least approximately perpendicular to the total cross-sectional area of the heat exchanger, a laminar as possible transition of the process air from the heat exchanger into the sub-channels can be achieved.

According to a further aspect of the present invention, the air guide rib is curved at least in sections. As a result, on the one hand, a most laminar and non-turbulent flow along the air guide rib can be achieved, so that pressure fluctuations and pressure losses due to turbulence and turbulence can be avoided. Furthermore, the course of the process air can be predetermined and influenced as well as possible by a laminar and non-turbulent flow that is as laminar as possible. On the other hand, a mechanical stiffening of the air guide rib can be achieved thereby.

According to a further aspect of the present invention, the curvature of the air guide rib is designed such that a separation of the flow of the process air can be prevented at least in sections. As a result, turbulent flows and thus the formation of vortices, which can lead to pressure losses, can be prevented. The concrete design of the curvature of the air guide rib depends on the application and can, for example. be determined by numerical methods for flow simulation.

According to a further aspect of the present invention, the heat pump has a housing with a housing lower part and with an upper housing part, wherein the Luftleitrippe in sections, preferably in half height, integral with the lower housing part and partially, preferably formed at half the height, integral with the housing upper part is. In this way, a simple production of the Luftleitrippe can be achieved by the formation as a respective partial component of the two housing parts, so that no separate production and installation of the air duct must be made. In this case, the air guide rib can be assigned in height one half each to one of the two housing parts, e.g. In an injection molding process their component distortion as low as possible and simplify their assembly.

The present invention also relates to a heat pump apparatus, preferably a heat pump household appliance, preferably a heat pump laundry dryer or a heat pump washing machine, with a heat pump cycle with a heat pump as described above. In this way, the previously described properties and advantages of a heat pump according to the invention in a heat pump device can be used to increase its energy efficiency. This can positively influence the purchase decision of a user. This increase in energy efficiency can be achieved at the same time at very low cost, because the Luftleitrippe in the manufacture of the heat pump and in particular in a design of the housing parts of a housing of the heat pump in the production by means of an injection molding process can be easily formed, so that these benefits almost without increased production costs can be implemented.

According to another aspect of the present invention, the heat pump apparatus has a drum drive configured to rotate a drum of the heat pump apparatus, the drum drive being further configured to rotate a fan of the heat pump. In other words, in this case, the fan is arranged in extension of the drum drive next to the heat exchanger, so that the process air from the heat exchanger via a non-axially extending channel must be supplied to the blower. This can in particular lead to an uneven flow through the heat exchanger, as described above. Therefore, especially in such a case, the use of a heat pump according to the invention is advantageous to these uneven Flow through the heat exchanger at least partially and compensate with simple means again.

According to another aspect of the present invention, the heat pump apparatus has a shaft extension which connects the drum drive with the fan in the axial direction. In this way, the fan can be driven by the drum drive, so that can be dispensed with a separate drive of the fan, which can reduce the cost of the heat pump device. At the same time, however, by using a heat pump according to the invention a more uniform flow through the heat exchanger as previously known and can be achieved with simple means.

An embodiment of the invention is shown purely schematically in the drawings and will be described in more detail below. It shows

1 a perspective view of a lower portion of a heat pump device with a heat pump according to the invention;

2 a perspective view of a housing of the heat pump according to the invention obliquely from above;

3 the representation of 2 from diagonally below;

4 a horizontal section of the heat pump device with a known heat pump;

5 a perspective view of a section of a portion of the heat pump according to the invention;

6 a section of the 4 for the heat pump according to the invention;

7 a section of the 6 ;

8th an alternative representation of the 1 ;

9 a section of the 7 ; and

10 a cross section of the channel of the heat pump according to the invention.

The o.g. Figures are considered in Cartesian coordinates. It extends a longitudinal direction X, which may also be referred to as depth X. Perpendicular to the longitudinal direction X extends a transverse direction Y, which may also be referred to as width Y. Perpendicular to both the longitudinal direction X and the transverse direction Y extends a vertical direction Z, which may also be referred to as height Z.

It becomes a heat pump device 2 in the form of a heat pump tumble dryer 2 considered as an example. The heat pump clothes dryer 2 has a heat pump in its lower part 1 on. The heat pump 1 has a housing 10 on, which also as a floor module 10 or in combination with some components of the heat pump unit 2 as floor module module 10 can be designated. The housing 10 consists of a lower housing part 11 , which also as a base plate 11 of the floor module 10 can be designated, and from an upper housing part 12 , which also serves as the lid of the floor module 10 can be designated, cf. eg 2 and 3 , The two housing parts 11 . 12 are made of plastic and have been produced by means of an injection molding process. The lower housing part 11 and the upper housing part 12 can be placed on each other so that they form between them different cavities, each half of the lower housing part 11 and the other half of the housing top 12 be formed.

Within a cavity, which is the essential space of the housing 10 can take a condenser 14 as well as an evaporator 16 the heat pump cycle are arranged. Both the condenser 14 as well as the evaporator 16 each have a heat exchanger 15 . 17 on which lamellae 15 . 17 having. The slats 15 . 17 both of the liquefier 14 as well as the evaporator 16 are aligned in the longitudinal direction X and extend each other. The slats 15 . 17 Extend together in the longitudinal direction X at a depth D and in the vertical direction Z in an identical height C and in the transverse direction Y in an identical width Bwü. Furthermore, on the lower housing part 11 a compressor 13 the heat pump cycle arranged, see eg 1 , A throttle of the heat pump cycle is not shown.

To the cavity, which is the condenser 14 as well as the evaporator 16 receives, closes in the longitudinal direction X a channel 3 at the end of which is an impeller 19 a blower 18 is arranged, which are also attributable to the process air cycle. The fan wheel 19 leads to a rear air duct 23 of the process air cycle. The entrance of the housing 10 to the evaporator 16 There is a front air duct 22 of the process air cycle.

Next to the compressor 13 is on the housing base 10 Furthermore, a drum drive 20 as part of the heat pump tumble drier 2 arranged, which on the one hand the drum of the heat pump tumble dryer 2 (not shown) can drive rotating and on the other via a shaft extension 21 with the blower wheel 19 connected to this together with the drum to drive.

During operation of the heat pump tumble dryer 2 The heat pump circuit serves to do this via the front air duct 22 wet process air R supplied by the drum, the wet process air R get their moisture in the evaporator 16 to remove by condensation and then reheat the dry process air, so that a dried and heated process air S the heat pump cycle via the rear air duct 23 leave in the direction of the drum again. The required flow of process air R, S is caused by the rotation of the impeller 19 generated by the shaft extension 21 simultaneously with the rotation of the drum is effected.

Due to the operation of drum and impeller 19 by means of a common drive 20 Although it can be on an additional drive of the fan 19 be waived. However, the impeller needs 19 in axial extension of the drum drive 20 to be ordered. This requires the deflection of the dried and heated process air S after leaving the condenser 14 by means of a channel 3 to the fan wheel 19 towards, cf. eg 4 and 6 , However, this causes the process air inside the fins 15 . 17 or within the heat exchanger 15 . 17 both of the liquefier 14 as well as the evaporator 16 in the transverse direction Y or in the width Bwü the heat exchanger 15 . 17 at the blower 18 closer side has a higher flow velocity V than on the opposite side, see diagram of 4 , In particular, arises at the right, inner edge of the heat exchanger 15 . 17 a peak of the flow velocity V of the dried and heated process air S. This uneven distribution of the flow velocity V causes the blower 18 in width Bwü averted slats 15 . 17 The process air flows around less, which reduces their effect and thus the energy efficiency of the heat pump 1 can reduce.

According to the invention, therefore, the channel 3 between the liquefier 14 and the blower 19 in the approximately first third of its extension by a Luftleitrippe 36 into a first subchannel 30 and into a second subchannel 33 divided. The air conduction rib 36 starts with its leading edge 37 about directly behind the slats 15 of the liquefier 14 and is roughly in the direction of the slats 15 of the liquefier 14 aligned, so that the process air as laminar of the slats 15 of the liquefier 14 in the two subchannels 30 . 33 can go over. The air conduction rib 36 ends after about one third of the extension of the canal 30 with its rear edge 38 in the canal 3 ,

The air conduction rib 36 extends throughout the height Z perpendicularly between the lower housing part 11 and the upper housing part 12 so they are injection molded to manufacture the body parts 11 . 12 can be trained with. Here is the air duct 36 about half as part of the housing base 11 and about half as part of the upper housing part 12 educated. In its course is the Luftleitrippe 36 curved, so that a mechanical stiffening of the air duct 36 can be achieved. At the same time, the curved course of the air guide rib 36 designed such that over the entire extent of the air duct 36 a laminar as possible flow of the dried and heated process air S along the air guide rib 36 can be achieved.

The first subchannel 30 extends from its entrance 31 , which by the beginning of the channel 3 on the blower 18 opposite side and the front edge 37 the air conduction rib 36 is formed, to its exit 32 passing through an area of the canal 3 near the end of the blower 18 and the back edge 38 the air conduction rib 36 is formed. The second subchannel 33 extends from its entrance 34 , which by the beginning of the channel 3 on the blower 18 facing side and the front edge 37 the air conduction rib 36 is formed, to its exit 35 passing through an area of the canal 3 in the front quarter of the canal 3 and the back edge 38 the air conduction rib 36 is formed.

The entrance 31 of the first subchannel 30 has a width Bwü1 and a cross-sectional area Awü1. The entrance 34 of the second subchannel 33 has a width Bwü2 and a cross-sectional area Awü2. The widths Bwü1, Bwü2 of the entrances 31 . 34 the two subchannels 30 . 33 together make up the total width Bwü of the canal 3 in the area of the front edge 37 the air conduction rib 36 , Due to the rectangular cross section of the entrances 31 . 34 the two subchannels 30 . 33 this applies accordingly for the cross-sectional areas Awü1, Awü2 and for the total cross-sectional area Awü.

The exit 32 of the first subchannel 30 has a width Bk1 and a cross-sectional area Ak1. The exit 35 of the second subchannel 33 has a width Bk2 and a cross-sectional area Ak2. The widths Bk1, Bk2 of the outputs 32 . 35 the two subchannels 30 . 33 together make up the total width Bk of the canal 3 in the area of the rear edge 38 the air conduction rib 36 , The cross-sectional areas Ak1, Ak2 of the outputs 32 . 35 the two subchannels 30 . 33 together form the total cross-sectional area Ak of the channel 3 in the area of the rear edge 38 the air conduction rib 36 , This is shown by the outputs 32 . 35 the two subchannels 30 . 33 different according to this embodiment and non-rectangular contours, cf. 9 and 10 ,

According to the invention, the subchannels 30 . 33 by the arrangement of the air guide rib 36 formed such that the width Bwü1 of the input 31 of the first subchannel 30 which is the blower 18 is turned away in the transverse direction Y, about two-thirds of the total width Bwü of the channel 3 occupies and the width Bwü2 the entrance 34 of the second subchannel 33 which is the blower 18 in the transverse direction Y, about one third of the total width Bwü of the channel 3 is. At the same time, the second sub-channel narrows 33 over its course, so that the width Bk1 of the output 34 of the first subchannel 30 which is the blower 18 facing away in the transverse direction Y, greater than two-thirds of the total width Bwü the channel 3 is and the width Bk2 of the output 35 of the second subchannel 33 which is the blower 18 in the transverse direction Y, less than one third of the total width Bwü of the channel 3 occupies.

By the conditions of the widths Bwü1, Bwü2 of the entrances 31 . 34 the two subchannels 30 . 33 to each other and through the narrowing of the second sub-channel 33 can the dried and heated process air S in the second subchannel 33 accelerated more than in the first sub-channel 30 , This may result in the second subchannel 33 build a higher dynamic pressure, which interacts with the volume flow and thus the flow velocity V at the entrance 34 of the second subchannel 33 can throttle, see diagram of 6 , In particular, a peak of the flow velocity V can be avoided in this way, cf. Diagram of 4 , For this the second subchannel 33 in the area of the third of the channel 3 which is the blower 18 in the transverse direction Y closest to form can be justified by the fact that in this area, the largest increase in the flow velocity V occurs, see. Diagram of 4 passing through the air duct 36 can be effectively reduced. In this way, a balance of the pressures of the two subchannels can 30 . 33 set and a larger part of the process air volume flow on the first sub-channel 30 shift, which without the use of the Luftleitrippe 36 would flow through too low. By the vote of the air duct 36 on the specific application, thus a much more uniform flow through the heat exchanger 15 . 17 be achieved. This applies all the more, the broader the heat exchanger 15 . 17 are formed in the transverse direction Y.

For this it is sufficient, the Luftleitrippe 36 comparatively short, such as just over one third of the length of the channel 3 form, as this length may already be sufficient to the previously described increased back pressure in the second sub-channel 33 and to achieve the associated previously described effect. This can keep the manufacturing costs for implementing this effect low. In particular, a better fit accuracy of the two halves of the housing parts 11 . 12 be achieved in that the extension of the Luftleitrippe 36 kept as low as possible.

LIST OF REFERENCE NUMBERS

ak

Total cross-sectional area of the channel 3 at outputs 32 . 35 the subchannels 30 . 33

k1

Cross-sectional area of the outlet 32 of the first subchannel 30

A k2

Cross-sectional area of the outlet 35 of the second subchannel 33

Awü

Total cross-sectional area of the heat exchanger 15 . 17

Awü1

Cross-sectional area of the entrance 31 of the first subchannel 30

Awü2

Cross-sectional area of the entrance 34 of the second subchannel 33

Bk

Total width of the channel 3 at outputs 32 . 35 the subchannels 30 . 33

Bk1

Width of the output 32 of the first subchannel 30

Bk2

Width of the output 35 of the second subchannel 33

BWC

Overall width of the heat exchanger 15 . 17

Bwü1

Width of the entrance 31 of the first subchannel 30

Bwü2

Width of the entrance 34 of the second subchannel 33

C

Height of the heat exchanger 15 . 17 and the channel 3 and the air ducting rib 36

D

Depth of the heat exchanger 15 . 17

R

 moist process air

S

 dried and heated process air

V

 Flow rate of the dried and heated process air S

X

 Longitudinal direction; depth

Y

 Transverse direction; width

Z

 vertical direction; height

1

 heat pump

10

 Casing; Floor module (-baugruppe)

11

Housing base; Base module base; Base plate of the floor module 10

12

Housing top; Base module shell; Cover of the floor module 10

13

 Compressor; compressor

14

 condenser; capacitor

15

Heat exchanger, heat exchanger or fins of the condenser 14

16

 Evaporator

17

Heat exchanger, heat exchanger or fins of the evaporator 16

18

 (Process air) blower

19

 blower

2

 Heat pump unit; Heat pumps household appliance; Heat pump dryer; Heat pumps Washer

20

 drum drive

21

Shaft extension of the drum drive 20

22

 front air duct

23

 rear air duct

3

Channel between condenser 14 and blowers 18

30

 first subchannel

31

Entrance of the first subchannel 30

32

Output of the first subchannel 30

33

 second subchannel

34

Input of the second subchannel 33

35

Output of the second subchannel 33

36

 Luftleitrippe

37

leading edge of the air duct 36

38

rear edge of the air duct 36

QUOTES INCLUDE IN THE DESCRIPTION

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

Cited patent literature

• EP 2628845 A1 [0016, 0017, 0018]

Claims (15)

Heat pump ( 1 ), with at least one heat exchanger ( 15 ), and with at least one channel ( 3 ), which is formed, a process air (S) from the heat exchanger ( 15 ), whereby the channel ( 3 ) at least one air guide rib ( 36 ), which is formed, the channel ( 3 ) at least in sections into a first subchannel ( 30 ) and into a second subchannel ( 33 ), the first subchannel ( 30 ) is designed, a portion of the process air (S) via an input ( 31 ) of the heat exchanger ( 15 ), and wherein the second subchannel ( 33 ) is designed, a portion of the process air (S) via an input ( 34 ) of the heat exchanger ( 15 ), characterized in that the width (Bwü1) of the input ( 31 ) of the first subchannel ( 30 ) at least twice as large as the width (Bwü2) of the entrance ( 34 ) of the second subchannel ( 33 ), and / or that the cross-sectional area (Awü1) of the entrance ( 31 ) of the first subchannel ( 30 ) at least twice as large as the cross-sectional area (Awü2) of the entrance ( 34 ) of the second subchannel ( 33 ). Heat pump ( 1 ) according to claim 1, characterized in that the channel ( 3 ) exactly one air conduction rib ( 36 ) having. Heat pump ( 1 ) according to claim 1 or 2, characterized in that the first sub-channel ( 30 ) a the heat exchanger ( 15 ) opposite exit ( 32 ) and the second subchannel ( 33 ) a the heat exchanger ( 15 ) opposite exit ( 35 ), wherein the cross-sectional area (Ak1) of the output ( 32 ) of the first subchannel ( 30 ) at least twice as large as the cross-sectional area (Ak2) of the exit ( 35 ) of the second subchannel ( 33 ). Heat pump ( 1 ) according to one of the preceding claims, characterized in that the first sub-channel ( 30 ) a the heat exchanger ( 15 ) opposite exit ( 32 ) and the second subchannel ( 33 ) a the heat exchanger ( 15 ) opposite exit ( 35 ), wherein the second sub-channel ( 33 ) from his entrance ( 34 ) to its output ( 35 ) narrowed more than the first subchannel ( 30 ) from his entrance ( 31 ) to its output ( 32 ). Heat pump ( 1 ) according to one of the preceding claims, characterized by a blower ( 18 ), which is formed, the process air (S) through the channel ( 3 ) through the heat exchanger ( 15 ), whereby the entrance ( 31 ) of the first subchannel ( 30 ) a greater distance to the blower ( 18 ) as the entrance ( 34 ) of the second subchannel ( 33 ), and / or wherein the output ( 32 ) of the first subchannel ( 30 ) a greater distance to the blower ( 18 ) as the output ( 35 ) of the second subchannel ( 33 ) having. Heat pump ( 1 ) according to one of the preceding claims, characterized by a blower ( 18 ), which is formed, the process air (S) through the channel ( 3 ) through the heat exchanger ( 15 ), whereby the channel ( 3 ) and / or the air guiding rib ( 36 ) of the heat exchanger ( 15 ) to the blower ( 18 ) is formed tangent continuous / are, preferably the heat exchanger ( 15 ) has a rectangular cross-section and the blower ( 18 ) has a circular cross-section. Heat pump ( 1 ) According to one of the preceding claims, characterized in that the channel ( 3 ) at least in the region of the air guide rib ( 36 ) has a rectangular cross section, wherein the air guide rib ( 36 ), preferably vertically, over the entire height (C) of the channel ( 3 ) is trained. Heat pump ( 1 ) according to one of the preceding claims, characterized in that the air guide rib ( 36 ) over less than half, preferably over approximately one third, of the extent of the channel ( 3 ) is trained. Heat pump ( 1 ) according to one of the preceding claims, characterized in that the air guide rib ( 36 ) from a front, the heat exchanger ( 15 ) facing edge ( 37 ) to a rear, the heat exchanger ( 15 ) facing away edge ( 38 ), with the leading edge ( 37 ) the air guide rib ( 36 ) approximately perpendicular to the total cross-sectional area (Awü) of the heat exchanger ( 18 ) is aligned. Heat pump ( 1 ) according to one of the preceding claims, characterized in that the air guide rib ( 36 ) is formed curved at least in sections. Heat pump ( 1 ) according to claim 10, characterized in that the curvature of the Luftleitrippe ( 36 ) is designed such that a detachment of the flow of the process air (S) can be prevented at least in sections. Heat pump ( 1 ) according to one of the preceding claims, characterized by a housing ( 10 ) with a housing lower part ( 11 ) and with an upper housing part ( 12 ), wherein the air guiding rib ( 36 ) in sections, preferably at half the height (C), integral with the lower housing part ( 11 ) and in sections, preferably in half the height (C), integral with the upper housing part ( 12 ) is trained. Heat pump device ( 2 ), preferably heat pump household appliance ( 1 ), preferably heat pump laundry driers ( 1 ) or heat pump washing machine ( 1 ), with a heat pump cycle with a heat pump ( 1 ) according to one of the preceding claims. Heat pump device ( 2 ) according to claim 13, characterized by a drum drive ( 20 ), which is formed, a drum of the heat pump device ( 1 ), whereby the drum drive ( 20 ) is further configured, a blower ( 18 ) of the heat pump ( 18 ) to rotate. Heat pump device ( 2 ) according to claim 14, characterized by a shaft extension ( 21 ), which drives the drum ( 20 ) with the blower ( 18 ) connects in the axial direction.

Images