DE102016217267A1 - Arrangement for a refrigeration system with a scroll compressor - Google Patents

Abstract

The invention relates to an arrangement for a refrigeration system with a scroll compressor (12) for compressing refrigerant, with a drive and with a controllable speed converter (14) which couples the drive with the scroll compressor (12). In order to improve the adaptability of the cooling capacity of the refrigeration system, it is proposed that the speed converter (14) is infinitely variable.

Description

The invention relates to an arrangement for a refrigeration system with a scroll compressor for compressing refrigerant, with a drive and with a controllable speed converter, which couples the drive with the scroll compressor, in particular according to the preamble of claim 1. Furthermore, the invention relates to a motor vehicle with a refrigeration system having such an arrangement.

In refrigeration systems in motor vehicles, which are used, for example, for air conditioning systems, the air conditioning compressor is often driven indirectly via the internal combustion engine present in the motor vehicle. In order to control the cooling capacity, the pumping power of the compressor must be able to be controlled. When using scroll compressors, this can only be done by controlling the speed of the scroll compressor.

From the DE 10 2006 035 364 A1 It is known to control the scroll compressor via a planetary gear to the internal combustion engine. Therefore, different gear ratios are possible. Nevertheless, the performance of the scroll compressor can not be set exactly to the necessary requirements.

The present invention has for its object to provide an improved or at least other embodiment of an arrangement for a refrigeration system with a scroll compressor available, which is characterized in particular by a finer adjustment of the cooling capacity. Further, the invention has the object to provide an improved or at least other embodiment of a motor vehicle with a refrigeration system, which is characterized in particular by the fact that the cooling capacity of the refrigeration system can be finer regulated.

This object is solved by the subject matters of the independent claims. Advantageous developments are the subject of the dependent claims.

The invention is based on the general idea to couple the scroll compressor, which is coupled to the drive, with a controllable speed converter to the drive, which is infinitely variable. As a result, the speed of the scroll compressor can be adjusted almost independently of the speed of the drive, so that independent of the speed of the drive control of the cooling capacity is possible.

An advantageous possibility provides that the speed converter is a hydraulic converter. Such hydraulic transducers are easy to control and already proven in automotive engineering.

Another favorable possibility provides that the speed converter has a first shaft, and a second shaft, that the speed converter has a working space in which first fins, which are coupled to the first shaft, and second fins, which are coupled to the second shaft are arranged, and that for controlling and / or regulating the transmitting torque between the first shaft and the second shaft, a working fluid can be introduced and discharged into the working space. When the working fluid is in the working space, a power transmission between the first fins and the second fins is provided, so that a torque between the first shaft and the second shaft can be transmitted. If the working fluid is drained and replaced by a gas, for example, air, the transmission of forces between the first fins and the second fins is greatly reduced, so that only a very small torque is transmitted. In general, such a speed converter allows a slip between the first shaft and the second shaft, so that thereby the speed of the scroll compressor can be adjusted independently of the speed of the drive. It is understood that the first shaft or the second shaft coupled to the drive and the respective other shaft is coupled to the scroll compressor, so that the speed converter can transmit the drive power of the drive to the scroll compressor and at the same time can reduce the speed variable.

Another particularly favorable possibility provides that a pump device is provided, with which the working fluid can be introduced and discharged and is. As a result, the level of the working fluid in the working space can be selectively changed. As a result, the transmitted torque from the drive to the scroll compressor can be adjusted, which in turn can affect the speed of the scroll compressor.

An advantageous solution provides that the working fluid is hydraulic oil. Such hydraulic oil is, for example, in motor vehicles for a variety of systems in use, so it is advisable to use this hydraulic oil also for the speed converter.

A further advantageous solution provides that the speed converter is a viscous coupling. Such viscous couplings have proven themselves in the automotive industry. They allow the transmission of torques while reducing the speed. This can be with a viscous coupling torque from the drive to the Spiral compressor and simultaneously adjust the speed of the scroll compressor almost independent of the speed of the drive.

A further advantageous solution provides that the speed converter has a first shaft and a second shaft, that the rotational speed has an eccentric held on the first shaft, that the speed converter has a displacement element which is driven by the eccentric that the speed converter has an outer Rotor, which is coupled to the second shaft, that in the speed converter between the displacer and the outer rotor at least two chambers are formed whose volume is changed by the displacer in the rotation of the first shaft to the second shaft that Überströmkanäle are formed , which connects each of the chambers with a compensation volume, and that a control is provided, which can control the flow cross-section of the transfer channels. Thus, when the first shaft rotates relative to the second shaft, the volumes of the chambers are changed so that the medium located in the speed converter must flow in or out through the transfer ports into the chambers. If now the flow cross section of the transfer channels is varied, this compensation is thus slowed down. Thereby, the rotation of the first shaft is braked to the second shaft, whereby a torque between the first shaft and the second shaft can be transmitted. Consequently, by adjusting the flow cross-section of the transfer ports, a transmitted torque from the first shaft to the second shaft can be controlled. Thus, with the aid of such a speed converter, which allows a slip between the first shaft and the second shaft, the speed of the scroll compressor can be set at least approximately independently of the speed of the drive.

A favorable variant provides that the overflow channels are formed in the outer rotor. As a result, the control and the compensation volume can be arranged lying on the outside, which allows a particularly simple arrangement.

Another favorable variant provides that the overflow channels are formed in the displacement element. This allows a very compact design can be achieved.

Another particularly favorable variant provides that the overflow channels are formed in the housing. As a result, for example, an axial guidance of the overflow channels can be achieved, so that a compact construction in the radial direction can be achieved.

It is understood that the overflow can be formed in the radial or axial direction. Depending on an axial or radial compact design can be achieved.

In the description and in the appended claims, the terms axially and radially refer to one of the shafts of the speed converter.

An advantageous possibility provides that the control is annular, and for each overflow channel has an opening that the openings are in an open position in alignment with the overflow, that the openings in a throttle position partially overlap with the overflow and that the openings in one Closed position adjacent to the overflow, so that the overflow are closed. As a result, the flow cross sections of all overflow channels can be controlled with a single control element. Consequently, the control torque can be used to adjust the transmitted torque between the first shaft and the second shaft.

A further advantageous possibility provides that a plurality of rotational locking elements are provided which change a rotation of the displacement element to the outer rotor and that the rotational locking elements separate the chambers from each other. Thus, the rotation locking elements cause a double action. First, they form the chambers through which the torque can be transmitted. On the other hand, they cause the rotation lock of the displacer to the outer rotor.

A particularly advantageous possibility provides that the displacement element has an outer circumferential surface, which is n-fold rotationally symmetrical, that the outer rotor has an inner circumferential surface which is rotationally symmetrical (n + 1) -fach and which is designed such that the displacement element with its outer circumferential surface can roll on it, and that when rolling the displacer on the inner circumferential surface of the outer rotor, the chambers are formed. In particular, not only the chambers are formed and dissolved during rolling of the displacer on the inner circumferential surface of the outer rotor, but also reduces the volume of the respective chambers and increased again. As a result, a flow is induced by the overflow channels, so that the throttling of the overflow channels can be used to transmit a torque between the first and the second shaft.

A favorable solution provides that the speed converter is a mechanical converter. This means that no fluids are used to increase the power transfer. Such mechanical speed converter are usually very low loss.

Another favorable solution provides that the speed converter is a belt or chain with a belt drive. The belt or chain may then abut against a first conical wheel of varying diameter in the axial direction and a second conical wheel, which preferably has a diameter varying in the axial direction, and thus, depending on the position of the belt or chain, a different ratio between them cause two wheels. Such stepless belt transmissions allow variable transmission. As a result, by selecting the ratio, the rotational speed of the scroll compressor can be set at least largely independently of the rotational speed of the drive.

An advantageous variant provides that the speed converter is a variable friction gear. Even such Reibradgetriebe allow a continuous adjustment of the transmission ratio.

Further, the invention is based on the general idea to equip a motor vehicle with a refrigeration system having an arrangement according to the above description, wherein an internal combustion engine of the motor vehicle is coupled via the speed converter with the scroll compressor. As a result, the advantages of the arrangement are transferred to the motor vehicle, to the above description of which reference is made.

Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

Show, in each case schematically,

1 a schematic diagram and partial sectional view, wherein a scroll compressor shown cut and arranged thereon a speed converter is indicated only schematically,

2 a longitudinal sectional view through a speed converter according to a first embodiment,

3 a cross-sectional view through a speed converter according to a second embodiment,

4 a cross-sectional view through a speed converter according to a third embodiment and

5 a longitudinal sectional view of a speed converter according to a fourth embodiment.

One in the 1 and 2 illustrated arrangement 10 for a refrigeration system is preferably used for a refrigeration system in a motor vehicle with an internal combustion engine. The arrangement comprises a scroll compressor 12 , which serves as a compressor for the refrigeration system. This scroll compressor 12 is about a speed converter 14 to a drive, in particular the internal combustion engine of the motor vehicle, connected. The drive is not shown in the figures.

The scroll compressor has at least one fixed spiral 16 and a moving spiral 18 on. Furthermore, the scroll compressor 12 an eccentric 20 on which the movable spiral 18 is mounted and through which the movable scroll is moved in a circular path. The solid spiral 16 and the moving spiral 18 are arranged inside each other, so that a variable volume between the fixed spiral 16 and the movable spiral 18 is formed. By the orbital motion of the movable scroll thus a pumping action can be achieved. Such a formed scroll compressor 12 forms a volumetric pump whose pumping volume is fixed to the speed of the scroll compressor 12 is coupled.

To regulate the pumping capacity of the scroll compressor and thus the cooling capacity of the refrigeration system, the speed of the scroll compressor 12 be controllable.

For this purpose, the arrangement 10 the speed converter 14 on. As exemplified in 2 shown, the speed converter 14 to be a hydraulic speed converter. For example, this may be designed as a viscous coupling.

The speed converter 14 has a first wave 22 and a second wave 24 on, between which a torque can be transmitted, at the same time a slip between the two waves 22 . 24 is possible. This allows the drive, so the internal combustion engine of the motor vehicle, the scroll compressor 12 drive. At the same time, the speed of the scroll compressor 12 differ from the speed of the drive, since the speed converter 14 allowed a slip.

The speed converter 14 has several first fins 26 and several second fins 28 on that in a workroom 30 are arranged. The first slats 26 are with the first wave 22 rotationally coupled while the second fins 28 with the second wave 24 are rotationally coupled.

The workroom 30 is through a bell 32 educated. The bell 32 is with the first wave 22 connected. The first slats 26 extend from an outer wall of the bell 32 radially inward. The second slats 28 extend from the second shaft 24 out radially to the outside. Further, the second wave 24 coaxial with the bell 32 and thus arranged coaxially with the first shaft.

In the workroom 30 are the first fins 26 and second fins 28 in the axial direction next to each other and overlap in the radial direction. Will now be the first wave 22 opposite the second wave 24 turned the first slats paint 26 at the second fins 28 past.

To achieve a torque transfer, the working space 30 be filled with a working fluid. This working fluid can be, for example, hydraulic oil. Both the first fins 26 as well as the second fins 28 drive the working fluid in the work space 30 which causes torques between the first fins 26 and the second fins 28 can be transmitted. Depending on the level of working fluid in the workspace 30 results in a transmitted torque. Consequently, by the amount of working fluid in the working space 30 the transmittable torque can be adjusted.

Thus, also the speed of the scroll compressor 12 with the help of the level of working fluid in the working space 30 be set. It is understood that the speed converter 14 According to the first embodiment, the speed can only reduce. Therefore, the speed of the scroll compressor 12 not be controlled independently of the speed of the drive, but at least approximately independent.

One in the 3 illustrated second embodiment of the arrangement 10 for a refrigeration system differs from that in the 1 and 2 illustrated first embodiment of the arrangement 10 for a refrigeration system by the construction of the speed converter 14 , The speed converter 14 according to the second embodiment has one on the first shaft 22 held eccentric 34 on which a displacement element 36 drives when the first wave 22 is turned. The displacer element 36 is preferably annular and has on an outer surface at least two, for example. Seven, axial grooves 38 on. In the axial grooves 38 are rotation locking elements 40 arranged, which is a rotation of the displacement element 36 hinder. The rotation lock elements 40 However, allow the movement of the displacer 36 on one through the eccentric 34 given circular path.

Furthermore, the speed converter 14 an outer rotor 42 on, which is preferably annular. The outer rotor 42 with the second wave 24 rotatably coupled. The outer rotor 42 encloses an interior 44 in which the eccentric 34 and the displacer 36 are arranged. On an inner surface 46 the outer rotor 42 are at least two, for example, seven, axial grooves 48 educated. In the axial grooves 48 are the rotation lock elements 40 added. As a result, connect the rotational locking elements 40 the axial grooves 38 of the displacement element 36 with the axial grooves 48 the outer rotor 42 , so by the rotation locking elements 40 the rotation of the displacer element 36 to the outer rotor 42 is blocked.

By the rotation locking elements 40 , the displacer 36 and the outer rotor 42 are chambers 50 formed, their volume by the movement of the displacer 36 is increased or decreased.

In the outer rotor 42 are also overflow channels 52 formed, which a fluidic connection of the chambers 50 to produce a compensation volume, not shown. The overflow channels 52 are, such as in 3 represented formed radially and thereby connect a radially outwardly arranged equalization volume with the chambers 50 , But it is also possible that the transfer channels 52 formed in the axial direction, for example. In a housing of the speed converter 14 , so that the equalizing volume in the axial direction next to the chambers 50 is arranged.

Furthermore, the speed converter 14 a control 54 on, which is preferably annular and at least two, for example. Seven openings 56 having. Preferably, each overflow channel 52 an opening 56 intended. The openings 56 are so in the control 54 arranged to be at outlets of overflow channels 52 can be arranged in alignment.

The control 54 is arranged such that it is the outer rotor 42 surrounds, leaving the openings 56 of the control 54 in alignment with the overflow channels 52 can be arranged. In such an open position, the control limits 54 not the flow cross section of the transfer channels. Will now be the control 54 opposite the outer rotor 42 twisted, the openings shift 56 opposite the overflow channels 52 , whereby the available flow cross-section through the overflow 52 is reduced. In such a throttle position can by the control 54 the flow through the transfer channels 52 be slowed down or throttled. Furthermore, a position is possible in which the openings 56 next to the overflow channels 52 lie. This closes the control 54 the overflow channels 52 almost completely, so that the transfer channels are almost closed in this closed position.

Through the control 54 Thus, the flow resistance of working fluid, which is in the compensation volume and the chambers 50 is located, control. To the orbit movement of the displacer 36 and thus a rotation of the first wave 22 opposite the second wave 24 to allow the working fluid through the transfer ports 52 stream. These are now through the control 54 throttled is a torque between the first shaft 22 and the second wave 24 transfer. Thus, with the help of the control 54 the torque transmission of the speed converter 14 to be controlled.

Incidentally, the in 3 illustrated second embodiment of the arrangement 10 with the in the 1 and 2 illustrated first embodiment of the arrangement 10 for a refrigeration system in terms of structure and function match, the above description of which reference is made.

An in 4 illustrated third embodiment of the arrangement 10 for a refrigeration system is different from the one in 3 illustrated second embodiment of the arrangement 10 for a refrigeration system in that the chambers 50 without rotation locking elements 40 are formed. Instead, the displacement element 36 an outer circumferential surface 58 on, which is rotationally symmetrical and so on the inner circumferential surface 46 the outer rotor 42 adapted is that the displacement element 36 with its outer circumferential surface 58 on the inner circumferential surface 46 the outer rotor 42 can roll. In this case, the outer circumferential surface 58 of the displacement element 36 n-fold rotationally symmetric and the inner circumferential surface 46 the outer rotor 42 (n + 1) -fold rotationally symmetric.

Will now be the displacer 36 through the eccentric 34 forced to the circular path, rolls at the same time the displacer 36 on the inner circumferential surface 46 the outer rotor 42 from. Thus, therefore, there is also a rotation of the displacer 36 opposite the outer rotor 42 , In this case, several, for example. Four chambers between the displacer 36 and the outer rotor 42 formed, whose volume through the rotation of the first shaft 22 to the second wave 24 and thus the circular movement of the displacement element 36 relative to the outer rotor 42 , be increased or decreased.

The speed converter 14 according to the second embodiment also has overflow 52 on which the chambers 50 connect to the equalization volume. Due to the design are in the speed converter 14 according to the third embodiment, an overflow channel 52 more provided as chambers 50 in the speed converter 14 are formed. This results from the fact that the overflow 52 in the outer rotor 42 are arranged, which has an n + 1-fold symmetry, while the displacer 36 an n-fold, for example 4-fold, as in 4 is shown having symmetry. Therefore, it is necessary with the 5-fold rotationally symmetric outer rotor 42 also five overflow channels 52 to arrange. If the transfer channels in the displacer 36 arranged, would N, so four, overflow 52 suffice.

The control 54 is according to the control 54 formed the second embodiment.

Incidentally, the in 4 illustrated third embodiment of the arrangement 10 for a refrigeration system with the in 3 illustrated second embodiment of the arrangement 10 for a refrigeration system in terms of structure and function match, the above description of which reference is made.

An in 5 illustrated fourth embodiment of the arrangement 10 for a refrigeration system differs from that in the 1 and 2 illustrated first embodiment of the arrangement 10 for a refrigeration system in that instead of a hydraulic speed converter 14 a mechanical speed converter 14 is used. The mechanical speed converter 14 is like in 5 represented formed as a friction ring gear.

At the first wave 22 is a first conical wheel 60 held. At the second wave 24 is a second conical wheel 62 arranged. In this fourth embodiment, the first shaft 22 and the second wave 24 not arranged coaxially with each other. Instead, lie the first wave 22 and the second wave 24 next to each other and overlap in the respective mutually facing end regions. This causes the first conical wheel 60 and the second conical wheel 62 radially next to each other, leaving a gap 64 between the first conical wheel 60 and the second conical wheel 62 is formed. Here are the cone angles of the first conical wheel 60 and the second conical wheel 62 and the angle of the first wave 22 to the second wave 24 chosen such that the gap 64 has a preferably constant width over its length. This can be achieved, for example, in that the first shaft 22 and the second wave 24 are arranged axially parallel to each other and the first conical wheel 60 and the second conical wheel 62 have the same cone angle.

Furthermore, the speed converter 14 a friction ring 66 on, which through the gap 64 runs and thus both in contact with the first conical wheel 60 as well as with the second conical wheel 62 is. In the example in 5 illustrated position of the friction ring 66 touches the friction ring 66 the second conical wheel 62 at a point where the second conical wheel 62 has a large diameter and the first conical wheel 60 at a point where the first conical wheel 60 has a small diameter. This allows a large gear ratio between the speeds of the first shaft 22 and the second wave 24 be achieved. Will now be the friction ring 66 shifted so that the point of contact with the first conical wheel 60 and the second conical wheel 62 shifts in itself, the ratio of the first wave changes 22 to the second wave 24 , This is because the diameters, at the points where the friction ring 66 the two conical wheels 60 . 62 touched, changed. If, for example, the friction ring 66 would be arranged rightmost, would the friction ring 66 the second conical wheel 62 touch at a point where the diameter is smaller while it is the first conical wheel 60 would touch at a location where the diameter of the first conical wheel 60 is great. This would increase the gear ratio compared to the in 5 just reverse the position shown in the example.

Thus, by the speed converter 14 a transmission formed with a variable transmission ratio. Thus, the speed of the scroll compressor 12 be set largely independent of the speed of the drive.

Incidentally, the in 5 illustrated fourth embodiment of the arrangement 10 for a refrigeration system with in the 1 and 2 illustrated first embodiment of the arrangement 10 for a refrigeration system in terms of structure and function match, the above description of which reference is made.

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

• DE 102006035364 A1 [0003]

Claims (11)

Arrangement for a refrigeration system with a scroll compressor ( 12 ) for compressing refrigerant, with a drive and with a controllable speed converter ( 14 ), the drive with the scroll compressor ( 12 ), characterized in that the speed converter ( 14 ) is infinitely variable. Arrangement for a refrigeration system according to claim 1, characterized in that the speed converter ( 14 ) is a hydraulic converter. Arrangement for a refrigeration system according to claim 2, characterized in that - the speed converter ( 14 ) a first wave ( 22 ) and a second wave ( 24 ), - that the speed converter ( 14 ) a work space ( 30 ), in which first lamellae ( 26 ), with the first wave ( 22 ), and second fins ( 28 ), with the second wave ( 24 ) are arranged, and - that for controlling and / or regulating the transmitted torque between the first shaft ( 22 ) and the second wave ( 24 ) a working fluid into the working space ( 30 ) can be introduced and discharged. Arrangement for a refrigeration system according to claim 2, characterized in that - the speed converter ( 14 ) a first wave ( 22 ) and a second wave ( 24 ), - that the speed converter ( 14 ) one at the first wave ( 22 ) held eccentric ( 34 ), - that the speed converter ( 14 ) a displacer element ( 36 ), which by the eccentric ( 34 ), - that the speed converter ( 14 ) an outer rotor ( 42 ) connected to the second shaft ( 24 ), that - in the speed converter ( 14 ) between the displacer element ( 36 ) and the outer rotor ( 42 ) at least two chambers ( 50 ) are formed whose volume through the displacement element ( 36 ) during rotation of the first wave ( 22 ) to the second wave ( 24 ), - that overflow channels ( 52 ) are formed, which each of the chambers ( 50 ) connects to a compensation volume, and - that a control ( 54 ) is provided, which has a flow cross section of the transfer channels ( 52 ) can control. Arrangement for a refrigeration system according to claim 4, characterized in that - the control element ( 54 ) is annular, and for each overflow ( 52 ) an opening ( 56 ), - that the openings ( 56 ) in an open position in alignment with the overflow channels ( 52 ), - that the openings ( 56 ) in a throttle position partially with the overflow channels ( 52 ) overlap, and - that the openings ( 56 ) in a closed position next to the overflow channels ( 52 ), so that the overflow channels ( 52 ) are closed. Arrangement for a refrigeration system according to claim 4 or 5, characterized in that - several rotational locking elements ( 40 ) are provided which a rotation of the displacement element ( 36 ) to the outer rotor ( 42 ), and - that the rotational locking elements ( 40 ) the chambers ( 50 ) separate each other. Arrangement for a refrigeration system according to claim 4 or 5, characterized in that - the displacement element ( 36 ) an outer circumferential surface ( 58 ) which is n-fold rotationally symmetric, - that the outer rotor ( 42 ) an inner circumferential surface ( 46 ), which is rotationally symmetrical (n + 1) -fach and which is formed such that the displacement element ( 36 ) with its outer circumferential surface ( 58 ) can roll on it, and - that when rolling the displacer ( 36 ) on the inner surface ( 46 ) of the outer rotor ( 42 ) the chambers ( 50 ) are formed. Arrangement for a refrigeration system according to claim 1, characterized in that - the speed converter ( 14 ) is a mechanical transducer. Arrangement for a refrigeration system according to claim 1 or 8, characterized in that the speed converter ( 14 ) is a variable belt transmission with a belt or a chain. Arrangement for a refrigeration system according to claim 1 or 8, characterized in that the speed converter ( 14 ) is a variable friction gear. Motor vehicle with a refrigeration system comprising an arrangement ( 10 ) according to one of claims 1 to 10, wherein an internal combustion engine of the motor vehicle via the speed converter ( 14 ) with the scroll compressor ( 12 ) is coupled.

Images