EP3126672B1 - Reciprocating-piston compressor and control method therefor - Google Patents

Description

The present invention relates to a reciprocating compressor according to the preamble of patent claim 1, as well as a reciprocating compressor having refrigeration or air conditioning or a Hubkolbenverdichter having heat pump according to claims 6 and 7. Furthermore, in the thought of the present invention, a corresponding control method is included.

Refrigeration systems are often operated with reciprocating compressors. Examples of this can be found inter alia in the field of bus air conditioning, where in a corresponding refrigeration system (air conditioning) a reciprocating compressor is arranged, which is driven by the crankshaft of the drive motor via a belt drive and a magnetic coupling. The compressor can be switched on and off via the magnetic coupling. However, the shut-off and shut-off affects the entire compressor and thus the entire power output of the compressor (100% on-off). Other examples can be found in the field of mobile and stationary air conditioning, mobile and stationary refrigeration, so for example in the field of transport refrigeration and supermarket refrigeration, and in the field of heat pumps.

The connection and disconnection causes a transient operation of the compressor and leads also to high peak loads in its drive. The switching frequency is basically limited by the masses to be moved and the switching work of the clutch.

In the compressors, for example, four-cylinder reciprocating compressors are predominantly used in the field of bus air conditioning, in which two individual cylinder banks are arranged in V-construction. In other applications, other reciprocating compressors with any number of cylinders are used, wherein the cylinders may be arranged in cylinder banks or may be divided into such or not.

By operating on a diesel engine, for example, in mobile applications, in particular mobile air-conditioning applications, compressors are constantly operated at a rotational speed corresponding to the driving operation, which does not coincide with a rotational speed at which the compressor would produce the desired cooling capacity. For this reason, there is a continuous need for correction of the cooling or cooling capacity.

A similar problem arises, for example, in some transport refrigeration systems.

It is known that this, e.g. can be partially compensated in passenger car by stroke-controlled axial piston compressor. There, the stroke is steplessly adjusted to near zero, thus partially compensating for the unwanted speed. This construction, which is common in small compressors, does without an independent oil system and works sufficiently well in limited systems with limited lifetimes for cars. A transfer to commercial vehicles with their larger benefits and longer life requirements, however, has not succeeded in series today.

In the area of bus air conditioning, it is known to switch off a cylinder bank (= two cylinders = 50%) in the case of four-cylinder V-compressors or to shift them into a state in which no delivery rate is provided by the corresponding cylinder bank. This is done by shutting off the suction gas flow for the corresponding cylinder bank. The compressor then runs under zero delivery, compresses against final pressure and reexpandes the gas, with the compression work being returned to the crankshaft becomes. With such a scheme, a bus air conditioning system can already be regulated somewhat more finely, namely in 50% steps, but this is still not enough if a high control quality is to be achieved.

A reciprocating compressor of the prior art is in US3119550 disclosed. It shows a reciprocating compressor with a control device having an input for supplying input information, in particular suction or high pressure of a corresponding compressor, and at least one output for controlling a control element, the reciprocating compressor a shut-off device, in particular a valve, further in particular a check valve which, viewed in a flow direction of the refrigerant during normal operation of the reciprocating compressor, is arranged downstream of the high-pressure volume. The reciprocating compressor has at least one suction gas volume and at least one high-pressure volume, wherein a connection between the at least one suction gas volume and the at least one high-pressure volume of the reciprocating compressor is formed. The at least one suction gas volume and the at least one high-pressure volume are integrated in the Hubkobenverdichter. Accordingly, it is an object of the present invention to provide a reciprocating compressor for a variety of applications, such as refrigeration, air conditioning, or heat pump applications, which has over the prior art, an increased control quality. It is another object of the present invention to provide corresponding systems, as well as a corresponding control method.
This object is achieved by a reciprocating compressor according to claim 1. The second aspect of the problem is solved by systems according to claims 6 and 7. The procedural aspect of the problem is solved by a method according to claim 8.
A corresponding reciprocating compressor has a control device which is provided for particular stepless control of a capacity of the reciprocating compressor and which has an input for supplying input information, in particular a suction pressure or a high pressure of the compressor, and at least one output for controlling a control element. The control device is designed to generate a digital output signal, wherein the control element has a digitally controllable control valve. The reciprocating compressor has at least one suction gas volume and at least one high-pressure volume, wherein a connection between the at least one suction gas volume and the at least one high-pressure volume of the refrigeration system is formed, and wherein the digitally controllable control valve is arranged in the connection. The reciprocating compressor further comprises a shut-off device, in particular a valve, further in particular a check valve, which, viewed in a flow direction of the refrigerant during normal operation of the compressor, downstream of the one / each associated high-pressure volume is arranged. The at least one suction gas volume and the at least one high-pressure volume and the control valve are integrated in the reciprocating compressor.
The connection between the high-pressure volume and the suction volume of the compressor can be at simultaneously closing one of the high pressure side associated and downstream in the operating flow direction of the refrigerant the high pressure volume shut-off, resulting in the two aforementioned volumes associated piston or cylinder banks or possibly all cylinders or cylinder banks of the compressor in a state of zero promotion of refrigerant spend. By integrating the high-pressure volume into the compressor, the smallest possible high-pressure volume is ensured, which ensures that the compressor operates in an energy-efficient manner.

With regard to the system aspect, the object is achieved by devices according to claim 6 or 7, which have a corresponding reciprocating compressor.

It is proposed in the entire compressor and / or cylinder banks or cylinder groups, possibly also individual cylinders with a quickly switchable controllability (digital control) equip. As a result, the compressor can be controlled virtually continuously from 100% to preferably about 10% of its nominal delivery volume or its maximum delivery volume.

Furthermore, a method for regulating a delivery rate of a reciprocating compressor or a refrigeration system equipped therewith by a digital signal within the scope of the present invention is included.

Finally, it should be noted that in the idea of the present invention, the use of a digitally controllable valve is included as a control valve for the flow rate of a reciprocating compressor in a control device for a refrigeration system.

Further optional features of the invention are specified in the dependent claims, as well as the following description of the figures. In the description of the figures, the invention will be described using the example of a device for bus air conditioning (refrigeration system for bus air conditioning or bus air conditioning system). However, it should be noted at this point that a refrigeration system according to the invention can be used in many applications, for example a refrigeration system for a trailer, generally in a transport refrigeration system, but also in a stationary refrigeration system (for example supermarket refrigeration).

• Fig. 1 eine schematische Darstellung eines Busses mit einer schematischen Darstellung einer ersten möglichen Ausführungsform der Erfindung im Einsatz in einer Klimaanlage desselben;
• Fig. 2 eine Teilansicht des Verdichters, wie er in Fig. 1 schematisch dargestellt ist
• Fig. 3 und 4 jeweils eine schematische Ansicht eines Teilausschnitts (Schnittansicht) des Verdichters gemäß Fig. 2; und
• Fig. 5 eine schematische Darstellung eines Verdichters, der in einer zweiten möglichen Ausführungsform einer erfindungsgemäßen Kälteanlage Verwendung findet.

The described respective features can be realized individually or in any desired combinations. The invention will therefore be described below with reference to the attached drawings by means of exemplary embodiments. In the drawings show:

• Fig. 1 a schematic representation of a bus with a schematic representation of a first possible embodiment of the invention in use in an air conditioner thereof;
• Fig. 2 a partial view of the compressor, as in Fig. 1 is shown schematically
• 3 and 4 each a schematic view of a partial section (sectional view) of the compressor according to Fig. 2 ; and
• Fig. 5 a schematic representation of a compressor which is used in a second possible embodiment of a refrigeration system according to the invention.

As in FIG. 1 1, a refrigeration system or air conditioning system 1 in the form of a bus climate system 1 comprises, as essential components, a compressor 10 for compressing refrigerant, which is designed as a reciprocating compressor, and a control device 12, which controls a control 14 and a control device in the form of a shut-off device a valve 16. In addition to an application of a compressor according to the invention in the climate sector, the areas stationary and mobile refrigeration as well as the area of heat pumps are mentioned by way of example.

The control device 12 further comprises an input 18 for supplying input information, which in the presently described embodiment is represented by a suction pressure of the compressor 10, and an output 20 for controlling the control element (valve 16), as well as a delivery volume determining device for determining a desired Delivery volume in response to an input signal applied to the input 18 and for generating a corresponding output 20 to be supplied to the output signal on. While in refrigeration or air conditioning systems, the input is preferably the suction pressure of the compressor 10, the input is in the case of heat pumps, for example, preferably the high pressure, ie the pressure which rests against the high-pressure side of the compressor 10.

The control device 12 is configured to generate a digital output signal. To implement the digital output signal, the valve 16, which regulates the delivery volume of the compressor 10, designed as a digitally controllable electromagnetic valve. Alternatively, other types of valve, in particular electromechanical or else mechanically, pneumatically or hydraulically operable valves or other shut-off devices (slides and the like.) Are conceivable.

The refrigeration system 1 has a suction gas volume 22 and a high pressure volume 24, wherein the suction gas volume 22 is arranged upstream of the cylinders of the compressor 10, and the high pressure volume 24 is arranged downstream of the cylinders of the compressor 10, the direction determinations upstream and downstream in a normal operation of the Refrigeration system 1 are defined by the flow direction of the refrigerant. Between the suction gas volume 22 and the high-pressure volume 24 is a connection 26 in the form of a bore or recess, for example in the housing of the compressor 10 or as a pipe, wherein the digitally controllable valve 16 is arranged in the connection 26 and open and interrupt or can close.

The refrigeration system 1 further has a second shut-off device in the form of a check valve 28 (second valve), which is arranged downstream of the high-pressure volume 24. It is instead of a check valve 26, any other shut-off device (slide, valve, for example, electromechanically actuated or solenoid-operated or pneumatically actuated valve, or a diaphragm or the like.) Possible.

The suction gas volume 22 and the high-pressure volume 24 are connected to each other through the above-mentioned connection 26, for example piping (bypass line), which can be opened and closed by the digitally controllable valve 16 such that the suction gas volume 22 and the high-pressure volume 24 directly into each other (Fluid) connection stand when the valve 16 is in an open position.

If the valve 16 is in a closed position, there is no direct connection between suction gas volume 22 and high-pressure volume 24. The compressor 10 is in normal operation (cf. Fig. 3 ), in which refrigerant is conducted from the suction gas volume 22 into the cylinders, is compressed therein, and then discharged into the high pressure volume 24 and provided to the bus air conditioning system 1 (the path of the refrigerant is indicated by arrows, respectively).

However, when the valve 16 is in its open position (see also Fig. 4 In an open position of the valve 16, the check valve 28 closes by the high pressure and thus keeps the high pressure away from the working spaces of the compressor. Thus, the absorbed power of the compressor drops to the unavoidable value, which arises from the internal losses of the compressor, for example at the working valves. In alternative embodiments, another shut-off device is closed, for example, by the control device 12. Thus, the compressor 10 is "turned off" because the conveyed through the cylinder refrigerant flows from the high-pressure volume 24 back into the suction gas volume 22 and from there in turn into the cylinder and then turn enters the high-pressure volume 24.

The opening duration of the valve 16 can be carried out by the control device 12 in an arbitrary, continuously variable clocking, so that a delivery rate of the compressor 10 of basically 0% to 100% is infinitely variable or nearly infinitely variable. However, in the presently described embodiment, the control device 12 is configured to provide a minimum displacement of 5% to 10% to cool the compressor 10. For air-cooled compressors only, this can be dispensed with.

It should be additionally noted that the described refrigeration system 1 has a condenser 30, an expansion element in the form of an expansion valve 32 and an evaporator 34 for air conditioning the vehicle (bus) 36 / for cooling the volume to be cooled. A set point with which the suction pressure, which is desired and thus to be regulated, is determined, is fed from the volume (in the embodiment described from the vehicle 36) which is to be conditioned.

Like from the FIGS. 2 to 4 it can be seen, the described embodiment of a refrigeration system 1 according to the invention has the suction gas volume 22 and the high-pressure volume 24 integrated in the compressor 10. The connection 26 between the suction gas side and the high-pressure side is preferably formed between the suction gas volume 22 and the high-pressure volume 24 in the form of a channel (alternatively as a bore or as a recess formed in the casting of the corresponding components, alternatively also as a pipeline). The valve 16 is arranged in the connection 26 (channel) as in the above-described embodiment, and thus also integrated in the compressor 10. Again, all conceivable types of valves and also other shut-off devices are conceivable, as have already been described in connection with the embodiment explained above. In particular, in systems in which high pressures are achieved, an integration of the volumes and the valve in the compressor 10 may be advantageous. The operation is identical to the first embodiment in the second embodiment.

As is apparent from the schematic representation in Fig. 5 a compressor 10 of a second embodiment of a refrigeration system according to the invention, which is also designed as a reciprocating cylinder, two cylinder groups in the form of two cylinder banks 40 (the cylinders need not necessarily be grouped as cylinder banks 40, other criteria for grouping are conceivable).

The refrigeration system 1, more precisely the reciprocating compressor 10 of the refrigeration system 1 has per cylinder bank 40 (in alternative embodiments per cylinder group or per cylinder) a suction gas volume 22 for feeding the respective cylinder bank 40 with refrigerant and a high-pressure volume 24 for discharging the refrigerant. The respective volumes of suction gas 22 are disposed upstream of the respective cylinder banks 40 associated therewith, while the respective high pressure volumes 24 are located downstream of the respective associated cylinder banks 40. In the illustrated embodiment, the suction gas volumes 22 and the high-pressure volumes 24 are disposed within the compressor 10, ie, integrated therein. Between the first cylinder bank 40 associated Sauggasvolumen 22 and the first cylinder bank 40 associated high-pressure volume 24, a compound 26 is formed, which connects the two volumes together. In the connection, a digitally controllable valve 16 is arranged. An analogous construction is realized for the second cylinder bank 40 associated volumes. Between the second cylinder bank 40 associated Sauggasvolumen 22 and the second cylinder bank 40 associated high-pressure volume 24, a further (second) connection 26 is formed, which connects the two volumes together. In the connection, a digitally controllable valve (third valve) 16 is arranged. The connections 26 are formed as pipelines.

The valves 16 are formed analogously to the valve 16 already described in the first and second embodiments and may also be substituted by any other shut-off device, wherein at least one of the shut-off devices must be digitally controllable in order to obtain the desired control precision. It would alternatively also be conceivable that only one cylinder bank 40 assigned volumes a connection 26 (for example, pipe or channel) is provided. The valves 16 are controlled by the control device 12. Also in this embodiment, both the compound (s) 26 and the high-pressure volumes and volumes of suction gas are integrated in the compressor 10.

By a construction according to the second embodiment, a shutdown and connection of individual cylinder groups (cylinder banks 40) take place. It is therefore proposed to actuate cylinder banks 40 or cylinder groups, possibly also individual cylinders, with a quickly switchable controllability. As a result, the compressor 10 can be controlled steplessly or virtually continuously or in any increments from 100% to approximately 10%, the lower limit being determined thermally and by the oil balance of the compressor 10. The shift of the Zylinderbänke40 or cylinder groups, possibly also individual cylinders can be carried out asynchronously, so that the time of total zero promotion can be limited.

It should be noted at this point that it is also included within the scope of the present application that the compound (s) 26 and / or the valve (s) 16 and / or the volumes of suction gas (or volumes) and / or the high pressure volume (s) are located outside the compressor. This is a simple construction, but may be energetically somewhat less effective than the embodiments described above, since in particular the Hochdruckv and the high-pressure volumes are greater than those described above Embodiments. In addition, with an integration of the components in the compressor uncomplicated installation and also an uncomplicated design by the manufacturer of the respective air conditioning or refrigeration system or heat pump, etc. possible.

As an example of a possible control is: with a desired refrigerant delivery corresponding to 50-100% of the rated power clocked a cylinder bank 40 up to the complete shutdown (at 50%); with a desired refrigerant delivery corresponding to 50-10% of the nominal capacity both banks clock with increasing overlap. At 10%, e.g. each bank in turn 6s per minute.

Another advantage of this scheme is that the starting torque of the compressor 10 can be limited by, for example, all cylinders are switched off at start. This makes it possible to limit the size of couplings and also drives, are driven by the corresponding compressor 10 in the rule. Also, the torque can generally be controlled and limited in order to protect the clutch in operation against a possible overload.

Another possibility is to switch off one or more cylinder banks 40 or cylinder groups or cylinders each time the clutch is switched on. This reduces the switching work of the clutch. This possibility exists even when switching off the compressor 10, so that even when the compressor 10 is separated from the drive, the torque is reduced.

In decentralized systems and individual compressor systems, such as in buses or in transport refrigeration, a relieved start-up of the compressor 10 is of particular importance, since the drive components can be dimensioned correspondingly weaker. In this respect, reference should also be made in particular to an application as a power control for CO ₂ compressors that can develop too much heat in other methods and at the same time can get into the dry ice area.

It should be noted at this point that a corresponding method for controlling a refrigeration system 1 is included in the idea of the present application. The inventive method for controlling the refrigeration system 1 is as follows represents.

The inventive method is used to control a reciprocating compressor 10, for example, a refrigeration or air conditioning 1 or a heat pump, the control of the refrigeration system 1 is accomplished by controlling the flow rate of the compressor 10. The control of the flow rate is performed by at least one digital signal , The digital signal or digital signals can be supplied to one or more digitally controllable control valve (s) 16. In possible embodiments, the refrigeration system 1 has at least one suction gas volume 22 and at least one high-pressure volume 24, wherein a connection 26 is formed between the at least one suction gas volume 22 and the at least one high-pressure volume 24 of the reciprocating compressor 10, wherein the regulation of the delivery rate of the compressor 10 by a Open and close the connection 26 controlled by the digital signal, in particular by means of the digitally controllable control valve 16 takes place.

The refrigeration system can have a plurality of cylinder groups, in particular cylinder banks 40, and more than one suction gas volume 22, in particular a suction gas volume 22 for each cylinder group, and more than one high pressure volume 24, in particular a high pressure volume 24 for each cylinder group, wherein at least one connection 26 between one of the suction gas volumes 22 and a corresponding high pressure volume 24 of the refrigeration system 1 is formed. The control of the delivery rate of the compressor 10 is effected by opening and closing the connection 26 controlled by the digital signal, in particular by means of the digitally controllable control valve 16.

Preferably, a connection 26 is formed between each of the suction gas volumes 22 and each corresponding high-pressure volume 24 of the refrigeration system 1, wherein the control of the delivery rate of the compressor 10 is controlled by opening and closing the connections 26 controlled by the digital signal, in particular by means of digitally controllable control valves 16. The opening and closing of connections 26 assigned to different cylinder groups preferably takes place asynchronously during operation of the refrigeration system 1.

In one possible embodiment of a method according to the invention is a method for controlling a reciprocating compressor 10, which, as already explained, has a control device 12 and is provided for compressing refrigerant. The regulation of the reciprocating compressor 10 is accomplished by controlling the capacity of the compressor 10, wherein the control of the flow rate is performed by at least one digital signal, wherein the digital signal or digital signals one or more digitally controllable control valve (s) 16 is fed.Der reciprocating compressor 10 has at least one suction gas volume 22 and at least one high pressure volume 24, wherein a connection between the at least one suction gas volume 22 and the at least one high pressure volume 24 of the refrigeration system is formed, wherein the control of the capacity of the compressor controlled by opening and closing the connection by the digital signal is carried out in particular by means of the digitally controllable control valve 16. The reciprocating compressor 10 has a shut-off device 28, which, viewed in a flow direction of the refrigerant during normal operation of the reciprocating compressor 10, downstream of the high-pressure volume 24 is arranged, wherein the shut-off device 28 is closed when the connection 26 is opened, and wherein the shut-off device 28 is open when the connection 26 is closed.

The control device controls one or more control valves such that a delivery volume of 5% to 10% of the nominal delivery volume or maximum delivery volume of the compressor 10 is provided as a minimum delivery volume and / or that 100% of the nominal delivery or nominal delivery volume or the maximum Delivery volume or the maximum capacity is provided as a maximum delivery volume. Between the minimum delivery volume and the maximum delivery volume is preferably varied or regulated continuously.

1. 1. Verfahren zum Regeln eines Hubkolbenverdichters mit einer Regelvorrichtung , wobei das Regeln der Kälteanlage durch eine Regelung der Förderleistung des Verdichters bewerkstelligt wird, wobei die Regelung der Förderleistung durch wenigstens ein digitales Signal erfolgt.
2. 2. Verfahren nach 1., wobei das digitale Signal oder digitale Signale einem oder mehreren digital ansteuerbaren Regelventil(en) zugeführt wird.
3. 3. Verfahren nach 1. oder 2., wobei die Kälteanlage wenigstens ein Sauggasvolumen und wenigstens ein Hochdruckvolumen aufweist, wobei eine Verbindung zwischen dem wenigstens einen Sauggasvolumen und dem wenigstens einen Hochdruckvolumen der Kälteanlage ausgebildet ist, wobei die Regelung der Förderleistung des Verdichters durch ein Öffnen und Schließen der Verbindung gesteuert durch das digitale Signal insbesondere mittels des digital ansteuerbaren Regelventils erfolgt.
4. 4. Verfahren nach 1., 2. oder 3.,wobei die Kälteanlage mehrere Zylindergruppen, insbesondere Zylinderbänke, und mehr als ein Sauggasvolumen, insbesondere ein Sauggasvolumen für jede Zylindergruppe, und mehr als ein Hochdruckvolumen, insbesondere ein Hochdruckvolumen für jede Zylindergruppe aufweist, wobei wenigstens eine Verbindung zwischen einem der Sauggasvolumen und einem korrespondierenden Hochdruckvolumen der Kälteanlage ausgebildet ist, wobei die Regelung der Förderleistung des Verdichters durch ein Öffnen und Schließen der Verbindung gesteuert durch das digitale Signal insbesondere mittels des digital ansteuerbaren Regelventils erfolgt.
5. 5. Verfahren nach 4., wobei eine Verbindung zwischen jedem der Sauggasvolumina und einem korrespondierenden Hochdruckvolumen der Kälteanlage ausgebildet ist, wobei die Regelung der Förderleistung des Verdichters durch ein Öffnen und Schließen der Verbindungen gesteuert durch das digitale Signal insbesondere mittels digital ansteuerbarer Regelventile erfolgt.
6. 6. Verfahren nach nach einem der Punkte 1. bis 5., wobei der Verdichter eine oder mehrere Zuführung(en) für zu verdichtendes Kältemittel aufweist, wobei bei einem Verdichter, der mehrere Zylindergruppen, insbesondere Zylinderbänke aufweist, insbesondere eine Zuführung für jede Zylindergruppe vorgesehen ist, wobei die Regelung der Förderleistung durch ein Öffnen und Schließen der Verbindung gesteuert durch das digitale Signal insbesondere mittels des digital ansteuerbaren Regelventils erfolgt.
7. 7. Verfahren nach einem der Punkte 1. bis 6., wobei die Regelvorrichtung ein oder mehrere Regelventile derart ansteuert, dass ein Fördervolumen von 5% bis 10% des Nenn-Fördervolumens oder maximalen Fördervolumens des Verdichters als minimales Fördervolumen vorgesehen ist.

The following method is further included in the present disclosure:

1. 1. A method for controlling a reciprocating compressor with a control device, wherein the rules of the refrigeration system is accomplished by controlling the flow rate of the compressor, wherein the control of the flow rate is performed by at least one digital signal.
2. 2. The method of 1., wherein the digital signal or digital signals to one or more digitally controllable control valve (s) is supplied.
3. 3. The method according to 1 or 2, wherein the refrigeration system comprises at least one suction gas volume and at least one high pressure volume, wherein a connection between the at least one suction gas volume and the at least one high pressure volume of the refrigeration system is formed, wherein the control of the capacity of the compressor by opening and closing the connection controlled by the digital signal, in particular by means of the digitally controllable control valve.
4. 4. The method according to 1, 2 or 3, wherein the refrigeration system comprises a plurality of cylinder groups, in particular cylinder banks, and more than a suction gas volume, in particular a suction gas volume for each cylinder group, and more than one high pressure volume, in particular a high pressure volume for each cylinder group at least one connection between one of the suction gas and a corresponding high-pressure volume of the refrigeration system is formed, wherein the control of the capacity of the compressor is controlled by opening and closing the connection by the digital signal, in particular by means of the digitally controllable control valve.
5. 5. The method of 4., wherein a connection between each of the suction gas and a corresponding high-pressure volume of the refrigeration system is formed, wherein the control of the capacity of the compressor is controlled by opening and closing the connections by the digital signal, in particular by means of digitally controllable control valves.
6. 6. The method according to any one of items 1 to 5, wherein the compressor has one or more feed (s) for refrigerant to be compressed, wherein provided in a compressor having a plurality of cylinder groups, in particular cylinder banks, in particular a supply for each cylinder group is, wherein the control of the delivery rate by opening and closing the connection is controlled by the digital signal in particular by means of the digitally controllable control valve.
7. 7. The method according to any one of items 1 to 6, wherein the control device is an or controls a plurality of control valves such that a delivery volume of 5% to 10% of the nominal delivery volume or maximum delivery volume of the compressor is provided as a minimum delivery volume.

Reference numerals:

1

Refrigeration system or air conditioning

10

compressor

12

control device

14

regulation

16

Control element or valve

18

entrance

20

output

22

suction gas

24

High volume printing

26

connection

28

check valve

30

capacitor

32

expansion valve

34

Evaporator

36

Vehicle (bus)

40

cylinder bank

Claims (9)

1. A reciprocating-piston compressor (10) having a regulating device (12) comprising an input (18) for the supply of input information, in particular suction pressure or high pressure of a corresponding compressor (10), and has at least one output (20) for the actuation of a regulating element (16),
   wherein the regulating device (12) is designed to generate a digital output signal,
   wherein the regulating element has a digitally actuable regulating valve (16),
   wherein the reciprocating-piston compressor (10) has at least one suction-gas volume (22) and at least one high-pressure volume (24), wherein a connection (26) is formed between the at least one suction-gas volume (22) and the at least one high-pressure volume (24) of the reciprocating-piston compressor (10), wherein the digitally actuable regulating valve (16) is arranged in the connection (26),
   wherein the reciprocating-piston compressor (10) has a shut-off device, in particular a valve, furthermore in particular a check valve (28), which is arranged downstream of the high-pressure volume (24) as viewed in a flow direction of the refrigerant during normal operation of the reciprocating-piston compressor (10),
   wherein the at least one suction-gas volume and the at least one high-pressure volume and the regulating valve (16) are integrated into the reciprocating piston compressor (10),
   wherein the regulating device (12) is provided for the continuously variable regulation of a delivery rate of the reciprocating-piston compressor (10).
2. The reciprocating-piston compressor (10) as claimed in claim 1,
   wherein the compressor (10) has multiple cylinder groups, in particular cylinder banks (40).
3. The reciprocating-piston compressor (10) as claimed in claim 1 or 2,
   wherein the reciprocating-piston compressor (10) has more than one suction-gas volume (22), in particular one suction-gas volume (22) for each cylinder group, and more than one high-pressure volume (24), in particular one high-pressure volume (24) for each cylinder group, wherein at least one connection (26) is formed between one of the suction-gas volumes (22) and a corresponding high-pressure volume (24) of the reciprocating-piston compressor (10), wherein the/a digitally actuable regulating valve (16) is arranged in the connection (26).
4. The reciprocating-piston compressor (10) as claimed in claim 3,
   characterized in that
   a connection (26) is formed between each suction-gas volume (22) and between each high-pressure volume (24) respectively corresponding therewith, wherein a digitally actuable regulating valve (16) is arranged in the respective connection (26).
5. The reciprocating-piston compressor (10) as claimed in one of the preceding claims,
   characterized in that
   the reciprocating-piston compressor (10), in particular the regulating device (12), is designed to regulate the delivery volume of the compressor (10) from 5%, in particular 10%, of a nominal delivery rate or of a maximum delivery rate up to 100% thereof.
6. A refrigeration installation or air-conditioning installation having a reciprocating-piston compressor (10) as claimed in one of the preceding claims.
7. A heat pump having a reciprocating-piston compressor (10) as claimed in one of the preceding claims.
8. A method for regulating a reciprocating-piston compressor (10) which has a regulating device (12) and which is provided for the compression of refrigerant, wherein the regulation of the reciprocating-piston compressor is effected by regulation of the delivery rate of the compressor (10), wherein the regulation of the delivery rate is realized by way of at least one digital signal, wherein the digital signal or digital signals are supplied to one or more digitally actuable regulating valve(s) (16),
   wherein the reciprocating-piston compressor (10) has at least one suction-gas volume (22) and at least one high-pressure volume (24), wherein a connection is formed between the at least one suction-gas volume (22) and the at least one high-pressure volume (24) of the reciprocating-piston compressor (10), wherein the regulation of the delivery rate of the compressor is performed by opening and closing of the connection in a manner controlled by the digital signal, in particular by way of the digitally actuable regulating valve (16), wherein the reciprocating-piston compressor (10) has a shut-off device (28) which is arranged downstream of the high-pressure volume (24) as viewed in a flow direction of the refrigerant during normal operation of the reciprocating-piston compressor (10), wherein the shut-off device (28) is closed when the connection (26) is open, and wherein the shut-off device is open when the connection (26) is closed,
   wherein continuous variation, or continuously variable regulation, is performed between the minimum delivery volume and the maximum delivery volume.
9. The method as claimed in claim 8, wherein the regulating device actuates one or more regulating valves such that a delivery volume of 5% to 10% of the nominal delivery volume or maximum delivery volume of the compressor is provided as a minimum delivery volume, and/or such that 100% of the nominal delivery rate or nominal delivery volume or of the maximum delivery volume or of the maximum delivery rate is provided as a maximum delivery volume.

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