阅读说明：本技术 用于操作活塞式压缩机的方法及活塞式压缩机 (Method for operating a piston compressor and piston compressor ) 是由 萨沙·多尔纳 克里斯托弗·纳格尔 约翰尼斯·弗里策 克劳斯·费舍尔 于 2018-11-06 设计创作，主要内容包括：本发明涉及用于操作在气缸(110)中具有往复活塞(111)的活塞式压缩机(100)的方法,其中在气缸(110)中在待压缩和输送的介质(b)的侧设置入口阀(112)和出口阀(113),其中通过在第一容积(141)中使用液压介质(a),往复活塞(111)借助于具有液压活塞(120)的液压驱动器(120,121)来回移动,由此,往复活塞(111)被负载在液压驱动器(120,121)的侧上,其中如果需要,则将液压介质(a)以一定方式馈送到第一容积(141)中和/或从第一容积(141)排出,该方式依赖于液压活塞(120)的位置和/或被设置用于使该液压活塞(120)相对于往复活塞(120)的位置(x)移动的轴(121)的旋转角<Image he="76" wi="121" file="DDA0002501920830000011.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>和/或该第一容积(141)中的压力(p),并且本发明涉及该类型的活塞式压缩机(100)。(The invention relates to a method for operating a piston compressor (100) having a reciprocating piston (111) in a cylinder (110), wherein an inlet valve (112) and an outlet valve (113) are provided in the cylinder (110) on the side of a medium (b) to be compressed and conveyed, wherein by using a hydraulic medium (a) in a first volume (141), the reciprocating piston (111) is moved back and forth by means of a hydraulic drive (120, 121) having a hydraulic piston (120), whereby the reciprocating piston (111) is loaded on the side of the hydraulic drive (120, 121), wherein if required, the hydraulic medium (a) is fed into the first volume (141) and/or discharged from the first volume (141) in a manner that depends on the position and/or is provided of the hydraulic piston (120)A rotation angle of a shaft (121) for moving the hydraulic piston (120) relative to the position (x) of the reciprocating piston (120) And/or the pressure (p) in the first volume (141), and to a piston compressor (100) of this type.)

1. A method for operating a piston compressor (100) having a reciprocating piston (111) in a cylinder (110), wherein an inlet valve (112) and an outlet valve (113) are provided in the cylinder (110) on the side of a medium (b) to be compressed and conveyed,

wherein the reciprocating piston (111) is moved back and forth by means of a hydraulic drive (120, 121) having a hydraulic piston (120) by using a hydraulic medium (a) in a first volume (141), whereby the reciprocating piston (111) is loaded on the side of the hydraulic drive (120, 121),

characterized in that, if required, hydraulic medium (a) is fed into and/or drained from the first volume (141) in a manner that depends on the position of the hydraulic piston (120) and/or the angle of rotation of a shaft (121) arranged for moving the hydraulic piston (120) relative to the position (x) of the reciprocating piston (120)And/or the firstPressure (p) in the volume (141).

2. A method according to claim 1, wherein the movement of the reciprocating piston (111) on the side of the hydraulic drive (120, 121) is limited as required, with a hydraulic damping unit (140) using the hydraulic medium (a) and forming a second volume (142) at least partly delimited by the reciprocating piston (111).

3. A method according to claim 2, wherein the second volume (142) is connected to the first volume (141) in order to reduce the amount of medium (b) to be delivered by the piston compressor (100), wherein excess hydraulic medium (a) is drained from the first volume (141) into a reservoir (130) and/or

Wherein the first volume (141) is connected to the reservoir (130) for the hydraulic medium in order to increase the amount of medium (b) to be delivered by the piston compressor (100), wherein the required hydraulic medium is supplied from the reservoir (130).

4. Method according to one of the preceding claims, wherein a multistage piston compressor with at least two reciprocating pistons and corresponding cylinders is used as the piston compressor (100).

5. Method according to one of the preceding claims, wherein an ionic fluid is used as operating fluid.

6. A piston compressor (100) having a reciprocating piston (111) in a cylinder (110), wherein an inlet valve (112) and an outlet valve (113) are provided in the cylinder (110) on the side of a medium (b) to be compressed and conveyed,

the piston compressor has a hydraulic drive (120, 121) with a hydraulic piston (120), by means of which the reciprocating piston (111) is moved back and forth by using a hydraulic medium (a) in a first volume (141), whereby the reciprocating piston (111) can be loaded on the side of the hydraulic drive (120, 121),

characterized by at least one measuring device (160, 161, 162) by means of which the position of the hydraulic piston (111) and/or the angle of rotation of a shaft (121) provided for moving the hydraulic piston (120) can be determinedAnd the position (x) of the reciprocating piston and/or the pressure (p) in the first volume (141),

wherein the piston compressor (100) is configured for feeding hydraulic medium (a) into and/or discharging hydraulic medium (a) from the first volume (141) when required in a manner dependent on the position of the hydraulic piston (111) and/or the rotational angle of the shaft (121) provided for moving the hydraulic piston (120) relative to the position (x) of the reciprocating piston (111)And/or the pressure (p) in the first volume (141).

7. The piston compressor (100) of claim 6, further having a hydraulic damping unit (140) by means of which the movement of the reciprocating piston (111) on the side of the hydraulic drive (120, 121) can be limited as required using the hydraulic medium (a) and forming a second volume (142) at least partly delimited by the reciprocating piston (111).

8. The piston compressor (100) of claim 7, having a first valve (150) by which the second volume (142) is connectable to the first volume (141); and having a second valve (155) by means of which hydraulic medium (a) can be discharged from the first volume (141) into a reservoir (130) for the hydraulic medium, and/or

Having a third valve (153) by which the first volume (141) can be connected to the reservoir (130) for the hydraulic medium.

9. A piston compressor (100) according to one of the claims 6 to 8, designed as a multistage piston compressor with at least two reciprocating pistons and corresponding cylinders.

10. The piston compressor (100) according to one of claims 6 to 8, wherein an ionic fluid is provided as operating fluid.

Background

The present invention relates to a method for operating a piston compressor and to a piston compressor.

Compressors are used in particular for compressing gaseous media. The efficiency of a conventional piston compressor is very strongly influenced by the presence of a residual volume or dead space in the top dead center. The gas or medium in this region leads to a possible re-expansion in the suction cycle and a reduction in the inflowing delivery volume. This area is unavoidable in order to compensate for manufacturing tolerances and thermal expansion of the components and subsequently to avoid mechanical contact of the reciprocating piston in the compressor with the cylinder head. The passages for the suction and pressure valves (i.e., the inlet and outlet valves) increase this negative effect.

Reducing this dead space reduces re-expansion of the remaining medium and thus increases the delivery volume or efficiency of the compression process. So-called ionic compressors, in particular piston compressors, on the one hand operate hydraulically and on the other hand compress a two-phase mixture consisting of a medium or gas and a liquid lubricant (i.e. an ionic fluid), which cannot evaporate and can therefore be completely separated again by a simple sedimentation process. An advantage of such an ion compressor is that by using a liquid phase in the compression chamber, the dead space in the cylinder can be minimized, thereby optimizing the efficiency of the compression process.

Disadvantageously, additional component loading, and thus increased acoustic emissions, results from the liquid-like behavior of the impact. Furthermore, in the compression concept of hydraulic drive, due to internal leakage in the hydraulic circuit, the amount of oil filling must be controlled and compensated for, if necessary. This major problem is caused by mechanical contact in the reversal point of the reciprocating piston and the consequent increased component loading and noise emission which are considered problematic-especially in the case of installations near populated areas-and require additional acoustic insulation.

The concept of damping is known, for example, from the field of automotive components, in particular in the case of shock absorbers. In this case, the kinetic energy is dissipated in the form of vibrations. This enables a reduction in component loads and acoustic emissions in addition to reducing undesirable fluctuations or oscillations of the vehicle.

Against this background, the object set forth is to provide a possibility of improving the operation of a piston compressor, in particular with respect to component loading and acoustic emissions.

Disclosure of Invention

The object of the invention is achieved by a method for operating a piston compressor and a compressor having the features of the independent claims. Preferred embodiments are subject matter of the dependent claims and the following description.

Advantages of the invention

The invention relates to a method for operating a piston compressor with a reciprocating piston in a cylinder, wherein inlet and outlet valves (or suction and pressure valves) are provided in the cylinder on the side of the medium to be compressed and conveyed, i.e. in the cylinder head. With a hydraulic drive comprising a hydraulic piston, the shuttle piston is moved back and forth (or up and down) by using a hydraulic medium in a first volume, whereby the shuttle piston is loaded on the side of the hydraulic drive.

The hydraulic piston oscillates in the cylinder between two points of reversal, the so-called Bottom Dead Center (BDC) and the so-called Top Dead Center (TDC). When moving in the top dead center direction, the medium present in the cylinder or the cylinder head is compressed and then discharged through the outlet valve; when moving in the direction of bottom dead center, the medium is drawn in through the inlet valve.

In principle, in this case, the reciprocating piston will move synchronously with the hydraulic piston. However, due to leakage effects in the circuit of the hydraulic medium (i.e. the mentioned first volume), it may happen that the reciprocating piston no longer moves synchronously with the hydraulic piston. This means that, for example, at bottom dead centre, the reciprocating piston hits the cylinder bottom and the hydraulic piston moves further downwards. This creates a negative pressure in the first volume or hydraulic circuit. The reciprocating piston may also hit the cylinder head while the hydraulic piston is moving further upwards. This creates an overpressure in the first volume or hydraulic circuit.

It is now provided that, when required, hydraulic medium is fed into and/or discharged from the first volume in a manner which is dependent on the position of the hydraulic piston and/or the angle of rotation of the shaft provided for moving the hydraulic piston relative to the position of the reciprocating piston and/or the pressure in the first volume. In this process, one or more suitable measuring devices may be used to determine the respective variable.

The position of the hydraulic piston and the angle of rotation of the shaft provided for moving the hydraulic piston are linked to each other and indicate the current position of the hydraulic drive. The position of the reciprocating piston and the pressure in the first volume are also linked to each other, because the pressure rises or falls when the reciprocating piston hits the cylinder. If these variables are now determined, they can be set in relation to one another so that it can be detected whether a stroke of the reciprocating piston takes place or, if applicable, whether such a stroke of the reciprocating piston is imminent. Thus, the hydraulic medium can then be fed into or discharged from the first volume.

Thus, the negative pressure occurring in the first volume or hydraulic circuit can be counteracted by supplying hydraulic medium when or before the hydraulic piston hits the bottom of the cylinder at bottom dead center. Thus, the impact can be reduced or even prevented, which leads to a reduction of acoustic emissions and component loads.

Thus, the impact on the top dead center can be reduced or even prevented by discharging the hydraulic medium, which likewise leads to a reduction of the acoustic emission and the component load. For this purpose, suitable valves can be provided, which are actuated correspondingly, i.e. opened or closed. For a more detailed description of such valves, reference is now made to the description of the piston compressor or to the description of the figures.

Preferably, in case the hydraulic damping unit uses a hydraulic medium and forms a second volume at least partly delimited by the reciprocating piston, the movement of the reciprocating piston on the hydraulic drive side is limited if necessary. Such a damping unit may be used not only to further resist the movement of the reciprocating piston, but also to adjust the compression ratio.

For this purpose, the second volume is preferably connected to the first volume in order to reduce the amount of medium to be conveyed through the piston compressor. This is accompanied by an increase in dead space in the cylinder head. For this purpose, excess hydraulic medium (thus, in order to reduce the hydraulic medium in the second volume) is discharged from the first volume into the reservoir. It is also preferred that the first volume is connected to a reservoir for hydraulic medium in order to increase the amount of medium delivered by the piston compressor. This is accompanied by a reduction in dead space in the cylinder head. In this case, the required hydraulic medium is supplied from the reservoir (thus, in order to increase the amount of hydraulic medium in the second volume or to fill the second volume).

Thus, the second volume can be filled with more or less hydraulic medium when needed. Since the movement of the reciprocating piston in the direction of the bottom dead center (and thus in the direction of the hydraulic actuator) can be limited by the hydraulic medium in the second volume, the volume available for compression at the cylinder head or top dead center can be changed. Therefore, the compression ratio can be changed.

Advantageously, a multistage piston compressor with at least two reciprocating pistons and corresponding cylinders is used as piston compressor. However, the movement of the reciprocating pistons in the respective cylinders can still be performed with one hydraulic drive and then with a corresponding number of such first volumes. Of course, a corresponding number of such damping units may then also be provided. The individual cylinders can then be arranged, for example, in series or star, as the case may be. The compression is then performed in such a way that the medium discharged from one cylinder is supplied to another cylinder and further compressed there.

It is particularly preferred that an ionic fluid is used as the operating fluid. In this regard, the compressor is also referred to as a so-called ion compressor. As described above, such ion compressors provide advantages such as dead volume reduction. By the supply or discharge of the hydraulic medium proposed here, the remaining disadvantages of acoustic emissions or component wear can now also be reduced.

The invention also relates to a piston compressor with a reciprocating piston in a cylinder, wherein an inlet valve and an outlet valve are provided in the cylinder on the side of the medium to be compressed and conveyed. Furthermore, the piston compressor has a hydraulic drive with a hydraulic piston, by means of which the reciprocating piston can be moved back and forth by using a hydraulic medium in the first volume, whereby the reciprocating piston can be loaded on the hydraulic drive side. In this case, at least one measuring device is provided, by means of which the position of the hydraulic piston and/or the angle of rotation of the shaft provided for moving the hydraulic piston, as well as the position of the reciprocating piston and/or the pressure in the first volume can be determined. The piston compressor is now configured to feed and/or discharge hydraulic medium to/from the first volume when required in a manner which depends on the position of the hydraulic piston and/or the angle of rotation of the shaft provided for moving the hydraulic piston relative to the position of the reciprocating piston and/or the pressure in the first volume.

Preferably, the piston compressor further comprises a hydraulic damping unit by means of which the movement of the reciprocating piston on the hydraulic drive side can be limited if required, using a hydraulic medium and forming a second volume which is at least partly delimited by the reciprocating piston. In this case, a first valve is advantageously provided, by means of which the second volume can be connected to the first volume, and a second valve, by means of which hydraulic medium can be discharged from the first volume into a reservoir for hydraulic medium. Thus, the amount of medium conveyed by the piston compressor can be reduced. It is furthermore preferred that a third valve is provided, by means of which the first volume can be connected to a reservoir for hydraulic medium. Thus, the hydraulic medium may be supplied to the first volume. The third valve may preferably also be designed in such a way that hydraulic medium can be automatically supplied from the reservoir to the first volume if there is a lower pressure on the first volume side than on the reservoir side. For this purpose, the third valve can be designed, for example, as a check valve.

The piston compressor is advantageously designed as a multistage piston compressor with at least two reciprocating pistons and corresponding cylinders. Expediently, an ionic fluid is provided as operating fluid in the piston compressor.

With regard to the detailed description and further preferred embodiments and advantages of the piston compressor according to the invention, reference is made to the above description, in order to avoid repetitions, which description applies here accordingly with regard to the method according to the invention, which method is described with reference to the piston compressor.

The invention is schematically represented in the drawings using exemplary embodiments and is described below with reference to the drawings.

Drawings

Fig. 1 schematically shows a piston compressor according to the invention in a preferred embodiment, which is adapted to perform the method according to the invention.

Detailed Description

Fig. 1 schematically shows in a preferred embodiment a piston compressor 100 according to the invention, which is adapted to perform the method according to the invention.

The piston compressor 100 (also referred to as a reciprocating piston compressor in the illustrated form) includes a cylinder 110 in which a reciprocating piston 111 can move back and forth or up and down. In principle, such a piston compressor may be multistage, i.e. there may be several cylinders 110 shown with reciprocating pistons 111. The following description in connection with the cylinder with reciprocating piston is thus also applicable to the further cylinder with reciprocating piston.

The piston compressor 100 is driven by a hydraulic drive, which here comprises a hydraulic piston 120. The hydraulic piston 120 is driven by a wheel (hydraulic crankshaft drive) with a shaft 121 with suitable connecting rods. Rotation of the shaft 121 as indicated by the arrow causes an up and down movement of the reciprocating piston 110 by using a hydraulic medium a (hydraulic oil) in the first volume 141, also as indicated by the arrow. The reciprocating piston 111 oscillates between two points of reversal, referred to as Bottom Dead Center (BDC) and Top Dead Center (TDC), in the cylinder 110.

The frequency of shaft rotation and reciprocating piston up and down movement may be, for example, between 0.5Hz and 12Hz (but is typically held constant); the stroke of the reciprocating piston may be, for example, between 30mm and 100 mm. The stroke or stroke volume of the hydraulic piston is also generally constant.

The hydraulic medium a is thus conveyed here to the bottom side of the reciprocating piston 111. Thus, the reciprocating piston 111 moves upward and compresses a so-called two-phase mixture in a cylinder 114 (i.e., the upper region of the cylinder). The two-phase mixture here comprises, on the one hand, the medium b to be compressed and transported and, on the other hand, the ionic operating fluid. If the pressure in the cylinder 110 exceeds the back pressure at the pressure or outlet valve 113, the latter opens and delivers the medium b approximately isobarically into the pressure region until top dead center is reached.

As soon as the hydraulic piston 120 moves downwards, the back pressure in the cylinder 110 undershoots and the outlet valve 113 closes. The reciprocating piston 111 moving downward reduces the pressure in the cylinder 110 until the pressure applied at the suction valve or inlet valve 112 falls below the level in the suction area.

The less residual volume or dead space present, the earlier inlet valve 112 can be opened, and the amount drawn increases in proportion thereto. Due to this system, the position of the shuttle piston 111 may be offset from the stroke position of the hydraulic piston 120. Compression in the hydraulic drive loaded with leakage then causes hydraulic medium a to be conveyed through the hydraulic piston 120, first into the reservoir 130 (or tank).

From there, the hydraulic medium can be fed back to the hydraulic circuit or first volume 141 via the pump 131 and the heat exchanger 132 and finally via the check valve 153 in order to compensate for the positional deviation between the hydraulic piston 120 and the reciprocating piston 111.

It is now possible within the scope of the invention to measure the position of the object e.g. via the measuring means 161 (e.g.,displacement measurement system) and the measuring device 160 (e.g., rotation angle sensor) to calculate and correct the required amount. For example, although the position x of the reciprocating piston 111 may be determined by the measuring device 161, the angle of rotation of the shaft 121 may be determined by the measuring device 160Furthermore, the pressure p in the first volume 141 may also be detected, for example, by a suitable measuring device 162.

The impact of the reciprocating piston 111 against the cylinder head is now detected by an excessive pressure increase at the end of the actual isobar extension phase, whereby excess hydraulic medium is conveyed back into the reservoir 130 via the pressure-limiting valve 154.

The mechanical contact of the reciprocating piston 111 with the piston or cylinder bottom is detected by the pressure drop during the inflow phase. In this case, a deficient amount of hydraulic medium is sucked or supplied via a check valve 153 (also referred to as a third valve in the scope of the present invention) in order to move the reciprocating piston 111 into the normal range.

Since, for example, a pressure measurement is now made in the first volume in a manner dependent on the angle of rotation of the shaft 121, it is possible to detect when a striking of the reciprocating piston 111 against the cylinder head or the cylinder bottom occurs or is about to occur, and to drain or supply hydraulic medium, for example by suitably actuating the valves 153 or 154.

Furthermore, a damping unit 140 is provided, by means of which an adaptive damping system can be achieved, irrespective of the frequency, the pressure ratio in the piston compressor and the leakage in the hydraulic region. The damping unit 140 may serve to block the downward movement of the reciprocating piston 111, thus reducing sound emission and mechanical load during the movement in the bottom dead center direction.

This can be compensated for if a leak in the oil circuit, i.e. in the first volume 141 here, is detected via a rotation angle resolved pressure measurement in the hydraulic system, i.e. in the first volume 141 here. Furthermore, it is possible to adjust the top dead center and the bottom dead center by means of an adaptive damping system, thus adjusting the compression ratio or the delivery quantity of the medium. For this purpose, depending on the demand or need for the required amount, additional hydraulic medium is supplied or the excess is drained off or pushed back into the reservoir.

If the delivery volume is to be increased or the existing dead space is to be reduced, the first valve 150 is closed. Accordingly, even if the hydraulic piston 120 moves downward, the reciprocating piston 111 is prevented from moving in the direction of the bottom dead center or the direction of the hydraulic actuator. Thus, due to the resulting negative pressure, a desired amount of hydraulic medium is drawn into the circuit or first volume 141 via the check valve 153. When the hydraulic piston 120 is moved upwards again, the system is closed and the shuttle piston 111 is raised by a defined volume (by an additional delivered amount of hydraulic medium), thus reducing the dead space and increasing the delivered amount of medium to be compressed.

If the amount of hydraulic medium increases too much and the shuttle piston 111 is in danger of colliding with the cylinder head, the third valve 155 may be opened and the filling amount may be reduced.

If the amount of delivery is to be reduced or the existing dead space is to be increased, the first valve 150 is opened so as not to affect the downward movement of the shuttle piston 111. At the same time, the second valve 155 is opened in order to reduce or discharge a defined amount of hydraulic medium, which is formed by the upward movement of the hydraulic piston 120. When the desired position of the shuttle piston is reached, the first valve 150 may be closed again.

If this is done before the hydraulic piston 120 reaches bottom dead center, the hydraulic piston is replenished with the necessary amount of hydraulic medium via check valve 153.

These adjustments can be made closer to the desired operating point by repeating the iterations in the control loop. If it is necessary to vary the intermediate circuit pressure of the various stages (in the case of a multistage piston compressor, therefore), this can be done in the same way as just described. Only pressure is used as a control variable and is consistent with other stages in the circuit.

If the operating point has been set, the pressure change in the system is proportional to the position of the reciprocating piston 111. Angle of rotation of the position x of the reciprocating piston 111 with the shaft 121 due to leakageThe associated positional deviation may occur by damping the reciprocating piston 111 with the damping unit 140; the hydraulic medium is replenished via the check valve 153 and the incorrect position is compensated for.

Such an adaptive damping system makes it possible to optimize the hydraulically driven piston compressor with respect to the available stroke volume. So that the stroke of the piston can be varied and the delivery volume, pressure and efficiency optimized according to the requirements of the system.

The residual volume between the reciprocating piston and the cylinder head, the so-called dead space, expands during the downward movement of the reciprocating piston and, depending on the size, affects the opening time of the normal spring-driven suction valve. The larger the dead space, the later the suction valve is opened, and the smaller the delivery volume that can be drawn in.

This directly affects the efficiency of the individual compressor stages. Thus, adaptation of the intermediate circuit pressure, which may be necessary within a particular operating range, is performed in coordination with the remaining stages. With the proposed method or piston compressor, therefore, a large variability with respect to the required delivery volume and the applied pressure can be achieved in the intermediate circuit.

The possibility of blocking the reciprocating piston and optimizing the stroke makes it possible to permanently reduce the mechanical load, which on the one hand results in an increase in the possible service life of the compressor components and on the other hand allows the use of lower quality materials, thus providing more room for cost optimization in terms of raw materials and production costs.

The mentioned effects are accompanied by a reduction of vibration and noise emissions, so that savings can also be achieved with respect to previously necessary damping measures, thus making it easier to operate, for example, a tank control system in a residential area, in which, for example, hydrogen is compressed with such a piston compressor.

As a result of said construction, such piston compressors are very variable, simplifying the application of modular systems even with respect to different operating media, limits and requirements, thus allowing simpler mass production despite different applications, thanks to the structural uniformity of the various components now possible.

The extension of the existing or already delivered piston compressor to the proposed piston compressor allows to optimize the operating parameters and to increase the efficiency. Furthermore, the existing service life can be extended and vibrations and acoustic emissions reduced.

Integration into existing systems (i.e. existing piston compressors or several of them) can be done during routine maintenance. For this purpose, a displacement measuring system and a rotation angle transmitter (in the sense of the mentioned measuring device) can additionally be attached, and the automation program of the system can be extended by necessary control routines.

Another embodiment consists in the possibility of implementing an expander system (in combination with controllable suction and pressure valves, for example based on piezoelectrics, for example used in automotive applications). Such expander systems use the work of expansion in the expansion of gases, for example in distribution systems requiring gases at lower pressure levels, and thus can be used for power generation based on energy recovery systems.