Oscillating piston compressor

Abstract

An oscillating piston compressor comprising a low-pressure inlet (4) for the fluid to be compressed, a high-pressure outlet (5) for the compressed fluid, and a medium-pressure inlet (6) for fluid at a medium-pressure level which lies between the pressure level of the low-pressure inlet (4) and the pressure level of the high-pressure inlet (5). The medium-pressure inlet (6) is fluidically connected to the working chamber (2) via a valve which is controlled by the rotational angle position of the eccentric shaft (8), the valve comprising a weighing element (3) which is received in a receptacle (71) and is equipped with a valve channel device which is fluidically connected to the medium-pressure inlet (6) and is opened or closed depending on the rotational angle position of the weighing element (3) with respect to the working chamber (2). The valve channel device comprises at least one valve channel (323), the valve channel (323) being designed to be pressure-optimized, in particular being dependent on the respectively desired mass flow level (medium-pressure level).

Description

[0001] vibrating piston compressor

[0002] The present invention relates to a vibrating piston compressor according to the preamble of claim 1.

[0003] A rotary piston compressor is a compressor in which a rotating piston moves. Therefore, rotary piston compressors are also called reciprocating or circulating compressors. The fluid to be compressed, for example, a refrigerant, is compressed in a closed working chamber, also called a cylinder, compression chamber, or cylinder chamber, in which an eccentrically mounted piston moves against the inner wall. The low-pressure and high-pressure sides are separated, for example, by a valve within the working chamber.

[0004] The oscillating piston is freely mounted on the eccentric shaft. Guided by the piston's web within the cradle element (or between the cradle element components), it performs a kind of orbiting motion within the cylinder. Instead of "rolling," the oscillating piston makes frictional contact / glides along the cylinder wall. The cradle element (or its components) performs an oscillating angular movement.

[0005] Furthermore, so-called medium-pressure systems are known for extending or optimizing compression, particularly the cold vapor compression cycle. Relatively early in the compression process, additional fluid to be compressed, especially refrigerant, is injected into the compressor's working chamber at a medium-pressure level (higher than suction / low pressure, lower than high pressure). This results in advantages such as higher efficiency and volumetric efficiency, lower final compression temperature, smoother operation, etc.

[0006] Such a oscillating piston compressor is known, for example, from DE102021132942 Al. This patent specifically demonstrates various possibilities for medium-pressure injection, in particular an axial groove or channel in the oscillating piston to control the injection timing via the piston position.

[0007] A oscillating piston compressor according to the preamble of claim 1 is known from US9261094B2.

[0008] A oscillating piston compressor of the aforementioned type therefore comprises an oscillating piston housed in a working chamber, which is driven by an eccentric, a low-pressure inlet for the fluid to be compressed opening into the working chamber, a high-pressure outlet for the compressed fluid opening into the working chamber, a medium-pressure inlet for fluid at a medium-pressure level which lies between the pressure level of the low-pressure inlet and the pressure level of the high-pressure inlet, wherein the medium-pressure inlet is in fluidic communication with the working chamber via a valve controlled by the angular position of the eccentric shaft, wherein the valve comprises a weighing element housed in a receptacle which is equipped with a valve channel device which is in fluidic communication with the medium-pressure inlet and can be opened or closed depending on the angular position of the weighing element relative to the working chamber.

[0009] Although a usable oscillating piston compressor with medium-pressure injection is already proposed here, there is still potential for improvement, especially with regard to the geometric design of the valve channel assembly.

[0010] According to the invention, this problem is solved by a oscillating piston compressor with the characterizing features of claim 1. By comprising at least one valve channel in the valve channel assembly, wherein the at least one valve channel is designed to be pressure-optimized, an improved, and in particular more efficient, oscillating piston compressor can be provided. The pressure optimization is intended to minimize flow resistance and also to avoid, or at least reduce, friction losses. The pressure optimization can be carried out, in particular, depending on the desired mass flow rate level at the medium pressure level.

[0011] In other words, the pressure-optimized design of the valve channel enables further system optimizations in rotary or oscillating piston compressors with medium-pressure injection, particularly in automotive applications. However, the inventive idea can also be applied to stationary rotary or oscillating piston compressors. In particular, the inventive idea can lead to efficiency improvements in medium-pressure injection.

[0012] Further advantageous embodiments of the proposed invention arise in particular from the features of the dependent claims. The subject matter or features of the various claims can, in principle, be combined with one another in any way. In an advantageous embodiment of the invention, the valve channel assembly may comprise several parallel valve channels, in particular with different lengths, widths, and / or depths. Advantageously, different opening times and / or different flow rates can be achieved by means of the parallel valve channels, in particular with different lengths. The size and shape of the channel cross-section influence the refrigerant flow rate (mass flow).

[0013] In a further advantageous embodiment of the invention, the at least one valve channel can be equipped with a downwardly tapered and / or particularly radially rounded mass flow outlet. This allows, in particular, a pressure-optimized mass flow outlet area to be provided.

[0014] In a further advantageous embodiment of the invention, the valve channel can be designed to be wide and / or shallow. A wide design advantageously results in a high mass flow rate. In a shallow design, the aspect ratio (cross-sectional area) of the valve channel is 2:1 (width / height). In a further preferred embodiment, the ratio can be 1:2 (width / height, narrow). Other ratios are conceivable. The width and height relative to the cross-sectional area of ​​the valve channel can influence the mass flow rate. The dimensions of the channel cross-section and the aspect ratio are structurally limited, in particular, by the dimensions of the weighing element.

[0015] In a further advantageous embodiment of the invention, the valve channel can be designed to be concave or conical. The concave design allows for improved flow characteristics. Advantageously, the concave channel contour results in improved flow characteristics.

[0016] In a further advantageous embodiment of the invention, the valve channel can be configured as either an open or closed channel. A closed channel configuration, or in other words, an internal channel geometry, allows for improved sealing between the weighing element and its receptacle in the cylinder housing. An open channel facilitates easier manufacturing. In a further advantageous embodiment of the invention, the valve channel can be configured to taper continuously towards the working chamber. This allows for optimized inflow characteristics and improved flow-related effects, such as regulation of the inflow behavior.

[0017] In a further advantageous embodiment of the invention, the at least one valve channel can be equipped with pressure build-up stages. This allows for improved flow characteristics, such as regulation of the inflow behavior.

[0018] The described geometries enable further system optimizations for rotary or oscillating piston compressors with medium-pressure injection, particularly in the automotive sector. However, the inventive idea can also be applied to stationary rotary or oscillating piston compressors.

[0019] It can be used in oscillating piston compressors. In particular, the inventive idea can lead to efficiency improvements in medium-pressure injection.

[0020] In a further advantageous embodiment of the invention, the weighing element can be composed of at least two components, preferably two components, with the valve channel assembly being arranged in one of the components. The weighing element is preferably designed in two parts. In this respect, the weighing element can have a component facing the low-pressure inlet channel and a component facing the high-pressure outlet channel. The receptacle for the piston rod segment is preferably provided between the two components. Preferably, the outlet-side component of the weighing element is provided with the valve channel in a circular or radially shaped outer contour.

[0021] In a further advantageous embodiment of the invention, the oscillating piston can be equipped with a piston rod segment, wherein the weighing element is provided with a receptacle for the slidably mounted piston rod element. A mechanical connection exists between the oscillating piston and the weighing element via the piston rod segment. The piston rod segment allows for a change in the rotational angle of the weighing element, such that the rotational angle is dependent on the rotational angle of the eccentric shaft or the oscillating piston. Depending on the rotational angle of the weighing element, the valve between the medium-pressure inlet and the working chamber can be opened or closed. Furthermore, the piston rod segment can serve as a fluidic and pressure-tight barrier between the low-pressure inlet and the high-pressure outlet.

[0022] In a further advantageous embodiment of the invention, the weighing element can be provided with a sealing coating on the side of the valve channel assembly. This measure allows for improved sealing between the weighing element and the receptacle that receives the weighing element.

[0023] Further features and advantages of the present invention will become clear from the following description of preferred embodiments with reference to the accompanying figures. The elements or features of the various embodiments can, in principle, be combined with one another as desired. These show:

[0024] Fig. 1 shows a schematic sectional view of a oscillating piston compressor;

[0025] Fig. 2 shows a detail “A” according to Fig. 1;

[0026] Fig. 3 shows a detail of a vibrating piston compressor, in particular the weighing element;

[0027] Fig. 4-7 a schematic representation of a compression process of a oscillating piston compressor (I - IV);

[0028] Fig. 8 shows a weighing element of a oscillating piston compressor in a position of the eccentric shaft at 0°;

[0029] Fig. 9 shows a cradle element of a vibrating piston compressor in a position of the eccentric shaft at 90°;

[0030] Fig. 10 shows a cradle element of a oscillating piston compressor in a position of the eccentric shaft at 180°;

[0031] Fig. 11 shows a cradle element of a vibrating piston compressor in a position of the eccentric shaft at 10°;

[0032] Fig. 12 shows a cradle element of a vibrating piston compressor in a position of the eccentric shaft at 20°;

[0033] Fig. 13 shows a cradle element of a vibrating piston compressor in a position of the eccentric shaft at 30°;

[0034] Fig. 14 shows a cradle element of a vibrating piston compressor in a position of the eccentric shaft at 90°;

[0035] Fig. 15 shows a cradle element of a vibrating piston compressor in a position of the eccentric shaft at 150°;

[0036] Fig. 16 shows a cradle element of a oscillating piston compressor in a position of the eccentric shaft at 160°;

[0037] Fig. 17 shows a cradle element of a vibrating piston compressor in a position of the eccentric shaft at 170°;

[0038] Fig. 18 shows a first embodiment of a weighing element in a perspective view;

[0039] Fig. 19 shows a first embodiment of a weighing element in a perspective view; Fig. 20 shows a first embodiment of a weighing element in a front view;

[0040] Fig. 21 shows a second embodiment of a weighing element in a top view;

[0041] Fig. 22 shows a second embodiment of a weighing element in a perspective view.

[0042] Opinion;

[0043] Fig. 23 shows a third embodiment of a weighing element in a top view;

[0044] Fig. 24 shows a third embodiment of a weighing element in a perspective view.

[0045] Opinion;

[0046] Fig. 25 shows a fourth embodiment of a weighing element in a top view;

[0047] Fig. 26 shows a fourth embodiment of a weighing element in a perspective view.

[0048] Opinion;

[0049] Fig. 27 shows a fifth embodiment of a weighing element in a top view;

[0050] Fig. 28 shows a fifth embodiment of a weighing element in a perspective view.

[0051] Opinion;

[0052] Fig. 29 shows a sixth embodiment of a weighing element in a perspective view;

[0053] Fig. 30 shows a sixth embodiment of a weighing element in a sectional perspective view;

[0054] Fig. 31 shows a seventh embodiment of a weighing element in a perspective view;

[0055] Fig. 32 shows a seventh embodiment of a weighing element in a front view;

[0056] Fig. 33 shows a detail of a vibrating piston compressor, in particular the weighing element;

[0057] Fig. 34 shows a detail of a weighing element according to Fig. 33.

[0058] The following reference symbols are used in the illustrations: a Rotation angle of the eccentric shaft

[0059] ÖB Opening area for medium-pressure injection into the compressor chamber

[0060] A3 Axis of rotation of the weighing element

[0061] A8 Rotation axis of the eccentric shaft

[0062] 1 oscillating piston

[0063] 2 Working room / compressor room

[0064] 3 weighing element

[0065] 4 Low-pressure inlet channel

[0066] 5 High-pressure outlet channel

[0067] 6 Medium pressure inlet channel

[0068] 7 cylinder housing

[0069] 8 eccentric shaft

[0070] 11 Piston rod segment / piston guide web

[0071] 31 Inlet-side component (of the weighing element)

[0072] 32 Outlet-side component (of the weighing element)

[0073] 33 Mounting for piston rod segment

[0074] 71 Mounting point for weighing element

[0075] 72 Clearance for piston rod segment

[0076] 311 Sliding surface (facing the inlet 71)

[0077] 312 Area (facing the recording 33)

[0078] 321 Sliding surface (facing the inlet 71)

[0079] 322 Area (facing the recording 33)

[0080] 323 Valve channel (groove)

[0081] 323a, b further valve channel. Features and details described in connection with a method naturally also apply in connection with the device according to the invention, and vice versa, so that the disclosure regarding the individual aspects of the invention always refers to each other or can refer to each other. Furthermore, any method described according to the invention can be carried out with the device according to the invention.

[0082] The terminology used herein serves only to describe certain embodiments and is not intended to limit the disclosure. As used herein, the singular forms "a" and "the" are intended to include the plural forms unless the context otherwise makes clear. It will also be clear that the expressions "indicates" and / or "indicating," when used in this description, specify the presence of the aforementioned features, integers, steps, operations, elements, and / or components, but do not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof. As used herein, the expression "and / or" includes any and all combinations of one or more of the associated, listed elements.

[0083] First, particular reference is made to Figures 1 to 3.

[0084] A vibrating piston compressor according to the invention essentially comprises a vibrating piston 1 received in a working chamber 2, which is driven by an eccentric shaft 8. The eccentric shaft 8 is preferably driven by an electric motor (not shown). However, other drive types are also conceivable, for example by means of the internal combustion engine already present in a motor vehicle.

[0085] The oscillating piston compressor further comprises a low-pressure inlet 4 opening into the working chamber 2 for the fluid to be compressed, a high-pressure outlet 5 opening into the working chamber 2 for the compressed fluid, and a medium-pressure inlet 6 for fluid at a medium-pressure level that lies between the pressure level of the low-pressure inlet 4 and the pressure level of the high-pressure inlet 5. Preferably, the fluid introduced via the medium-pressure inlet 6 is the same fluid introduced into the low-pressure inlet 4, but at a different pressure level. Preferably, the fluid, which can also be referred to as the working medium, is a refrigerant. The oscillating piston compressor is thus preferably part of an air conditioning system.The oscillating piston compressor can be part of a refrigerant circuit or similar system, such as stationary refrigeration units for food, building air conditioning, air conditioning for passenger vehicles, and refrigerators for private use. Its use is conceivable not only in air conditioning systems but also in heat pumps, etc. Furthermore, the compressor proposed here can also be used to compress process gases or air. Other applications are also possible.

[0086] Regarding the applied pressure, low pressure < medium pressure < high pressure applies. The following pressure ranges can be assumed as examples for refrigerant R744 (CO2) in the automotive sector.

[0087] Low pressure: 15-60 bar

[0088] Medium pressure: 35-90 bar

[0089] High pressure: 55-130 bar

[0090] Variation also arises in particular from different operating points, including different heat pump operating points.

[0091] The medium-pressure inlet 6 is in fluidic communication with the working chamber 2 via a valve controlled by the rotational position of the eccentric shaft 8. Depending on the angular position of the eccentric shaft 8 and thus the position of the oscillating piston 1, the fluidic connection is open or closed. Here, "fluidic connection" refers to a connection for the transfer of the fluid or working medium.

[0092] Specifically, the valve is implemented by comprising a weighing element 3 rotatably mounted in a receptacle 71, which is equipped with a valve channel assembly 323 that is fluidically connected to the medium-pressure inlet 6 and can be opened or closed depending on the angular position of the weighing element 3 relative to the working chamber 2. The weighing element 3 can also be referred to as a pendulum bushing or sliding bushing.

[0093] According to the invention, the valve channel assembly comprises at least one valve channel 323 in the weighing element 3, wherein the valve channel 323 is designed to be pressure-optimized, in particular depending on the desired mass flow rate (mean pressure level). It is also conceivable that the valve channel assembly comprises more than one single valve channel 323, for example, three valve channels 323a, 323b. The function of the valve will first be described in more detail in connection with a valve channel 323 that is open on one side, i.e., a groove-shaped configuration of the valve channel.

[0094] The weighing element 3 is mounted in the receptacle 71 within the cylinder housing 7. The weighing element 3 is rotatably mounted in the receptacle 71 about an axis A3, which is aligned parallel to the axis of rotation A8 of the eccentric shaft 8. The weighing element 3 includes a receptacle 33 for a piston rod segment 11 of the oscillating piston 1. The piston rod segment 11 is slidably mounted in the receptacle 33. The direction of displacement of the piston rod segment 11 is radial to the eccentric shaft axis. To allow sufficient displacement, a clearance 72 is provided above the receptacle 33 for the piston rod segment 11, into which the tip of the piston rod segment 11 can immerse.

[0095] The valve channel 323 extends over a section on the outside of the weighing element 3. Figure 2 shows that while the valve channel 323 is open to the intermediate pressure inlet channel 6, it is otherwise completely closed by the inner wall of the receptacle 71. It is evident that the state depicted in Figure 2 is the closed state of the valve. The fluid at intermediate pressure at the intermediate pressure inlet channel 6 can flow into the valve channel 323, but cannot exit it towards the working chamber 2. Accordingly, in this rotational position of the weighing element 3, there is no suitable connection between the intermediate pressure inlet channel 6 and the working chamber 2 for the transfer of fluids.

[0096] As explained above, the piston rod segment 11 is connected to the oscillating piston 1 and is slidably mounted in the weighing element 3. Therefore, by changing the position of the piston rod segment 11, the rotational angle of the weighing element 3 can be influenced by the position of the oscillating piston 1 and thus by the rotational angle of the eccentric shaft 8.

[0097] The piston rod segment 11 advantageously also separates the low-pressure area from the high-pressure area of ​​the working chamber 2. It is preferably provided that the weighing element 3 is composed of at least two components 31, 32, with the valve channel assembly being arranged in one of the components 32. In this respect, the weighing element 3 can have a component 31 facing the low-pressure inlet channel 4 and a component 32 facing the high-pressure outlet channel 5. The receptacle 33 for the piston rod segment 11 is preferably provided between the two components 31 and 32. Preferably, the outlet-side component 32 of the weighing element 3 is provided with the valve channel 323 in a circular or radially shaped outer contour.

[0098] In the sense of the inventive idea, the cradle element 3 is understood to be a pair of components with components 31, 32 facing the low-pressure inlet channel 4 for low pressure and the outlet channel 5 for high pressure.

[0099] The component pair can preferably be designed symmetrically with respect to their external dimensions. Theoretically, differently sized weighing element components are also possible, as long as they have a common axis of rotation.

[0100] Preferably, the weighing element 3 or the weighing element component 31 on the low-pressure side does not have a groove or channel. However, the weighing element 3 or the weighing element component 31 on the low-pressure side can also be designed with its own channel or groove, for example to save material / weight.

[0101] The division of the weighing element 3 into two parts is primarily due to manufacturing considerations. A two-part weighing element 3 is generally easier to manufacture.

[0102] The inlet-side component 31 of the weighing element 3 comprises a sliding surface 311 facing the receptacle 71 for the weighing element 3. Furthermore, the inlet-side component 31 comprises a surface 312 facing the piston segment 11 or the receptacle 33 for the piston rod segment 11.

[0103] The inlet-side component 31 of the weighing element 3 rests with its curved / radially shaped sliding surface 311 on the left side – as shown in the figure below – in the cylinder housing 7, and with its other, largely vertically shaped surface 312 – radially rounded in the direction of the oscillating piston 1 – rests on the right side against the piston guide web 11. The inlet-side component 31 does not have a valve channel 323. The outlet-side component 32 of the weighing element 3 preferably comprises a sliding surface 321 facing the receptacle 71 for the weighing element 3. Furthermore, the outlet-side component 32 comprises a surface 322 facing the piston segment 11 or the receptacle 33 for the piston rod segment 11.

[0104] The exhaust-side component 32 rests with its curved / radially shaped sliding surface 321 on the right side – as shown in the figure below – against the cylinder housing, and with its other, mostly vertically shaped surface 322 – radially rounded in the direction of the oscillating piston 1 – on the left side against the piston guide web 11. The second component has the valve channel 323 on its curved / radially shaped sliding surface 321.

[0105] Particular reference is made below to Figures 4 to 7.

[0106] The full-section views of Figs. 4 to 7 of a compressor according to the invention schematically show a compression process, subdivided into the individual processes I - IV.

[0107] The starting point is the closed state of the valve, as already outlined above, which in the following example is assumed to be at an angle of 0° for the eccentric shaft 8 or the oscillating piston 1. The weighing element 3 is in a state where the end of the valve channel 323 facing the working chamber 2 is not open to the working chamber 2.

[0108] The mean effective pressure is permanently present in the inlet channel 6 for the cylinder housing 7. The mean effective pressure inlet channel 6 is permanently fluidically connected to the valve channel 323 of the weighing element 3. During piston movement towards the low-pressure inlet channel 4, the weighing element 3 moves from TDC (top dead center) towards BDC (bottom dead center). During this movement, the valve channel 323 of the weighing element 3 is displaced circumferentially, or its position relative to the cylinder housing 7 is changed by the rotation of the weighing element 3, such that an additional pressure (mean effective pressure level) is indirectly generated between the mean effective pressure inlet channel 6 and the working chamber 2 via the valve channel 323.

[0109] In other words, the partial rotation of the weighing element 3 into the piston chamber 2 opens the valve channel 323 into the working chamber 2, allowing an additional mass flow of fluid (at medium pressure level) to enter the working chamber 2. The opening times of the valve channel 323, i.e., the times between "channel opens" and "channel closes" - depend on the position of the oscillating piston 1 and thus on the rotation angle of the eccentric shaft 8.

[0110] Geometrically, the opening times can be defined, for example, by the position of the valve channel 323 in the weighing element 3 and the resulting overlap with the working space 2. The resulting overlap can also be referred to as the opening area EE.

[0111] The achievable opening range ÖB, in particular the range between "channel opens" and "channel closes", focuses on the angular positions of the eccentric shaft between > 0° (top dead center = TDC) and 180° (bottom dead center = BDC), with the maximum deflection being at 90°.

[0112] The angular position of “channel opens” and “channel closes” is preferably symmetrical to 90°, which means: the length of the opening range can be varied by the design of the valve channel 323 in the weighing element 3, but a later “channel opens” generally results in an earlier “channel closes” (e.g. “channel opens” at 30° » “channel closes” at 150°).

[0113] The area from an angular position of 180° (bottom dead center = BDC) can also be referred to as the closing area for medium-pressure injection.

[0114] The valve channel 323 is preferably not in a pressure connection with the receptacle 33 for the piston rod segment 11 at any time or operating point.

[0115] The contact surfaces in the movement area of ​​the cylinder housing and weighing element on the outlet side 32 are designed to be particularly impermeable to pressure and mass flow. This prevents mean pressure losses.

[0116] The valve or valve channel 323 closes in time before a backflow occurs from the

[0117] Working chamber 2 can enter the medium-pressure inlet channel 6. The opening of the

[0118] Medium-pressure inlet channel 6 preferably only occurs when the oscillating piston 1 already covers the low-pressure inlet channel 4, which prevents backflow from the medium-pressure inlet channel 6 to the low-pressure inlet channel 4.

[0119] Particular reference is made below to Figures 8 to 10.

[0120] The opening range ÖB for medium-pressure injection into the compressor chamber 2 is established from an angular position of the weighing element 3 on the outlet side 32 > 0°.

[0121] The maximum opening range ÖB for medium-pressure injection into the compressor chamber is 32 = 90° when the weighing element 3 is at the outlet.

[0122] The closing range for medium-pressure injection into the compressor chamber is established from an angular position of the weighing element 3 on the outlet side of 32 > = 180°.

[0123] Particular reference is made below to Figures 11 to 17.

[0124] Figures 11 to 17 show in detail a design of the valve channel 323, which results in "channel opens" = 10° and "channel closes" = 170°.

[0125] Reference is made in particular to Figures 18 to 34 below. Figures 18 to 34 show various embodiments of the valve channel assembly, in particular of the valve channel 323, and of the weighing element 3. Specifically, only the outlet-side component 32 of a two-part weighing element 3 is shown. Alternatively, the weighing element can also be designed as a single piece.

[0126] Reference is made in particular to Figures 18 to 20 below. Figures 18 to 20 show a first embodiment of the valve channel assembly, in particular of the valve channel 323, of the weighing element 3.

[0127] This describes the design of the valve channel assembly with a single valve channel 323, which is configured as a groove within the weighing element 3 or the component 32. Particular reference is made below to Figures 21 and 22. Figures 21 and 22 show a second embodiment of the valve channel assembly, in particular of the valve channel 323, of the weighing element 3.

[0128] Here, the valve channel assembly comprises several parallel valve channels 323 of different lengths. Advantageously, different opening times can be achieved through the parallel valve channels 323 of different lengths.

[0129] Reference is made in particular to Figures 23 and 24 below. Figures 23 and 24 show a third embodiment of the valve channel assembly, in particular of the valve channel 323, of the weighing element 3.

[0130] Figures 23 and 24 show a valve channel 323 with a downwardly tapered / particularly radially rounded mass flow outlet. Advantageously, a pressure-optimized mass flow outlet area can be created.

[0131] Particular reference is made below to Figures 25 and 26. Figures 25 and 26 show a fourth embodiment of the valve channel assembly, in particular of the valve channel 323, of the weighing element 3.

[0132] Figures 25 and 26 show the valve channel 323 in a wide configuration. Advantageously, a high mass flow rate can be achieved.

[0133] Particular reference is made below to Figures 27 to 30. Figures 27 to 30 show a sixth embodiment of the valve channel assembly, in particular of the valve channel 323, of the weighing element 3.

[0134] Figures 27 to 30 show the valve channel 323 in a particularly deep, especially concave, configuration with a channel contour open to the sliding surface 311 of the receptacle 71 of the cylinder housing 7. Advantageously, the concave channel contour allows for improved inflow characteristics. Advantageously, the particularly deep channel contour allows for a high mass flow rate. Reference is subsequently made in particular to Figures 31 to 34. Figures 31 to 34 show a seventh embodiment of the valve channel assembly, in particular of the valve channel 323, and of the weighing element 3.

[0135] In particular, when the weighing element 3 is designed with an additional internal channel geometry, an improved seal between the weighing element 3 and the receptacle 71 in the cylinder housing 7 can be achieved. In other words, the valve channel 323 is incorporated into the weighing element 3 as a closed contour in this area.

[0136] In principle, the invention is not limited to the embodiments outlined above. Rather, variations are conceivable without deviating from the inventive idea.

[0137] For example, other pressure-optimized designs (not shown) of the valve channel 323 are possible.

[0138] For example, the valve channel 323 can be designed to be continuously tapered / conical from the cylinder housing 7 to the compressor chamber 2.

[0139] The valve channel 323 can also be wider and / or flatter.

[0140] It is also conceivable that several valve channels 323 are arranged next to each other.

[0141] It is also conceivable that the valve channels 323 are designed with different widths and depths.

[0142] It is also conceivable that the valve channel(s) 323 are equipped with pressure relief stages.

[0143] Preferably, the weighing element on the side of the valve channel assembly may be equipped with a sealing coating. One conceivable embodiment of the movement area of ​​cylinder housing 7 and weighing element 3 on the outlet side is that the surfaces facing each other are provided with a sealing coating.

[0144] In summary, it can therefore be stated that the valve channel assembly of the oscillating piston compressor described here comprises at least one valve channel, wherein the valve channel 323 is designed to be pressure-optimized, in particular depending on the respective desired mass flow level (mean pressure level).

[0145] Preferred embodiments of this valve channel device may consist of the following:

[0146] - the valve channel assembly comprises several parallel valve channels 323, 323a, 323b, in particular with different lengths, widths and / or depths,

[0147] - the valve channel 323 is equipped with a downwardly tapered and / or particularly radially rounded mass flow outlet,

[0148] - the valve channel 323 is designed to be wide or flat,

[0149] - the valve channel 323 is designed to be particularly deep,

[0150] - the valve channel 323 is designed concavely or conically,

[0151] - the valve channel 323 is designed as an open channel or a closed channel,

[0152] - the valve channel 323 is designed to taper continuously towards the working space, and / or

[0153] - the valve channel 323 is equipped with pressure dam stages (not shown).

[0154] The aforementioned configurations of the valve channel or valve channel assembly can, in principle, be combined with each other in any way desired.

Claims

Claims 1. Oscillating piston compressor, comprising - a vibrating piston (1) received in a working space (2) which is driven by an eccentric shaft (8), - a low-pressure inlet (4) leading into the working space (2) for the fluid to be compressed; - a high-pressure outlet (5) opening into the working chamber (2) for the compressed fluid; - a medium-pressure inlet (6) for fluid at a medium-pressure level which is between the pressure level of the low-pressure inlet (4) and the pressure level of the high-pressure inlet (5) is located, wherein the intermediate pressure inlet (6) is in fluidic communication with the working chamber (2) via a valve controlled by the rotational angular position of the eccentric shaft (8), wherein - the valve comprises a weighing element (3) received in a receptacle (71), which is equipped with a valve channel device connected to the medium pressure inlet (6) is in fluidic connection and is open or closed depending on the rotational angle position of the weighing element (3) relative to the working space (2), characterized in that the valve channel device comprises at least one valve channel (323), wherein the valve channel (323) is designed to be pressure-optimized.

2. Oscillating piston compressor according to claim 1, characterized in that the valve channel device comprises several parallel valve channels (323, 323a, 323b), in particular with different lengths, widths and / or depths.

3. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the valve channel (323) is equipped with a downwardly tapered and / or particularly radially rounded mass flow outlet.

4. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the aspect ratio, in particular the cross-section, of the valve channel (323) is designed in a flat configuration in a ratio of 2:1 (width to height) or in a narrow configuration in a ratio of 1:2 (width to height) to each other.

5. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the valve channel (323) is designed to be deep, in particular particularly deep.

6. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the valve channel (323) is concave or conical.

7. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the valve channel (323) is designed as an open channel or a closed channel.

8. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the valve channel (323) is designed to taper continuously in the direction of the working chamber (2).

9. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the at least one valve channel (323) is equipped with pressure staging stages.

10. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the weighing element (3) is composed of at least two components (31, 32), in particular two components (31, 32), wherein the valve channel device, in particular the at least one valve channel (323), is arranged in one of the components (32).

11. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the oscillating piston (1) is equipped with a piston rod segment (11), wherein the weighing element (3) is equipped with a receptacle (33) for the slidable receptacle of the piston rod element (11).

12. Oscillating piston compressor according to at least one of the preceding claims, characterized in that the weighing element (3) on the side of the valve channel assembly, in particular the valve channel (323), is equipped with a sealing coating.

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