DE102019115263A1 - Storage device for storing a refrigerant compressor for a motor vehicle and storage arrangement - Google Patents

Abstract

The invention relates to a storage device (4) for mounting a refrigerant compressor (2) on a structure (3) of a motor vehicle, with a holder (7) formed separately from the refrigerant compressor (2) as an intermediate mass, with a plurality of elastically deformable first spacers Bearing elements (6a-d), via which the refrigerant compressor (2) is mounted on the holder (7), and with several, in addition to the first bearing elements (6a-d), provided from each other and from the first bearing elements (6a-d) spaced apart and elastically deformable second bearing elements (8a-d), via which the holder (7) is to be mounted on the structure (3).

Description

The invention relates to a storage device for storing a refrigerant compressor on a body of a motor vehicle. The invention also relates to a mounting arrangement of a refrigerant compressor on a body of a motor vehicle.

The DE 103 92 645 T5 discloses an electric compressor having a plurality of cylinders circumferentially arranged on one end side of a compressor body. The DE 198 07 923 A1 a compressor for an air conditioning system of a motor vehicle can be found as known. In addition, from the DE 10 2007 048 936 B4 a refrigerant compressor arrangement is known.

The object of the present invention is to create a storage device and a storage arrangement so that a refrigerant compressor can be particularly advantageously stored on a structure of a motor vehicle.

This object is achieved according to the invention by a storage device with the features of claim 1 and by a storage arrangement with the features of claim 11. Advantageous refinements of the invention are the subject of the dependent claims.

A first aspect of the invention relates to a mounting device for mounting a refrigerant compressor on a structure of a motor vehicle, in particular a passenger vehicle, which is designed, for example, as a self-supporting body. It is preferably provided that the storage device comprises the refrigerant compressor. The refrigerant compressor is also referred to as a compressor, compressor or refrigerant compressor and is designed to compress and convey a refrigerant of an air conditioning system. This means that the motor vehicle in its completely manufactured state comprises the storage device, the refrigerant compressor and the air conditioning system. The air conditioning system has at least one refrigerant circuit through which the refrigerant can flow and in which the refrigerant compressor can be or is arranged. The refrigerant can be compressed by means of the refrigerant compressor and conveyed through the refrigerant circuit. For this purpose, the refrigerant compressor has, for example, a housing and at least one conveying element received in the housing, which conveying element can be moved relative to the housing. For conveying and compressing the refrigerant, the conveying element is moved relative to the housing. In particular, for conveying and compressing the refrigerant, the conveying element is rotated about an axis of rotation relative to the housing. In particular, it can be provided that the conveying element is movably, in particular rotatably, mounted on the housing.

In order to be able to mount the refrigerant compressor in a particularly advantageous manner on the structure of the motor vehicle, the mounting device comprises a holder as an intermediate mass which is formed separately from the refrigerant compressor and preferably separately from the structure. This means that the holder or its mass is an intermediate mass or is used as an intermediate mass, with the intermediary of which the refrigerant compressor is to be mounted or mounted on the structure. The storage device also includes a plurality of spaced apart and elastically deformable first bearing elements, which are formed, for example, separately from the holder, separate from the structure and separately from the refrigerant compressor and are in particular arranged outside the housing of the refrigerant compressor. The refrigerant compressor is mounted on the holder, in particular damped and / or decoupled, via the first bearing elements. The feature that the first bearing elements are spaced from one another is to be understood in particular that the refrigerant compressor is connected to the first bearing elements in particular via its housing at points spaced apart from one another and is thus mounted on the holder via the first bearing elements. The respective first bearing element is formed, for example, on its elastically deformable material, in particular from an elastically deformable plastic and thus, for example, from an elastomer, wherein the respective first bearing element can be formed in particular from rubber. In particular, the refrigerant compressor, in particular via its housing, is mounted on the holder in a vibration-damped and / or vibration-decoupled manner via the first bearing elements. Since the first bearing elements are elastically deformable, the first bearing elements allow, for example, relative movements between the refrigerant compressor and the holder. With such relative movements between the refrigerant compressor and the holder, the first bearing elements are elastically deformed. As a result, vibration energy is converted into deformation energy, as a result of which the relative movements between the refrigeration element compressor and the holder are damped by means of the first bearing elements. Vibrations of the refrigerant compressor that occur relative to the holder can thus be damped. The refrigerant compressor is thus at least substantially decoupled via the first bearing elements, in particular at least substantially vibration decoupled, mounted on the holder so that the first bearing elements are, for example, first decoupling elements.

The storage device according to the invention also comprises several, in addition to the First bearing elements provided, spaced apart and elastically deformable from a first bearing element, which are for example formed separately from the first bearing elements, separate from the refrigerant compressor, separate from the holder and separate from the structure. In addition, for example, the second bearing elements are designed separately from one another and / or the second bearing elements are designed separately from the first bearing elements. Furthermore, the first bearing elements can be formed separately from one another. The holder, in particular damped and / or decoupled, preferably vibration damped and / or vibration decoupled, is to be supported or supported on the structure via the second bearing elements. The respective second bearing element is formed, for example, from an elastically deformable material, in particular from an elastically deformable plastic and thus, for example, from an elastomer. In particular, it is conceivable that the respective second bearing element is formed from rubber.

The feature that the second bearing elements are spaced apart from one another is to be understood in particular as the fact that the holder is connected to the respective second bearing elements at respective, spaced apart second locations and is thereby to be supported or supported on the structure via the second bearing elements. Since the second bearing elements are elastically deformable, the second bearing elements allow relative movements between the holder functioning as an intermediate mass and the structure. With such relative movements between the holder and the structure, the second bearing elements are elastically deformed, whereby vibration energy is converted into deformation energy. As a result, the relative movements between the holder and the structure are damped by means of the second bearing elements, so that vibrations of the holder relative to the structure can be damped. Thus, the holder is damped and / or decoupled, in particular vibration-damped and / or vibration-decoupled, to be supported or supported on the structure. The second bearing elements are therefore also referred to as second decoupling elements. Overall, it can be seen that the first bearing elements form, for example, a first decoupling plane, which is also referred to as the first bearing plane or first damping plane. By means of the first decoupling level, the refrigerant compressor is mounted on the holder at least essentially decoupled. In addition, vibrations of the refrigerant compressor and thus relative movements between the refrigerant compressor and the holder can be dampened by means of the first decoupling plane. The second bearing elements form a second decoupling level, which is also referred to as the second bearing level or second damping level. By means of the second decoupling level, the holder can be stored or stored on the structure at least essentially decoupled. Vibrations of the holder and the resulting relative movements between the holder and the structure can be damped by means of the second decoupling plane, so that vibrations of the refrigerant compressor occurring relative to the structure can be dampened particularly effectively and efficiently by means of the decoupling planes. As a result, the refrigerant compressor can be mounted on the structure, that is to say connected to the structure, particularly advantageously in terms of vibration or noise. In other words, the storage device according to the invention can prevent excessive noises resulting from relative movements between the refrigerant compressor and the structure, so that a particularly advantageous noise behavior of the motor vehicle can be achieved. In particular, it is provided that the refrigerant compressor is connected to the first bearing elements via its housing, so that the refrigerant compressor is mounted at least essentially decoupled on the holder via its housing and the first bearing elements.

The invention is based in particular on the following findings: Since, for example, during operation of the refrigerant compressor, the conveying element is moved relative to the housing in order to compress and convey refrigerant, it can conventionally cause vibrations and thus oscillations of the refrigerant compressor in particular relative to the Construction come. With conventional mounting arrangements of conventional refrigerant compressors on conventional superstructures of motor vehicles, the vibrations of the refrigerant compressor can lead to a vibroacoustic stimulation of the structure, which can result in noises. These noises can be perceived acoustically, for example, by people staying in the interior of the motor vehicle and / or by people staying in the vicinity of the motor vehicle. By means of the storage device according to the invention it is now possible to prevent undesired, excessive noises from occurring. In particular, an excessive, vibroacoustic stimulation of the structure caused by the refrigerant compressor during its operation can be avoided by means of the mounting device. For this purpose, the refrigerant compressor can be particularly advantageously acoustically decoupled on the structure by means of the storage device according to the invention. As a result, high acoustic requirements can also be met, and an advantageous noise behavior of the motor vehicle can be achieved. In this way, a particularly high perceived value of the motor vehicle can be represented. One A further advantage of the storage device according to the invention is that the refrigerant compressor is not provided alone as an oscillating mass, but according to the invention the holder is used as an, in particular oscillating or oscillatable, intermediate mass. As a result, excessive stimuli in the structure that can be brought about or can be brought about by means of the refrigerant compressor can be kept low or avoided.

The bearing elements and the holder form a decoupling system which, in particular with regard to a number of the bearing elements, a bearing rigidity of the respective decoupling plane, the respective characteristics of the bearing elements, a mass, a weight distribution, etc. is specifically and advantageously designed and in particular to the refrigerant compressor, in particular whose operation is adapted. As a result, the storage device according to the invention can be used to provide adequate vibroacoustic insulation of the refrigerant compressor from the structure. The respective characteristic curve of the respective bearing element is also referred to as the bearing or damping characteristic curve and illustrates or visualizes, for example, a behavior and / or a respective rigidity, in particular bearing rigidity, of the respective bearing element. In particular, the characteristic curve describes or visualizes, for example, a relationship between a force acting on the respective bearing element and a deflection or deformation of the respective bearing element resulting from this force.

Since the two decoupling levels are provided according to the invention, a double-elastic decoupling of the refrigerant compressor with respect to the structure is shown according to the invention. The holder is also provided as an intermediate mass. The bearing stiffnesses of the bearing elements, the number of bearing elements, the characteristic curve of the bearing elements, the intermediate mass and a weight distribution are preferably or will be specifically coordinated with one another in order to achieve adequate, in particular vibration isolation, of the refrigerant compressor from the structure.

The motor vehicle is designed, for example, as an electric vehicle, in particular as a battery-electric vehicle (BEV). It was found that, in particular in the case of electric vehicles, adequate vibration isolation of the refrigerant compressor from the structure is desirable and should be provided, since otherwise unpleasant and acoustically perceptible noises can occur. The storage device according to the invention makes it possible, even in an electric vehicle, to sufficiently decouple the refrigerant compressor from the structure and to be able to store it on the structure and thus hold it.

It has been shown to be particularly advantageous if at least a first of the first bearing elements is arranged on a first side of the refrigerant compressor, in particular the housing of the refrigerant compressor. At least a second of the first bearing elements is arranged on a second side of the refrigerant compressor facing away from the first side, in particular the housing of the refrigerant compressor, and at least a third of the first bearing elements is on a third side of the refrigerant compressor facing away from the first side and the second side, in particular of the housing of the refrigerant compressor, arranged. A particularly advantageous decoupling of the refrigerant compressor can hereby be achieved.

Another embodiment is characterized in that the respective first bearing element, considered by itself, has a bearing rigidity which, along a first direction, is in a range from 10 N / mm up to and including 55 N / mm, in particular in a range from 15 N inclusive / mm up to and including 45 N / mm and preferably in a range from and including 17 N / mm up to and including 40 N / mm, and along a second direction running perpendicular to the first direction in a range from and including 5 N / mm up to and including 15 N / mm, in particular in a range from 7 N / mm up to and including 10 N / mm, in particular with regard to tensile and compressive loads, that is to say with regard to tensile and compressive forces, for example from the refrigerant compressor on the respective first Act bearing element. For example, the bearing rigidity of the respective first is Bearing element along the first direction in a range from and including 18 N / mm to and including 40 N / mm. In particular, the bearing rigidity of the respective first bearing element can be 17 N / mm along the first direction. For example, the bearing rigidity of the respective first bearing element along the second direction is 7 N / mm or 8 N / mm. The respective bearing rigidity of the respective first bearing element considered in isolation is also referred to as the individual bearing rigidity of the respective first bearing element.

In order to be able to realize a particularly advantageous noise behavior of the motor vehicle, it is provided in a further embodiment of the invention that the respective second bearing element, considered by itself, has a bearing rigidity which, along the first direction, is in a range from 10 N / mm up to and including 40 N / mm, in particular in a range from 15 N / mm up to and including 35 N / mm. In particular, the bearing rigidity of the respective second bearing element along the first direction can be in a range from 24 N / mm to and including 32 N / mm. In particular, the bearing rigidity of the respective second bearing element can be 15 N / mm along the first direction. The bearing rigidity of the respective second bearing element along the second direction can be 38 N / mm or 35 N / mm. The respective bearing rigidity of the respective second bearing element considered in isolation is also referred to as the individual bearing rigidity of the respective second bearing element.

In order to be able to reliably avoid excessive, undesired noises, it has been shown to be advantageous if the first direction is the axial direction of the refrigerant compressor, the second direction being the radial direction of the refrigerant compressor. The axial direction of the refrigerant compressor coincides, for example, with the previously mentioned axis of rotation about which the conveying element can be rotated relative to the housing of the refrigerant compressor.

In a particularly advantageous embodiment of the invention, the intermediate mass is at least 7 kilograms (kg), in particular at least 10 kg. In this way, particularly advantageous vibration damping can be achieved.

In order to be able to cancel or damp vibrations particularly advantageously, it has also been shown to be advantageous if the intermediate mass is at most 20 kg, in particular at most 15 kg. For example, the intermediate mass is 10 kg or 15 kg.

Another embodiment is characterized in that the holder is designed as a holding frame. The holding frame delimits a through opening in which the refrigerant compressor is at least partially arranged or received. In particular, it can be provided that the refrigerant compressor, in particular its housing, penetrates the through opening. This allows the refrigerant compressor to be connected to the structure in a particularly low-vibration manner. In order to be able to realize a sufficiently high rigidity of the holding frame, it is preferably provided that the through opening is delimited completely circumferentially along its circumferential direction by the holding frame and thus completely closed circumferentially.

In order to achieve particularly advantageous noise behavior, it is provided in a further embodiment of the invention that the refrigerant compressor is designed as an electrically operable refrigerant compressor. The electrically operated refrigerant compressor is also referred to as an electric refrigerant compressor or eKMV. For this purpose, the refrigerant compressor comprises, for example, an electric motor which, for example, can be arranged at least partially, in particular at least predominantly or completely, in the housing. In this case, for example, the conveying element can be driven by the electric motor and thereby moved relative to the housing, as a result of which the refrigerant can be conveyed and compressed by means of the refrigerant compressor.

Finally, in order to implement a particularly advantageous coupling, it has been shown to be particularly advantageous if at least three first bearing elements and / or at least three second bearing elements are provided. In other words, the number of first bearing elements is at least or exactly 3. Preferably, the number of first bearing elements is at least or exactly 4. Alternatively or additionally, it is preferably provided that the number of second bearing elements is at least or exactly 3. The number of second bearing elements is preferably at least or exactly 4.

A second aspect of the invention relates to a mounting arrangement of a refrigerant compressor on a structure of a motor vehicle, in particular a passenger vehicle, which is preferably designed as a self-supporting body. In the case of the storage arrangement, the refrigerant compressor is mounted as an intermediate mass, in particular damped or decoupled, via a plurality of spaced apart and elastically deformable first bearing elements on a holder formed separately from the refrigerant compressor and separately from the structure. Since the holder is formed separately from the refrigerant compressor, the holder is formed separately from the aforementioned housing of the refrigerant compressor. The holder or the intermediate mass is mounted on the structure, in particular damped or decoupled, via several elastically deformable second bearing elements, which are provided in addition to the first bearing elements, are spaced apart from one another and are spaced from the first bearing elements. Advantages and advantageous configurations of the first aspect of the invention are to be regarded as advantages and advantageous configurations of the second aspect of the invention and vice versa.

• 1 ausschnittsweise eine schematische Perspektivansicht einer erfindungsgemäßen Lagerungsanordnung eines Kältemittelverdichters an einem Aufbau eines Kraftwagens gemäß einer ersten Ausführungsform;
• 2 eine schematische Rückansicht einer Lagerungseinrichtung zum Lagern des Kältemittelverdichters an dem Aufbau;
• 3 eine schematische Draufsicht der Lagerungseinrichtung gemäß 2;
• 4 eine schematische Seitenansicht der Lagerungseinrichtung gemäß 2 und 3;
• 5 ausschnittsweise eine schematische Perspektivansicht der Lagerungsanordnung gemäß einer zweiten Ausführungsform;
• 6 eine schematische Rückansicht einer Lagerungseinrichtung zum Lagern des Kältemittelverdichters gemäß der zweiten Ausführungsform;
• 7 eine schematische Draufsicht der Lagerungseinrichtung gemäß 6 und
• 8 eine schematische Seitenansicht der Lagerungseinrichtung gemäß 6 und 7.

Further details of the invention emerge from the following description of preferred exemplary embodiments with the associated drawings. It shows:

• 1 a fragmentary schematic perspective view of a storage arrangement according to the invention of a refrigerant compressor on a structure of a motor vehicle according to a first embodiment;
• 2 a schematic rear view of a storage device for supporting the refrigerant compressor on the structure;
• 3 a schematic plan view of the storage device according to 2 ;
• 4th a schematic side view of the storage device according to 2 and 3 ;
• 5 a fragmentary schematic perspective view of the storage arrangement according to a second embodiment;
• 6th a schematic rear view of a storage device for storing the refrigerant compressor according to the second embodiment;
• 7th a schematic plan view of the storage device according to 6th and
• 8th a schematic side view of the storage device according to 6th and 7th .

Identical or functionally identical elements are provided with the same reference symbols in the figures.

1 shows a section of a first embodiment of a bearing arrangement in a schematic perspective view 1 of a refrigerant compressor 2 on one as a self-supporting body 3 trained structure of a motor vehicle. The motor vehicle is preferably designed as a passenger vehicle and in its fully manufactured state comprises the self-supporting body 3 and the storage arrangement 1 and thus the refrigerant compressor 2 . In particular, the motor vehicle is designed as an electric vehicle. In the storage arrangement 1 is the refrigerant compressor 2 at least essentially decoupled or at least essentially damped on the self-supporting body 3 stored. A storage facility is used for this 4th used, which is explained in more detail below by.

The refrigerant compressor 2 is part of the car's air conditioning system. The air conditioning system has a refrigerant circuit through which a refrigerant can flow, the refrigerant compressor 2 is arranged in the refrigerant circuit. During operation of the refrigerant compressor 2 is the refrigerant by means of the refrigerant compressor 2 conveyed through the refrigerant circuit, and during operation the refrigerant is by means of the refrigerant compressor 2 condensed. For example, it is in the refrigerant circuit downstream of the refrigerant compressor 2 a cooling device is arranged, which is designed or functions, for example, as a capacitor. The refrigerant is cooled by means of the cooling device. In the refrigerant circuit, for example, an expansion member, in particular an expansion valve, is arranged downstream of the cooling device, by means of which the compressed and for example liquid refrigerant is expanded or relaxed. In the refrigerant circuit, for example, is downstream of the expansion element and upstream of the refrigerant compressor 2 a heating device which functions or is designed, for example, as an evaporator and by means of which the refrigerant can be heated. For example, heat from air which flows around the heating device can be transferred to the refrigerant via the heating device, whereby the air is cooled. The cooled air can be introduced into the interior of the motor vehicle and thus supplied to the interior. The air conditioning system is thus designed, for example, as a compression air conditioning system or as a compression refrigeration machine.

The refrigerant compressor 2 is also referred to as a refrigerant compressor, compressor or compressor and has a housing 5 on, in which, for example, a conveying element is arranged. The conveying element is relative to the housing 5 movable, the refrigerant by means of the refrigerant compressor by moving the conveying element 2 is to be promoted and condensed. In particular, the conveying element is about an axis of rotation relative to the housing 5 rotatable, so that, for example, to convey the refrigerant, the conveying element about the axis of rotation relative to the housing 5 is rotated. The axial direction of the refrigerant compressor falls, for example 2 with the axis of rotation.

Preferably the refrigerant compressor is 2 designed as an electrically operated refrigerant compressor. This includes the refrigerant compressor 2 an electric motor by means of which the use of electrical energy moves the conveying element relative to the housing 5 is movable or is moved in order to convey and compress the refrigerant. In doing so, illustrate 1 to 4th a first embodiment of the storage arrangement 1 and thus a first embodiment of the storage device 4th . The storage facility 4th comprises according to the first embodiment at least or exactly four first bearing elements 6a-d which are separate from the refrigerant compressor 2 are formed, spaced from each other and elastically deformable. The storage device also includes 4th one separate from the bearing elements 6a-d , separate from the body 3 and separate from the refrigerant compressor 2 trained holder 7th on which the refrigerant compressor 2 over the first bearing elements 6a-d is stored. The bearing elements 6a-d allow relative movements between the refrigerant compressor 2 and the holder 7th to. With such relative movements between the refrigerant compressor 2 and the holder 7th become the bearing elements 6a-d elastically deformed. As a result, vibration energy is converted into deformation energy, thereby reducing the relative movements between the refrigerant compressor 2 and the holder 7th be dampened.

Out 3 and 4th it is particularly easy to see that the storage facility 4th in the first embodiment at least or exactly 4 second bearing elements 8a-d has, which in addition to the first bearing elements 6a-d provided from each other and from the first bearing elements 6a-d are spaced and elastically deformable. In the storage arrangement 1 is the holder 4th over the second bearing elements 8a-d on the self-supporting body 3 stored. The bearing elements 8a-d allow relative movements between the holder designed or functioning as an intermediate mass 7th and the body 3 to. With such relative movements between the holder 7th and the body 3 become the bearing elements 8a-d elastically deformed. This converts vibration energy into combustion energy, which reduces the relative movements between the holder 7th and the body 3 be dampened. The bearing elements 6a-d are designed separately from each other. Alternatively or additionally, the bearing elements are 8a-d formed separately from each other. In particular, the bearing elements 8a-d separate from the bearing elements 6a-d educated. Furthermore are the bearing elements 8a-d separate from the body 3 , separate from the refrigerant compressor 2 , separate from the holder 7th and separate from the bearing elements 6a-d educated.

Out 1 it can be seen that the bearing element 6a is on a first side 9 of the refrigerant compressor 2 , especially the housing 5 , is arranged. The bearing element 6b is on one side 9 remote second side 10 of the refrigerant compressor 2 , especially the housing 5 , arranged. The bearing element 6c is on a third side 11 of the refrigerant compressor 2 , especially the housing 5 , with the third side facing away from the first side and the second side. Finally, the bearing element 6d is on a fourth side 12th of the refrigerant compressor 2 , especially the housing 5 , arranged, with the side 12th the sides 9 , 10 and 11 is turned away. This allows the refrigerant compressor 2 Particularly advantageous in terms of vibration on the holder 7th be stored. Especially good 3 it can be seen that the holder 7th is designed as a holding frame which has a through opening 13th limited. The refrigerant compressor is here 2 in the through opening 13th arranged, the refrigerant compressor 2 , especially the case 5 , the through opening 13th can penetrate. Furthermore is the through opening 13th along their in 3 by an arrow 14th illustrated circumferential direction completely circumferentially through the holder 7th limited and therefore completely closed all round.

Overall it's over 1 to 4th recognizable that the first bearing elements 6a-d form a first decoupling level, while the bearing elements 8a-d form an additional, second decoupling level. In this case, vibrations can be dampened particularly advantageously by means of the decoupling planes, so that excessive vibrations caused by the refrigerant compressor 2 brought about or can be brought about stimulation of the body 3 can be avoided. As a result, unwanted, excessive noise can be avoided. Thus, through the storage arrangement 1 or by the storage facility 4th a particularly advantageous noise behavior of the motor vehicle can be shown.

5 to 8th show a second embodiment of the storage arrangement 10 and thus the storage facility 4th . In the second embodiment there are exactly four first bearing elements 6a-d provided, exactly three second bearing elements 8a-c are provided.

The respective bearing element 6a-d respectively 8a-d is designed, for example, as a rubber bearing and thus made of a rubber. The respective decoupling level is also referred to as a storage level, for example. With regard to the first decoupling level, the refrigerant compressor is 2 for example in its center of gravity and on its circumference by means of the first bearing elements 6a-d stored. On a front side and thus, for example, on a front housing part of the housing 5 the bearing element 6d is provided, which situational and tilting movements of the refrigerant compressor 2 relative to the holder 7th counteracts. The respective bearing element 6a-d has a single bearing stiffness. The single bearing stiffness of the bearing elements 6a-d together or in total result in a first overall bearing rigidity of the first decoupling level. Advantageous for a design of the bearing elements, which are also simply referred to as bearings 6a-d is the sum of the effective single bearing stiffnesses of all bearing elements 6a-d in respective spatial directions. For example, a first of the spatial directions runs perpendicular to a second of the spatial directions, with the first spatial direction, for example, being an axial direction and the second spatial direction being a radial direction. For example, the axial direction is the axial direction of the refrigerant compressor 2 while the radial direction is the radial direction of the refrigerant compressor 2 can be. In the first embodiment, for example, the respective individual bearing rigidity of the respective first bearing element is 6a-d along the first spatial direction 17 N / mm, the respective single bearing stiffness of the respective first bearing element 6a-d along the second spatial direction is, for example, 8 N / mm. In the second embodiment, for example, the respective individual bearing rigidity of the respective first bearing element is 6a-d along the first spatial direction 45 N / mm, the respective single bearing stiffness of the respective first bearing element 6a-d is, for example, 7 N / mm along the second spatial direction. In particular, it is possible in the second embodiment, for example, that the respective individual bearing rigidity of the respective first bearing element 6a-d lies along the first spatial direction in a range from and including 18 N / mm up to and including 40 N / mm, in particular while the respective individual bearing rigidity of the respective first bearing element 6a-d along the second spatial direction is 7 N / mm.

Also the respective second bearing element 8a-d has, for example, per se, that is, considered on its own or per se, a respective individual bearing stiffness.

The respective individual bearing stiffnesses of the bearing elements 8a-d together or in total result in a second overall bearing stiffness of the second decoupling level. For example, in the first embodiment, the respective individual bearing rigidity of the respective second bearing element is 8a-d along the first spatial direction 15 N / mm, with the respective individual bearing rigidity of the respective second bearing element in the first embodiment 8a-d can be, for example, 35 N / mm along the second spatial direction.

For example, in the second embodiment, the respective individual bearing rigidity of the respective second bearing element is 8a-d along the first spatial direction 32 N / mm. Furthermore, it can be provided that in the second embodiment the respective individual bearing rigidity of the respective second bearing element 8a-d along the second spatial direction is 38 N / mm. Furthermore, it is conceivable that in the second embodiment the respective individual bearing rigidity of the respective second bearing element 8a-d lies along the first spatial direction in a range from and including 24 N / mm to and including 32 N / mm, in particular while the respective individual bearing rigidity of the respective second bearing element 8a-d along the second spatial direction is 38 N / mm. Overall it can be seen that the holder 7th as an intermediate mass over the three or four bearing elements 8a-d with the most even weight distribution possible in a front end of the motor vehicle on the body, also known as the vehicle body 3 attached and thus stored. For example, the respective bearing element is here 8a-d designed as a rubber mount. Also with regard to the second storage level, there is a need to design the bearing elements 8a-d the sum of the effective single bearing stiffnesses of all bearing elements 8a-d advantageous in the respective spatial directions.

The intermediate mass is specifically designed, for example, depending on the respective individual bearing stiffnesses or overall bearing stiffnesses, in order to provide sufficient insulation with regard to a decoupled storage of the refrigerant compressor 2 on the body 3 to realize. This is particularly advantageous with regard to the first natural frequency of the holder 7th . In the first embodiment the intermediate mass is 10 kg, for example, the intermediate mass in the second embodiment being 15 kg, for example. The structural modes of the holder, also known as the intermediate holder 7th is preferably due to the refrigerant compressor 2 brought about or can be brought about excitation, which is, for example, greater than 150 Hz, matched to avoid resonance excitation.

The respective bearing element 6a-d respectively 8a-d has a characteristic curve, also referred to as a bearing characteristic or damping characteristic, which, for example, shows progressive behavior in the end stop and enables a linear oscillation path in the context of all design-relevant driving maneuvers in order to adequately isolate the refrigerant compressor 2 opposite the body 3 to enable. The oscillation path is 7 mm, for example. In other words, it is preferably provided that the bearing elements 6a-d respectively 8a-d allow an oscillation path over which the refrigerant compressor 2 relative to the holder 7th or the holder 7th relative to the body 3 can oscillate, the respective characteristic curve of the respective bearing element 6a-d respectively 8a-d is or runs linearly over the preferably entire oscillation path. It has been found that there are strong interactions between the respective design parameters, so that a decoupling system formed by the intermediate mass and the decoupling level, by means of which the refrigerant compressor 2 decoupled from the body 3 is stored, is designed as a complete system.

List of reference symbols

1

Storage arrangement

2

Refrigerant compressor

3

body

4th

Storage facility

5

casing

6a-d

Bearing element

7th

holder

8a-d

Bearing element

9

page

10

page

11

page

12

page

13th

Through opening

14th

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QUOTES INCLUDED IN THE DESCRIPTION

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

Patent literature cited

• DE 10392645 T5 [0002]
• DE 19807923 A1 [0002]
• DE 102007048936 B4 [0002]

Claims (11)

Storage device (4) for mounting a refrigerant compressor (2) on a structure (3) of a motor vehicle, with a holder (7) formed separately from the refrigerant compressor (2) as an intermediate mass, with several elastically deformable first bearing elements (6a- d), via which the refrigerant compressor (2) is mounted on the holder (7), and with a plurality of elastically deformable and spaced apart from one another and from the first bearing elements (6a-d) provided in addition to the first bearing elements (6a-d) second bearing elements (8a-d), via which the holder (7) is to be mounted on the structure (3). Storage device (4) after Claim 1 , characterized in that at least a first of the first bearing elements (6a-d) on a first side (9) of the refrigerant compressor (2), at least a second of the first bearing elements (6a-d) on a second side facing away from the first side (9) Side (10) of the refrigerant compressor (2) and at least a third of the first bearing elements (6a-d) is arranged on a third side (11) of the refrigerant compressor (2) facing away from the first side (9) and the second side (10). Storage device (4) after Claim 1 or 2 , characterized in that the respective first bearing element (6a-d) has a bearing rigidity which, along a first direction, is in a range from 10 N / mm up to and including 55 N / mm, in particular in a range from 15 N / mm up to and including inclusive 45 N / mm and preferably in a range from inclusive 17 N / mm up to inclusive 40 N / mm, and along a second direction running perpendicular to the first direction in a range from inclusive 5 N / mm up to and including 15 N / mm, in particular in a range from 7 N / mm inclusive to 10 N / mm inclusive. Bearing device (4) according to one of the preceding claims, characterized in that the respective second bearing element (8a-d) has a bearing rigidity which, along a first direction, is in a range from 10 N / mm up to and including 40 N / mm, in particular in a range from 15 N / mm up to and including 35 N / mm and along a second direction running perpendicular to the first direction in a range from 30 N / mm up to 45 N / mm inclusive, in particular in a range from 35 N / mm inclusive up to and including 40 N / mm. Storage device (4) after Claim 3 or 4th , characterized in that the first direction is the axial direction of the refrigerant compressor (2), the second direction being the radial direction of the refrigerant compressor (2). Storage device (4) according to one of the preceding claims, characterized in that the intermediate mass is at least 7 kg, in particular at least 10 kg. Storage device (4) according to one of the preceding claims, characterized in that the intermediate mass is at most 20 kg, in particular at most 15 kg. Storage device (4) according to one of the preceding claims, characterized in that the holder (7) is designed as a holding frame which delimits a through opening (13) in which the refrigerant compressor (2) is at least partially arranged. Storage device (4) according to one of the preceding claims, characterized in that the refrigerant compressor (2) is designed as an electrically operated refrigerant compressor. Storage device (4) according to one of the preceding claims, characterized in that at least three first bearing elements (6a-d) and / or at least three second bearing elements (8a-d) are provided. Storage arrangement (1) of a refrigerant compressor (2) on a structure (3) of a motor vehicle, in which the refrigerant compressor (2) via several, spaced apart and elastically deformable first bearing elements (6a-d) on a separate from the refrigerant compressor (2) and separately from the structure (3) formed holder (7) is mounted as an intermediate mass, which is provided via several, in addition to the first bearing elements (6a-d), spaced apart and from the first bearing elements (6a-d) and elastically deformable second bearing elements (8a-d) is mounted on the structure (3).

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