ITCO20110070A1 - METHODS AND DEVICES FOR CONSTRUCTIVE USE OF PRESSURE PULSES IN INSTALLATIONS OF ALTERNATIVE COMPRESSORS - Google Patents

Description

TITLE / TITLE:

METHODS AND DEVICES FOR CONSTRUCTIVELY USING THE PRESSURE PULSATIONS IN RECIPROCATING COMPRESSORS INSTALLATIONS

KNOWN ART TECHNICAL FIELD

The embodiments of the object disclosed in this document refer in general to installations for which reciprocating compressors are used in the oil and gas sector and, more precisely, to the constructive use of pressure pulsations to improve the volumetric efficiency of the compressor, obtaining, for example, a pulse loading effect.

TREATMENT OF KNOWN ART

Compressors used in the oil and gas sector must comply with industry-specific requirements which take into account, for example, the fact that compressed gas is often corrosive and flammable. The American Petroleum Institute (API), the organization that sets the recognized industry standard for equipment used in the oil and gas industry, has issued a document, API618, which lists the full set of minimum requirements for reciprocating compressors.

Compressors can be classified as volumetric compressors (e.g. reciprocating, screw or vane compressors) and dynamic compressors (e.g. centrifugal or axial compressors). In volumetric compressors, compression is obtained by trapping the gas and reducing the volume in which it is contained. In dynamic compressors, compression is obtained by transforming the kinetic energy (e.g. that of the rotating element) into pressure energy at a predetermined point inside the compressor.

An ideal compression cycle (graphically illustrated in Figure 1 by plotting the evolution of pressure versus volume) includes at least four stages: expansion, intake, compression and exhaust. When the compressed fluid is evacuated from a compression chamber at the end of the compression cycle, a small amount of fluid at the delivery pressure P1 remains trapped in a noxious space V1 (i.e. the minimum volume of the compression chamber). During the expansion phase 1 and the suction phase 2 of the compression cycle, the piston moves to increase the volume of the compression chamber. At the beginning of the expansion phase 1, the delivery valve closes (while the suction valve remains closed) and, therefore, the pressure of the trapped fluid decreases as the volume available in the compression chamber increases. The suction phase of the compression cycle begins when the pressure inside the compression chamber becomes equal to the suction pressure P2 and the suction valve is activated by opening to the volume V2. During the suction phase 2 the volume of the compression chamber and the quantity of fluid to be compressed (at pressure P2) increase until the maximum volume of the compression chamber V3 is reached.

During the compression and exhaust phases of the compression cycle, the piston moves in the opposite direction to that of the expansion and suction phases in order to reduce the volume of the compression chamber. During the compression phase 3 both the inlet and outlet valves are closed (and therefore the fluid does not enter or leave the cylinder) and the fluid pressure in the compression chamber increases (from the suction pressure P2 to the delivery pressure Pi) as the volume inside it decreases to V4. The delivery phase 4 of the compression cycle begins when the pressure inside the compression chamber becomes equal to the delivery pressure Pi and the opening of the delivery valve is activated. During the delivery phase 4 the fluid at the delivery pressure P2 is evacuated from the compression chamber until the minimum (harmful) volume V1 of the compression chamber is reached.

A measure of the compressor efficiency is represented by the volumetric efficiency, which is the ratio between the volume of the compression chamber crossed by the piston of the reciprocating compressor during the suction phase V3-V2 and the total volume V3-V1 crossed by the piston during the cycle. compression.

The phenomenon of pressure pulsations, which occurs outside the reciprocating compressor, is due to the discontinuous nature of the gas flow inside the reciprocating compressor itself. These pressure pulsations can cause large vibrations and fatigue stresses, a high level of noise and reduced compressor performance. Document API618 includes detailed requirements for an acoustics study to be carried out during the design of an installation including a reciprocating compressor, which has among its purposes that of avoiding the detrimental effect of pressure pulsations. To prevent these pulsations from spreading throughout the installation, pulsation dampers are installed before the suction valves and after the discharge valves of the compressors to protect the reciprocating compressor from the rest of the installation.

For example, Figure 2 shows a simplified model of an interface between a reciprocating compressor 10 and the rest of the installation. In this case the term "interface" refers to all the components present between the valve 20 of the reciprocating compressor 10 and the pipe 30 through which the gas is channeled from the rest of the installation or towards it (for example a system for oil and gas). The reciprocating compressor 10 has a piston 40 and is connected through a tube 50 to a pulsation damper 60. The pulsation damper 60 is then connected to the oil and gas system through the pipeline of the system 30.

The pulsation damper 60, filled with the gas to be compressed or with the compressed gas (depending on whether the damper precedes the intake valve or follows the exhaust valve or reciprocating compressor 10), is characterized by a high acoustic impedance and acts as a pulse reflector, allowing only a small fraction to be transmitted to the system pipeline 30.

The frequency of the pressure pulsations generated by the reciprocating compressor 10 is the frequency of the compression process within the reciprocating compressor. Resonance occurs when the natural frequency f of pipeline 30 equals the frequency of the pressure pulses generated by the reciprocating compressor. The natural frequency f of the pipe 50 depends on the speed of sound in the gas c and on the length L of the pipe 50. According to a first approximation, there is the following relationship between these quantities: f = c / (2L). In the event that standing pressure waves are formed along the tube 50, the holes (i.e. the circumscribed constriction of the tube) can be used to reduce the amplitude of the aforementioned standing pressure waves.

In this way the pressure pulsations (which occur inherently, due to the discontinuous nature of the gas flow, in a reciprocating compressor) are conventionally dissipated and not used.

It would be desirable to provide methods and devices (included or practiced in oil and natural gas installations including a reciprocating compressor) that constructively utilized pressure pulsation to improve the efficiency of the reciprocating compressor.

SUMMARY

Some of the embodiments have a valve with an actuator and a device for the circulation of the gas configured in such a way as to have a resonance frequency substantially equal to the frequency of the compression cycles performed inside the reciprocating compressor. The valve is operated to improve the volumetric efficiency of the compressor, constructively using intrinsic pressure pulsations. This way of using pressure pulses to increase efficiency is known as the pulse loading effect. According to an exemplary embodiment, an apparatus comprises a gas circulation device and a controller. The gas circulation device provides a path through which gas (to be compressed or freshly compressed) circulates between a reciprocating compressor and a pulsation damper, which protects the gas flow connection of the reciprocating compressor with the oil plant it's gas. The device for the circulation of the gas is configured in such a way as to have a resonance frequency substantially equal to the frequency of the compression cycles running inside the reciprocating compressor. The controller is configured to adjust the timing of the activation of the valve located between the reciprocating compressor and the gas circulation device, in order to constructively use the pressure pulsations that occur in the gas circulation device, to increase the 'volumetric efficiency of the reciprocating compressor.

According to another exemplary embodiment, a method is provided for using the pulse loading effect to improve the volumetric efficiency of a reciprocating compressor. The method involves the need for a gas circulation device between a reciprocating compressor valve and a pulsation damper, which protects the reciprocating compressor itself from the oil and gas system, with the gas circulation device configured in such a way as to have a resonant frequency substantially equal to the frequency of the compression cycles running inside the reciprocating compressor. The method also provides for the control of the timing of the activation of the valve to constructively use the pressure pulsations that occur inherently within the device for the circulation of the gas, in order to improve the volumetric efficiency of the reciprocating compressor. .

In another exemplary embodiment, a method is proposed for introducing innovations to the installation of a reciprocating compressor. The installation reciprocating compressor has an outlet or inlet protected from the rest of the installation by a pulsation damper. The installation of the reciprocating compressor is improved to utilize the pulse loading effect of the reciprocating compressor itself, in order to increase its volumetric efficiency. The method involves modifying the gas circulation device that connects an outlet or inlet of the reciprocating compressor to the pulsation damper, by adding at least one acoustic resonator to a pipe of the gas circulation device, to make so that it has a resonant frequency substantially identical to the frequency of the compression cycles in progress inside the reciprocating compressor. The method also involves connecting a valve between the reciprocating compressor and the gas circulation device to a controller configured to adjust the timing of the valve activation in order to constructively use the pressure pulsations that occur in the gas circulation device. gas circulation to increase the volumetric efficiency of the reciprocating compressor.

BRIEF DESCRIPTION OF THE DRAWINGS

The technical drawings annexed to the detailed description, and of which they form an integral part, represent one or more embodiments and, together with the description, explain these embodiments. In the drawings:

Figure 1 is a graph of pressure versus volume illustrating an ideal compression cycle;

Figure 2 is a schematic diagram of a conventional interface between a reciprocating compressor and an oil and gas plant;

Figure 3 is a schematic diagram of an interface between a reciprocating compressor and an oil and gas plant, according to an exemplary embodiment;

Figure 4 is a schematic diagram of an interface between a reciprocating compressor and an oil and gas plant, according to an exemplary embodiment;

Figure 5 is a schematic diagram of an interface between a reciprocating compressor and an oil and gas plant, according to an exemplary embodiment;

Figure 6 is a schematic diagram of an interface between a reciprocating compressor and an oil and gas plant, according to an exemplary embodiment;

Figure 7 is a schematic diagram of an interface between a reciprocating compressor and an oil and gas plant, according to an exemplary embodiment;

Figure 8 is a schematic diagram of an interface between a reciprocating compressor and an oil and gas plant, according to an exemplary embodiment;

Figure 9 is a flow chart of a method of using inherently generated pulsations during operation of a reciprocating compressor, which is intended to increase the efficiency of the compressor, according to an exemplary embodiment, and

Figure 10 is a flow chart of a method for introducing innovations to the installation of a reciprocating compressor, according to an exemplary embodiment.

DETAILED DESCRIPTION

The following description of the exemplary embodiments refers to the attached technical drawings. Like reference numerals, occurring in different drawings, represent similar or identical elements. The following detailed description does not limit the invention. On the contrary, the scope of the invention is defined by the included claims. The following embodiments are discussed, for the sake of simplicity, in relation to the terminology and structure of reciprocating compressors used in an oil and gas plant (i.e., installation or equipment). However, the embodiments to be discussed below are not limited to this system, but can be applied to other similar technical conditions.

Throughout the detailed description, reference to "an embodiment" means that a particular feature, structure or property described in connection with an embodiment is included in at least one embodiment of the disclosed object. Therefore, the use of the expression "in one embodiment" at various points of the detailed description will not necessarily refer to the same embodiment. Further, the particular functions, structures or features can be combined in any suitable way in one or more embodiments.

In some embodiments described below, a gas circulation device, which provides a path through which the gas (to be compressed or just compressed) circulates between a reciprocating compressor (i.e. the compression chamber above) and a pulsation damper. The device for the circulation of the gas is configured in such a way as to have a resonance frequency substantially equal to the frequency of the compression cycles running inside the reciprocating compressor. Furthermore, a valve located between the compression chamber and the gas circulation device is controlled to be opened in relation to the pressure pulsation phase next to the valve in the gas circulation device so as to increase the efficiency of the compressor.

If we consider that the valve is the suction valve, a higher pressure inside the gas circulation device next to the suction valve while it is open will cause a greater quantity of gas to enter the volume to be compressed in the chamber. compression. The suction that occurs at a higher pressure Ρ2 + Δρ, where Δρ is due to the effect of pulse loading, is illustrated as a dashed line in Figure 1. Since the volume V2 'corresponding to the intersection of the dashed line with the which represents the expansion phase 1 is lower than V2, the volumetric efficiency increases, because the numerator of the ratio that defines it V3-V2 '> V3-V2 increases.

In fact Δρ does not represent a constant deviation of the pressure variation over time, between a maximum positive value and a maximum negative value. A controller could determine the opening moment of valve 20 in order to obtain a maximum pressure Δρ (added or subtracted) at the moment the valve opens or obtain a pressure higher than the suction pressure during (or at the end of) the suction phase .

Figure 3 is a schematic diagram of an interface 100 (i.e. an apparatus) between a reciprocating compressor 10 and a pulsation damper 60, which provides gas volume protection for an oil and natural gas plant, according to an exemplary embodiment. The large volume of gas within the pulsation damper 60 prevents or substantially dampens the pressure pulsations that occur in the gas outside the reciprocating compressor 10 due to the flow variation within the reciprocating compressor 10 itself (and i.e. due to the effect of pulse loading). The interface 100 includes a gas circulation device and a controller 110. The gas circulation device provides a path through which the gas (to be compressed or freshly compressed) circulates between the reciprocating compressor 10 and the pulsation damper 50. The device for the circulation of the gas is configured in such a way as to have a resonance frequency substantially equal to the frequency of the compression cycles running inside the reciprocating compressor. The gas circulation device comprises a tube 130 and an in-line resonator 140 with a larger surface area than that of the tube. The exact position of the inline resonator 140 along the tube 130 does not affect the acoustic characteristics of the gas circulation device. The controller 110 commands an actuator (not shown) which activates the valve 120. This means that the controller 110 adjusts the timing of the activation of the valve 120 in relation to the phase of the pressure pulsations (due to the effect of the pulse loading). to the valve, in order to use pressure pulsations to increase the volumetric efficiency of the compressor. If the valve 120 is the suction valve, the controller 110 adjusts the timing of the activation of the valve 120 so as to obtain a value of the maximum pressure Δp added to the suction pressure while the valve 120 is open (i.e. during the suction phase of the compression cycle).

In another exemplary embodiment illustrated in Figure 4, the gas circulation device of an interface 101 includes a lateral resonator 150 in addition to the inline resonator 140. Optionally, the lateral resonator 150 can be connected to the inline resonator 140 by means of a valve 160. The valve of the resonator 160 can be used to connect or disconnect the lateral resonator 150 to / from the tube 130, depending on the composition of the gas (composition affecting the speed of sound in the gas and therefore the resonant frequency of the gas circulation device). The controller 110 can manage the valve of the resonator 160.

In another exemplary embodiment illustrated in Figure 5, the gas circulation device of an interface 102 includes a side tube 170 instead of the inline resonator 140. Optionally, the side tube 170 can be connected to the tube 130 by means of a resonator valve 180. Resonator valve 180 can be used to connect or disconnect side pipe 170 to / from pipe 130, for example, depending on the composition of the gas (composition affecting the speed of sound in the gas and hence the frequency of the gas circulation device). The controller 110 can manage the valve of the resonator 180.

Alternatively in another exemplary embodiment illustrated in Figure 6, the device for circulating the gas of an interface 103 includes a lateral resonator 200 connected to the tube 130. Optionally, the lateral resonator 200 can be connected to the tube 130 by means of the valve resonator 210. The valve of the resonator 210 can be used to connect or disconnect the lateral resonator 200 to / from the tube 130, for example, depending on the composition of the gas (composition affecting the speed of sound in the gas and therefore the frequency of resonance of the gas circulation device). The controller 110 can manage the valve of the resonator 210.

In another embodiment illustrated in Figure 7, the interface gas circulation device 104 comprises an additional lateral resonator 220 connected to the lateral resonator 200. Optionally, the lateral resonator 200 and / or the additional lateral resonator 220 may be connected to tube 130 and side resonator 200, through resonator valves 210 and 230 respectively. Resonator valves 210 and 230 can be used to connect or disconnect side resonator 200 and additional side resonator 220, respectively, depending on the gas composition (composition that affects the speed of sound in the gas and therefore the resonant frequency of the gas circulation device). The controller 110 can manage the valve of the resonator 210 and / or 230.

In another embodiment illustrated in Figure 8, the gas circulation device of the interface 105 has a connection between the lateral resonator 200 and the pulsation damper via a secondary piping 240. The valve of the resonator 250 located on the pipeline 240 is activated or deactivated according to the composition of the gas.

In several embodiments illustrated in Figures 3 to 8 and in other equivalent embodiments, a method 300 is used to exploit the pulsations inherently generated outside, but due to the operation of the reciprocating compressor, to increase the volumetric efficiency of the compressor. As shown in Figure 9, Method 300 requires a gas circulation device between a reciprocating compressor valve and a pulsation damper that protects the reciprocating compressor itself from the oil and gas system, with the device for the circulation of the gas configured in such a way as to have a resonance frequency substantially equal to the frequency of the compression cycles running inside the reciprocating compressor, in S310. Method 300 also provides for control of the timing of valve activation to utilize the pressure pulsations that occur inherently within the gas circulation device due to the effect of pulse loading, in order to improve the volumetric efficiency of the reciprocating compressor, in S320.

In one embodiment, the S310 condition of method 300 may comprise adding a side resonator or side tube to a pipeline connecting the valve to the pulsation damper. In one embodiment, the S310 condition of method 300 may comprise turning on or off of one or more resonator valves that connect the acoustic resonators to the tubing which, in turn, connects the valve to the pulsation damper.

An existing reciprocating compressor installation can be upgraded to be able to use inherently generated pulsations during reciprocating compressor operation to increase efficiency. Figure 10 is a flowchart of a method 400 for innovating the installation of a reciprocating compressor, according to an exemplary embodiment. Method 400 involves modifying the gas circulation device that connects an outlet or inlet of the reciprocating compressor to the pulsation damper by adding at least one acoustic resonator to a tube of the gas circulation device to causing it to have a resonant frequency substantially identical to the frequency of the compression cycles in progress within the reciprocating compressor, in S410. Method 400 also involves connecting a valve between the reciprocating compressor and the gas circulation device to a controller configured to manage the timing of valve activation in order to use the pressure pulsations that occur in the device for gas circulation due to the pulse loading effect of the reciprocating compressor, in order to increase the volumetric efficiency of the reciprocating compressor itself.

In one embodiment of the method 400 the acoustic resonator may comprise an in-line acoustic resonator, a lateral acoustic resonator or a side tube. In another embodiment the method 400 may further comprise connecting at least one acoustic resonator to the apparatus through the valve of the resonator.

The disclosed exemplary embodiments provide apparatus (devices) and methods for the constructive use of pressure pulsations (i.e. the effect of pulse loading) that occur around reciprocating compressors due to flow variation, to increase the volumetric efficiency of the compressor. It is understood that the present description is not intended to limit the invention. Conversely, exemplary embodiments include alternatives, modifications and equivalent solutions within the spirit and scope of the invention, as defined by the appended claims. Furthermore, numerous specific details are set forth in the detailed description of the exemplary embodiments, in order to allow a thorough understanding of the claimed invention. However, anyone skilled in the art understands that various embodiments can be implemented without such details.

Although the features and elements of the present exemplary embodiments are described in the embodiments in particular combinations, each feature or each element can be used individually without the other features and elements of the embodiments or in various combinations with or without other features. and elements disclosed in this document.

The present written description uses examples relating to the disclosed subject matter to enable any one skilled in the art to implement the invention, including making and using any device or system as well as carrying out any including methods. The patentable scope of the subject of this document is defined by the claims and may include other examples known to those skilled in the art. These other examples are within the scope of the claims.

Claims (10)

CLAIMS / CLAIMS 1. Apparatus, including: a gas circulation device, which provides a path through which the gas to be compressed circulates between a reciprocating compressor, and a pulsation damper, which protects the reciprocating compressor itself from an installation, with the gas circulation device configured to have a resonant frequency substantially equal to the frequency of the compression cycles within the reciprocating compressor, e a controller configured to manage the timing of the activation of the valve located between the reciprocating compressor and the gas circulation device, in order to constructively use the pressure pulsations that occur in the gas circulation device, to increase the volumetric efficiency of the reciprocating compressor. The apparatus of claim 1, wherein the gas circulating device comprises a tube and an inline resonator with a larger surface area than the tube and with the tube and inline resonator arranged between the reciprocating compressor and I pulsation damper. 3. The apparatus of claim 2, wherein the gas circulation device further comprises a lateral resonator, located alongside the inline resonator to which the lateral resonator is connected via a resonator valve, which is opened and closed connecting or disconnecting the lateral resonator to the in-line resonator, depending on the composition of the gas. 4. The apparatus of claim 1, wherein the gas circulating device comprises a tube arranged between the reciprocating compressor and the pulsation damper and a side tube arranged alongside the pipeline to which the side tube is connected via a valve of the resonator, which is opened and closed by connecting or disconnecting the side pipe to the pipe, depending on the composition of the gas. The apparatus of claim 4, wherein the gas circulation device further comprises an additional lateral resonator connected to the lateral resonator. The apparatus of claim 5, wherein at least one of the side resonators and the additional side resonator are connected via a valve, respectively, to the side pipe or the side resonator, with the valve being opened and closed by connecting or disconnecting the side pipe or the lateral resonator, depending on the composition of the gas. 7. The apparatus of claim 1, wherein the gas circulating device comprises a tube arranged between the reciprocating compressor and the pulsation damper and a side tube arranged alongside the pipeline to which the side tube is connected via a valve of the resonator, which is opened and closed by connecting or disconnecting the side pipe to the pipe, depending on the composition of the gas. The apparatus of claim 1, wherein the valve is the suction valve and the controller adjusts the timing of the valve activation to obtain a maximum pulsing pressure added to the suction pressure while the valve is open. 9. Method for using the pulse loading effect to increase the volumetric efficiency of a reciprocating compressor, where the method includes: the need for a gas circulation device between a reciprocating compressor valve and a pulsation damper, which protects the reciprocating compressor itself from an installation, with the gas circulation device configured to have a frequency of resonance substantially equal to the frequency of the compression cycles running inside the reciprocating compressor; And the control of the valve activation timing, to constructively use the pressure pulsations that occur inherently inside the gas circulation device, in order to improve the volumetric efficiency of the reciprocating compressor. 10. Method for adapting the installation of a reciprocating compressor in which the outlet or inlet of the compressor is protected by a pulsation damper with respect to the rest of the installation, which is adapted in order to exploit the effect of loading at pulses of the reciprocating compressor itself, in order to increase its volumetric efficiency; the method provides: modification of the gas circulation device that connects an outlet or inlet of the reciprocating compressor to the pulsation damper, by adding at least one acoustic resonator to a tube of the gas circulation device, to make it has a resonant frequency substantially identical to the frequency of the compression cycles in progress within the reciprocating compressor, e the connection of a valve between the reciprocating compressor and the gas circulation device to a configured controller, to adjust the timing of the valve activation in order to constructively utilize the pressure pulsations that occur in the gas circulation device , to increase the volumetric efficiency of the reciprocating compressor. CLAIMS / CLAIMS 1. An apparatus, comprising: a gas circulation device that provides a path through which a gas to be compressed circulates between a reciprocating compressor and a volume bottle buffering the reciprocating compressor from an installation, the gas circulation device being configured to have a resonance frequency substantially equal to a frequency of performing compression cycles in the reciprocating compressor; and a controller configured to control timing of switching a valve located between the reciprocating compressor and the gas circulation device in order to use constructively pressure pulsations occurring in the gas circulation device, to enhance a volumetric efficiency of the reciprocating compressor. 2. The apparatus of claim 1, wherein the gas circulation device comprises a pipe and an in-line resonator having an area larger than the pipe area, the pipe and the in-line resonator being arranged in-between the reciprocating compressor and the volume bottle. 3. The apparatus of claim 2, wherein the gas circulation device further comprises a side-branch resonator, arranged lateral to the in-line resonator wherein the side-branch resonator is connected to the in-line resonator via a resonator valve, the resonator valve being switched between being opened and being closed thereby connecting or disconnecting the side-branch resonator to the in-line resonator depending on a composition of the gas. 4. The apparatus of claim 1, wherein the gas circulation device comprises a pipe arranged between the reciprocating compressor and the volume bottle, and a side-branch pipe arranged lateral to the pipe, wherein the side-branch pipe is connected to the pipe via a resonator valve, the resonator valve being switched between being opened and being closed thereby connecting or disconnecting the side-branch pipe to the pipe depending on a composition of the gas. 5. The apparatus of claim 4, wherein the gas circulation device further comprises an additional side-branch resonator connected to the side resonator. 6. The apparatus of claim 5, wherein at least one of the side-branch resonator and the additional side-branch resonator is connected via a valve to the pipe or to the side-branch resonator, respectively, the valve being switched between being opened and being closed thereby connecting or disconnecting the side-branch pipe or the additional side-branch resonator thereof depending on a composition of the gas. 7. The apparatus of claim 1, wherein the gas circulation device comprises a pipe arranged between the reciprocating compressor and the volume bottle, and a side-branch pipe arranged lateral to the pipe, the side-branch pipe being connected to the pipe via a resonator valve, the resonator valve being switched between being opened and being closed thereby connecting or disconnecting the side-branch pipe to the pipe depending on a composition of the gas. 8. The apparatus of claim 1, wherein the valve is a suction valve and the controller controls the timing of actuating the valve to have a maximum pulsation pressure added to a suction pressure while the valve is open. 9. A method of using a pulse charging effect to enhance a volumetric efficiency of a reciprocating compressor, the method comprising: providing a gas circulation device between a valve of the reciprocating compressor and a volume bottle buffering the reciprocating compressor from an instalation, the gas circulation device being configured to have a resonance frequency substantially equal to a frequency of performing compression cycles in the reciprocating compressor; and controlling timing of actuating the valve to use constructively pressure pulses inherently occurring in the gas circulation device, to enhance the volumetric efficiency of the reciprocating compressor. 10. A method for retrofitting a reciprocating compressor installation in which an output or an input of a reciprocating compressor is buffered by a volume bottle from the rest of the installation, the installation being retrofitted to use a pulse charging effect of the reciprocating compressor to enhance a volumetric efficiency thereof, comprising: modifying a gas circulation device connecting an output or an input of the reciprocating compressor to the volume bottle, by adding at least one acoustic resonator to a pipe of the gas circulation device, to make the gas circulation device to have a resonance frequency substantially equal to a frequency of performing compression cycles in the reciprocating compressor; and connecting a valve between the reciprocating compressor and the gas circulation device, to a controller configured to control timing of actuating the valve in order to use constructively pressure pulsations occurring in the gas circulation device, to enhance a volumetric efficiency of the reciprocating compressor.