Valve arrangement and operation method of piston compressor

Abstract

This relates to the optimization of the flow area in the intake valve section and discharge valve section of a piston compressor. [Solution] A valve arrangement for a piston compressor, comprising an intake valve section 200 and a discharge valve section 300, wherein the intake valve section 200 and the discharge valve section 300 together form an operating chamber head section 1200, the intake valve section 200 has a truncated pyramidal shape and is equipped with at least a first self-operating check valve.

Description

Detailed description of the invention

[0001] [Field] This invention relates to valve arrangements for piston compressors. More specifically, it relates to the optimization of flow area in the intake and discharge valve sections of a piston compressor. Although this invention has found particular utility in the field of high-temperature heat pumps, it can be used not only in high-temperature heat pumps but also in piston compressors in any machine.

[0002] [background] For example, thermal machinery such as heat pumps are well-known devices. Heat pumps are generally used to heat indoor spaces or to supply hot water, steam, or hot air to users. The use of heat pumps is preferable because they provide more sustainable heat than heating devices that use fossil fuels or direct electrical heating (e.g., purely resistive heaters). Heat pumps transfer thermal energy from a low-temperature heat source to a high-temperature heat sink.

[0003] Many industrial processes require high temperatures, such as steam or hot water, to produce products that are highly energy-intensive, especially when primary energy sources are used. Examples of industries that utilize high temperatures include pulp and paper, food and beverages, chemicals, automobiles, metals, plastics, engineering, textiles, and wood. For example, in the food and beverage industry, high temperatures are used in processes such as drying, evaporation, pasteurization, sterilization, boiling, distillation, blanching, decontamination, concentration, tempering, and smoking, to name just a handful of examples.

[0004] Industrial waste heat is often underutilized because it is at a low temperature, below the temperatures required for many industrial processes. This waste heat can be reused by upgrading it using high-temperature thermal machinery such as high-temperature heat pumps, which offers clear economic and environmental benefits.

[0005] Heat pumps, in both household and industrial settings, are a known technology. The operating principle of a heat pump is described in German patent application DE102011086476A1 by Siemens AG. This patent application conveniently describes the principle of a high-temperature heat pump.

[0006] A heat pump typically comprises an evaporation unit, a condensing unit, an expansion unit, and an electric compressor. The compressor is provided to compress the working fluid circulating in a closed-loop working fluid circuit.

[0007] The working fluid is supplied in a gaseous state from the evaporation unit to the compressor. The compressor typically draws in this working fluid and compresses it to a reasonable pressure, and as a result, after the compression of the gaseous working fluid in the compressor, the temperature of the working fluid rises to a level usable by the heat consumer.

[0008] Prior art utilizes various types of compressors for this application. For example, screw compressors, vane compressors, rotary piston compressors, and reciprocating compressors are all used in prior art.

[0009] Reciprocating compressors are well-known and understood in many applications, not just in the field of heat pump technology. Reciprocating compressors can handle temperatures up to several hundred degrees Celsius in the working chamber. Due to its structure being very similar to that of an internal combustion engine designed for lubricant temperatures up to approximately 100°C, it is very well suited to operating at temperatures above 100°C.

[0010] A reciprocating compressor has a basic operating principle that involves a movable piston in the working chamber. The movable piston draws in a gaseous working fluid during its downward stroke. The working fluid is drawn from the intake chamber into the working chamber through the intake valve section. The working fluid is compressed and then discharged through the discharge valve section into the discharge channel. This operation is very well understood by those skilled in the art and forms a very basic operating regime for well-known reciprocating compressors.

[0011] In a piston compressor, the piston reciprocates along the longitudinal axis of the cylinder. In this regard, the piston moves upward and downward along the longitudinal axis of the cylinder, resulting in reciprocating motion. In the context of this disclosure, the compressor described is referred to as a piston compressor.

[0012] It will be understood that when piston compressors are used in heat pump systems, they are most commonly combined with other components. For example, a piston compressor is typically combined with a drive unit, which is almost always an electric motor. Furthermore, a piston compressor is typically combined with a lubricant reservoir that continuously supplies lubricant to the piston compressor during use. Lubricant is typically required to lubricate the piston itself and / or other components of the piston compressor, such as bearings and cylinders.

[0013] The most basic design of a piston compressor involves providing a flat working chamber head section in the working chamber. The intake valve section and discharge valve section are located in the flat working chamber head section and are positioned perpendicular to the longitudinal axis of the cylinder, as will be described in more detail later.

[0014] A common characteristic of all types of compressors is that they operate with a working fluid, commonly referred to as a refrigerant or simply a gas. In some examples, the working fluid may be a condensable gas. In other examples, the working fluid never changes phase and therefore operates only in a gaseous state. Further examples include combinations of the two aforementioned modes. Throughout this disclosure, when referring to working fluid, all working fluids in any phase, including but not limited to partially liquid, gaseous, and supercritical, are intended.

[0015] The performance of heat pump compressors, and more specifically gas / vapor compressors, is primarily a result of the following three characteristics: 1. Machine efficiency 2. Volumetric efficiency 3. Equal Enentropy Efficiency Mechanical efficiency is primarily a result of internal mechanical friction, or rather, the absence of internal mechanical friction. Volumetric efficiency is primarily a result of the so-called internal dead volume (also known as the clearance volume in the compressor's working chamber, i.e., the minimum achievable internal volume within the cylinder of the compressor's working chamber during compression). Finally, isentropic efficiency is primarily a result of the effectiveness of the gas exchange process, including the intake and discharge processes.

[0016] In addition, there are further factors that affect the aforementioned characteristics, including, for example, heat leakage / unwanted heat exchange through internal surfaces, such as cylinder walls, which affects isentropic efficiency, and gas leakage through sealing elements, etc., which affects isentropic efficiency and volumetric efficiency.

[0017] The operation of a compressor consists of four main processes (or steps) that are performed periodically. In the case of a piston compressor, these are performed once for each rotation of the crankshaft (or other piston driving means such as a rotating swashplate).

[0018] 1. Inhalation process. 2. Compression process. 3. Dispensing process.

[0019] 4. Re-expansion process. The intake and discharge processes include a gas exchange process during which the working fluid, normally in the form of a gas / vapor, is either drawn into the cylinder or discharged from the cylinder. The gas exchange process is controlled by an intake valve and a discharge valve. Specifically, the intake valve controls the inflow of fresh, uncompressed gas into the cylinder during the intake process, while the discharge valve controls the outflow of compressed gas during the discharge process.

[0020] The compressor may have one or more cylinders, each cylinder has a corresponding set of suction valve and discharge valve, and each of the suction valve / discharge valve may in turn consist of a plurality of valves operating in parallel, as is extremely common. Throughout the present disclosure, reference is made to a single cylinder (and corresponding piston, suction valve section, discharge valve section, etc.) for clarity and conciseness. It will be understood that any single cylinder may be a single cylinder in a system of a plurality of cylinders (and corresponding pistons, suction valve sections, discharge valve sections, etc.).

[0021] In conventional compressor designs, the suction valve / discharge valve is often in the form of a so-called reed valve, which constitutes a simple and effective main component for many compressor applications.

[0022] A reed valve, in principle, comprises at least a valve plate or valve port section having reed elements (also called reed valve blades) and a retainer (sometimes called a stop plate). The reed elements are typically in the form of thin metal sheets, sometimes made from spring material, and perform the actual opening and closing of the valve by covering or not covering the port opening or slot in the valve plate or valve port section. A separate spring element may be provided, which is designed to continuously push the reed elements and thereby exert a closing force on the reed elements. This is to assist in closing the valve and to prevent flow through the valve when the valve should otherwise be closed. A retainer is typically a curved, relatively rigid sheet of metal, shaped to "curl" the lead element upon contact with its curved surface, for the purpose of restricting the movement of the lead element, guiding it, and preventing damage that could otherwise occur due to excessive bending during operation. At other times, the retainer takes the form of a retainer plate, which is fixed at a certain distance from the lead element, often with a spring element between the plate and the lead element. While the primary function remains the same, the design can be diverse.

[0023] Reed valves operate passively, meaning that they open or close solely due to the pressure difference (or lack thereof) between the ends of the reed element in the opening direction. Reed valves are small and lightweight, their design is generally simple, and they are easy to use. and enables production that is cost-effective. However, reed valves have several drawbacks for certain specific applications. Namely, it is difficult to design a reed valve that has an effective flow area comparable to that of certain other types of valves, and this also makes it difficult to design a compressor with a very low dead volume, particularly when the suction valve is of the reed type and a corresponding suction valve retainer (stopper plate) is provided, which subsequently results in the formation of some non-displaceable dead volume. As a result, compressors equipped with reed valves typically have a higher dead volume and a smaller effective flow area than necessary. This in turn results in lower volumetric efficiency and lower isentropic efficiency, respectively.

[0024] One area that can be improved in piston compressors is the arrangement of the suction valve section and the discharge valve section. Flow through these valve sections can be optimized in different ways. One such method is to increase the available area for each of the valve sections. This has been provided in prior art attempts to optimize performance. More specifically, attempts have been made to optimize performance by angling the suction valve and discharge valve away from a 90-degree arrangement relative to the cylinder axis.

[0025] That is, the valve sections form a wedge-shaped cross-section in the head section. This provides an increased surface area for the valve sections when compared with the aforementioned flat head section. Chinese utility model document CN201739117U describes an acetylene compressor that utilizes a wedge-shaped cross-section.

[0026] Further optimizing the valve section arrangement to further improve the performance of a piston compressor is difficult. Performance optimization is based on many different parameters, and these parameters are affected by changes to the head section design. Although it is possible to significantly increase the surface area of ​​the intake and discharge valve sections, this typically results in a significant increase in dead volume. In this regard, it is highly desirable to increase the area of ​​the intake and discharge valves without significantly increasing the dead volume, thereby resulting in an optimized valve arrangement for the piston compressor.

[0027] Furthermore, the configuration of specific valves used in the intake and discharge valve sections can significantly affect the performance of the piston compressor. For example, certain valves used may increase the dead volume in the head section, thereby affecting the performance of the piston compressor.

[0028] Therefore, piston compressors can be described as complex systems, and consequently, optimizing their performance depends on many interrelated components and design considerations. Therefore, it is highly desirable to provide a valve arrangement for a piston compressor that results in optimized piston compressor performance, rather than simply optimizing one parameter at the expense of another.

[0029] Patent document SE354505B discloses a piston compressor and, in particular, an arrangement of a pressure valve in such a compressor. The compressor comprises a cylinder in which a piston moves up and down via the action of a crankshaft. A valve plate is provided in the cylinder. An intake duct is located on the side of the cylinder head and is covered by an expansion valve flap.

[0030] Patent document US231059A discloses a vertically positioned pump barrel or cylinder, wherein the lower section inside the pump barrel or cylinder is located below It is constructed in the form of a frustum of a cone or pyramid with a closed end, and has a series of openings through its inclined side, which are spaced apart around the periphery of the pump barrel or cylinder, and each is adapted to be covered by one or more valves that are positioned to rest on an inclined valve seat within the aforementioned pump barrel and to open inward.

[0031] Patent document US2004 / 163713A discloses an intake reed valve comprising a central ring-shaped body having a pair of tabs extending radially outward. One of the pair of tabs is fixed to the valve plate, while the other tab is free to move. A constricted region is located between the fixed tab and the central ring-shaped body to facilitate bending / flexing of the intake reed valve.

[0032] Patent document US2015 / 0204323A1 discloses a compressor cylinder head having a cylinder head housing and at least one pressure valve. The pressure valve has an associated pressure valve channel within the cylinder head housing. The pressure valve channel connects a compression chamber located below the compressor cylinder head to a pressure chamber inside the compressor cylinder head. Furthermore, the compressor cylinder head has one or more channel portions having a first coolant channel system inside the cylinder head housing, the first coolant channel system may be filled with coolant flowing around the pressure chamber. By a casting method, the cylinder head housing is manufactured integrally with the first coolant channel system located inside, and further coolant channels are located on either side of the at least one pressure valve channel.

[0033] At least one object of the present invention is to prevent or at least mitigate one or more drawbacks of the prior art. [overview] According to a first aspect of the present invention, a valve arrangement for a piston compressor is provided, the valve arrangement comprising an intake valve section and a discharge valve section, the intake valve section and the discharge valve section together forming an operating chamber head section, the intake valve section having a truncated pyramidal shape.

[0034] The intake valve section may include at least a first self-operating check valve. The truncated pyramidal shape of the intake valve section may have multiple sides, and the first self-operating check valve is located on the first of the multiple sides of the intake valve section.

[0035] The first self-operating check valve may include a first reed suction valve. The intake valve section may include at least a first intake port configured to provide fluid communication through the intake valve section, and the first reed intake valve includes at least a first finger blade arranged to open and close the first intake port.

[0036] The intake valve section may include a second intake port configured to provide fluid communication through the intake valve section, and the first finger blade is positioned to open and close the second intake port.

[0037] The intake valve section may include a second intake port configured to provide fluid communication through the intake valve section, and the first reed intake valve includes a second finger blade positioned to open and close the second intake port.

[0038] The first finger blade and the second finger blade may be made as a single unit. The first finger blade and the second finger blade may not be integrated. The valve arrangement may further include a first finger catch configured to prevent the movement of the first finger blade.

[0039] The valve arrangement may further include a second finger catch configured to prevent the movement of the second finger blade. The discharge valve section may include a first discharge port configured to provide fluid communication through the discharge valve section and to prevent the movement of the first finger blade.

[0040] The discharge valve section may include a second discharge port configured to provide fluid communication through the discharge valve section and to prevent the movement of the first finger blade and / or the second finger blade.

[0041] The valve arrangement may further include a second self-operating check valve located on a second side of one of the multiple sides of the intake valve section. The second self-operating check valve may include a second reed suction valve.

[0042] The intake valve section may include at least a third intake port configured to provide fluid communication through the intake valve section, and the second reed intake valve includes at least a third finger blade arranged to open and close the third intake port.

[0043] The intake valve section may include a fourth intake port configured to provide fluid communication through the intake valve section, and the third finger blade is positioned to open and close the fourth intake port.

[0044] The intake valve section may include a fourth intake port configured to provide fluid communication through the intake valve section, and the second reed intake valve includes a fourth finger blade positioned to open and close the fourth intake port.

[0045] The first finger blade and the second finger blade may be made as a single unit. The first finger blade and the second finger blade may not be integrated. The valve arrangement may have a central axis configured to align with the longitudinal axis of the cylinder of the piston compressor during use, and the discharge valve section is configured perpendicular to the central axis so that during use, the discharge valve section is at 90 degrees, or substantially 90 degrees, with respect to the longitudinal axis of the cylinder.

[0046] According to a second aspect of the present invention, a valve arrangement for a piston compressor is provided, the valve arrangement comprising an intake valve section and a discharge valve section, the intake valve section and the discharge valve section together forming an operating chamber head section, the intake valve section having a substantially frustoconical shape with at least a first flat side surface.

[0047] The intake valve section may include at least a first self-operating check valve located on a first flat surface. The first self-operating check valve may include a first reed suction valve.

[0048] The intake valve section may include at least a first intake port configured to provide fluid communication through the intake valve section, and the first reed intake valve includes at least a first finger blade arranged to open and close the first intake port.

[0049] The valve arrangement may further include a first finger catch configured to prevent the movement of the first finger blade. The discharge valve section may include a first discharge port configured to provide fluid communication through the discharge valve section and to prevent the movement of the first finger blade.

[0050] The valve arrangement may have a central axis configured to align with the longitudinal axis of the cylinder of the piston compressor during use, and the discharge valve section is configured perpendicular to the central axis so that during use, the discharge valve section is at 90 degrees, or substantially 90 degrees, with respect to the longitudinal axis of the cylinder.

[0051] According to a third aspect of the present invention, a valve arrangement for a piston compressor is provided, the valve arrangement comprising an intake valve section and a discharge valve section, the intake valve section and the discharge valve section together forming an operating chamber head section, the discharge valve section having a truncated pyramidal shape.

[0052] According to a fourth aspect of the present invention, a valve arrangement for a piston compressor is provided, the valve arrangement comprising an intake valve section and a discharge valve section, the intake valve section and the discharge valve section together forming an operating chamber head section, the discharge valve section having a substantially frustoconical shape with at least a first flat side surface.

[0053] A fifth aspect of the present invention is provided, which comprises a cylinder having a longitudinal axis, a piston mounted in the cylinder and movable linearly along the longitudinal axis, and a valve arrangement according to any of the first to fourth aspects of the present invention.

[0054] The piston may have a piston head section that is matched to the working chamber head section. A sixth aspect of the present invention provides a method for optimizing fluid flow through a valve arrangement, the method comprising the steps of: providing a valve arrangement according to any of the first to fourth aspects of the present invention; drawing in a working fluid through an intake valve section; and discharging a working fluid through a discharge valve section.

[0055] A seventh aspect of the present invention provides a method for operating a piston compressor, the method comprising the steps of: providing a piston compressor according to a fifth aspect of the present invention; drawing a working fluid into a cylinder through an intake valve section; compressing the working fluid by moving a piston linearly along a longitudinal axis; and discharging the working fluid from the cylinder through a discharge valve section. [Brief explanation of the drawing]

[0056] Herein, embodiments of the present invention will be described with reference to the following drawings. [Figure 1] This shows a cross-sectional view of a prior art piston compressor. [Figure 2a-2b] Figure 2a shows a computer-aided design model of a first modified working chamber having a first angled surface and a second angled surface, and Figure 2b shows a computer-aided design model of a second modified working chamber having a first angled surface, a second angled surface and a third surface perpendicular to the cylinder axis. [Figure 2c] This shows a computer-aided design model of a third modified working chamber having a truncated tapered shape. [Figure 2d] This shows a computer-aided design model of the fourth modified working chamber, which has a truncated pyramidal shape. [Figure 3] This diagram shows a cross-sectional view through a cylinder head equipped with a valve arrangement for a piston compressor, but without showing the intake valve. [Figure 4] Figure 3 shows the same cross-sectional view passing through the cylinder head, but with the intake valve visible. [Figure 3a-4a] Figures 3 and 4 show cross-sectional views in which the cylinder is visible. [Figure 3b-3c] Figure 4 shows a detailed view of the intake valve section. [Figure 3d-3e] The first alternative finger blade configuration is shown. [Figure 3f-3g] A second alternative finger blade configuration is shown. [Figure 5] Figure 3 shows a plan view of the cylinder head. [Figure 6] Figure 3 shows an isometric view of the cylinder head. [Figure 7] A cross-sectional view is shown through the alternative cylinder head. [Figure 8] This shows a cross-sectional view of a multi-cylinder cylinder head. [Figure 9] Figure 8 shows an isometric view of the cylinder head of the multi-cylinder system. [Modes for carrying out the invention]

[0057] It will be noted that, for the sake of brevity and clarity, many of the basic components of the piston compressor are not shown in the drawings. Some of the basic components missing from the drawings are major components of the piston compressor, such as the piston and cylinder. It will be understood that these are omitted from the drawings because the exact configuration of the missing components is not important to the present invention as described with respect to the valve arrangement.

[0058] [Detailed description of the drawing] Throughout this explanation, terms such as truncated pyramid, truncated pyramidal shape, truncated pyramidal form, truncated pyramidal shape, truncated cone, truncated conical shape, truncated conical form, and truncated cone shape are used. In geometry, a pyramid is a polyhedron formed by connecting the base of a polygon with points called vertices. Each base edge and vertex forms a triangle called a lateral surface.

[0059] A regular pyramid has a regular polygonal base. An irregular pyramid has an irregular polygonal base. A pyramid with a triangular base is often called a tetrahedron. However, in this disclosure, a pyramid with a triangular base is included within the general term pyramid rather than being individually referred to as a tetrahedron. In this regard, a pyramid, and further shapes derived from pyramids discussed herein, may have a polygonal base with three or more edges and three or more sides. As will be discussed later, the number of sides is not important to the present invention.

[0060] Continuing with general geometric shapes, truncation is an operation of any dimension that cuts off the vertices of a polyhedron, resulting in a new facet in place of each vertex. More simply, a truncated shape is a shape from which one of its parts or one of its corners has been cut off.

[0061] As previously mentioned, truncated pyramids are referred to throughout this disclosure. The described truncated pyramids may have a number of faces so as to be substantially like truncated cones. As will be described in more detail below, even when there are many faces making up a truncated pyramid, each face has a substantially flat surface, as will be described below.

[0062] A cone is a geometric shape that tapers smoothly from a flat base to a point called the apex. Most commonly, the base of a cone is a perfect circle. However, the base does not need to be a perfect circle to form a cone in this context. In general usage, a cone is a geometric shape. Structurally, it is a right-circular cone, where the base is a circle and the axis of the cone passes through the center of the base perpendicular to its plane. This can be in contrast to an oblique cone, where the axis of the cone passes through the center of the base not perpendicularly. As mentioned above, the base can be of any shape, and the vertex can be anywhere within the cone. As mentioned above, a cone with a polygonal base is called a pyramidal cone.

[0063] In geometric shapes, a frustum is a three-dimensional geometric shape formed by the volume between two parallel planes and a polyhedron, which is often a pyramidal or conical shape. Therefore, in geometric shapes, a truncated cone is the same as a frustum, and a truncated pyramidal shape is the same as a frustum.

[0064] It will be understood that cones and pyramids may be solid or hollow. In this context, most references are made to valve sections being frustoconical or frustopyrotic. It will become clear that valve sections in piston compressors cannot be solid pyramidal or solid conical. Rather, as will be shown in the following description and with reference to the figures, valve sections are hollow structures with an outer shell. The use of "frustoconical" as a prefix to the main shape designation can generally be seen as the removal of the requirement that the shape has a vertex. In this regard, throughout this disclosure, since frustoconical and frustopyrotic shapes generally refer to frustocones and frustopyrotic shapes that are open at their top and bottom truncated portions, the working fluid can flow through their top and bottom truncated portions.

[0065] While it may often be convenient to provide truncated cones and truncated pyramidal shapes between two parallel planes, the terms truncated pyramidal and truncated cone are not limited to truncated portions between two parallel planes. Rather, it will be understood that truncated portions can be formed between two non-parallel planes.

[0066] Furthermore, a solid cone or pyramid would obstruct the aforementioned stroke of the piston within the cylinder at the head section of the cylinder. Figure 1 shows a prior art compressor 1 in the form of a piston compressor utilizing a condensable working fluid. Compressor 1 comprises a working chamber 2 and a reciprocating piston 3 located inside a cylinder 4. The working chamber 2 is defined by the piston 3, the cylinder 4, and a working chamber head section 5. The working chamber 2 is for compressing the condensable working fluid inside it. As can be seen in Figure 1, the working chamber head section 5 is formed by an intake valve section 6 and a discharge valve section 7. The working chamber head section 5 is substantially flat. That is, the intake valve section 6 and the discharge valve section 7 share substantially the same plane and are positioned so as not to be angled to each other, as can be clearly seen in Figure 1. Continuing to refer to Figure 1, the intake valve section and the discharge valve section are positioned perpendicular to the longitudinal axis L of the cylinder 4. In such an arrangement, the available flow area through the intake valve section and the discharge valve section is relatively small. As discussed earlier, a reduction in the available flow area has a detrimental effect on the overall performance of the compressor.

[0067] Referring here to Figures 2a and 2b, computer-aided design (CAD) models of working chamber volumes are shown, provided solely to assist in the description of the present invention, which will be explained later. Figures 2a and 2b are labeled “prior art” because they are models based on well-known valve arrangement designs. These models are provided as basic, modified working chamber volumes for the later description of flow through the top section of the working chamber.

[0068] First, referring to Figure 2a, the first working chamber volume 2a is provided. The intake valve section 6a and the discharge valve section (not visible in Figure 2a) are also provided. The 6a and discharge valve sections are positioned at a 90-degree angle with respect to the cylinder axis La, resulting in a wedge-shaped cross-section in the indicated head section.

[0069] An exemplary first working chamber volume 2a has a diameter d2a of 210 mm, and the intake valve section 6a and discharge valve section have a longitudinal height l2a of 75 mm from the top of the head section. The usable area of ​​the intake valve section 6a is approximately 210 cm². 2 Therefore, the usable area for the discharge valve section is approximately 210 cm². 2 Therefore, the total usable area for the intake valve section and the discharge valve section is approximately 420 cm². 2 That is the case.

[0070] Referring here to Figure 2b, a second working chamber volume 2b is provided. An intake valve section 6b is also provided, which is partially provided on the visible side shown in Figure 2b and partially provided in the same position on the non-visible side. A discharge valve section 7b is also provided. The intake valve section 6b is positioned at a 90-degree angle with respect to the cylinder axis Lb, and the discharge valve section 7b is positioned at a 90-degree angle with respect to the cylinder axis.

[0071] The cylinder 2b has a diameter d2b of 210 mm, and the intake valve section 6b has a longitudinal height l2b of 75 mm from the top of the head section. The usable area of ​​the intake valve section 6b is approximately 130 cm² on either side. 2 Therefore, the total usable area for the intake valve section 6b is approximately 260 cm². 2 Therefore, the usable area for the discharge valve section is approximately 200 cm². 2 Therefore, the total usable area for the intake valve section and the discharge valve section is approximately 460 cm². 2 That is the case.

[0072] Referring here to Figures 2c and 2d, CAD models of the working chamber volume are shown, provided solely to aid in the description of the present invention. These models are provided as basic, modified working chamber volumes for the subsequent description of the flow through the valve arrangement of the present invention.

[0073] Referring now to FIG. 2c, a third working chamber volume 2c is provided. A suction valve section 6c is also provided, wherein the suction valve section 6c is partially provided on the visible side shown in FIG. 2c and is also partially provided similarly on the non-visible side. That is, the suction valve section 6c is continuous around the periphery of the working chamber volume 2c at the non-visible portion. A discharge valve section 7c is also provided. The suction valve section 6c is offset from a 90-degree arrangement relative to the cylinder axis Lc, and the discharge valve section 7b is provided at 90 degrees relative to the cylinder axis.

[0074] The cylinder 2c has a diameter d2c of 210 mm, and the suction valve section 6c has a longitudinal height l2c from the top of the head section reaching 75 mm. The suction valve section 6c has a truncated pyramid shape including a plurality of side surfaces 6c'. Each of the plurality of side surfaces 6c' is a substantially flat surface that tapers toward the top. In this regard, since the plurality of side surfaces 6c' together form a truncated pyramid, the suction valve section 6c can be described as having a truncated pyramid shape.

[0075] By providing this truncated pyramid shape, the available area for the suction valve section 6c is significantly improved. The available area for the suction valve section is approximately 38 cm 2 per side surface 6c'. In the presently described example, twelve side surfaces are provided. Therefore, the total available area for the suction valve section 6c is approximately 450 cm 2 . The discharge valve section 7c is provided as a flat area at 90 degrees relative to the cylinder longitudinal axis. As will be described later, the discharge valve section 7c being at 90 degrees relative to the cylinder longitudinal axis is not essential, and this is rather presented merely as an example herein. In the present example, the available area for the discharge valve section is approximately 200 cm 2Therefore, the total usable area for the intake valve section and the discharge valve section is approximately 650 cm². 2 That is the case.

[0076] Referring here to Figure 2d, a fourth working chamber volume 2d is provided. An intake valve section 6d is also provided, which is partially provided on the visible side shown in Figure 2d and similarly partially provided on the non-visible side. That is, the intake valve section 6d is continuous around the periphery of the working chamber volume 2d in the non-visible portion. A discharge valve section 7d is also provided. The intake valve section 6d is positioned at a 90-degree angle with respect to the cylinder axis Ld, while the discharge valve section 7d is positioned at a 90-degree angle with respect to the cylinder axis Ld. Again, the discharge valve section 7d does not need to be at a 90-degree angle with respect to the cylinder axis Ld in other examples; this is provided in this example merely as an illustrative angle.

[0077] The cylinder 2d has a diameter d2d of 210 mm, and the intake valve section 6d has a longitudinal height l2d of 75 mm from the top of the head section. The intake valve section 6d has a frustum-shaped pyramid with multiple sides 6d'. Each of the multiple sides 6d' is a substantially flat surface that tapers towards the top. In this regard, it can be said that the intake valve section 6d has a frustum-shaped pyramid because the multiple sides 6d' together form a truncated pyramid. It will be understood that the terms frustum-shaped pyramid and frustum-shaped cone are intended to mean substantially frustum-shaped and substantially frustum-shaped cone, respectively, and that the terms frustum-shaped pyramid and frustum-shaped cone include imperfect frustums and imperfect frustums. Trustums and cones can be imperfect for a number of design reasons, such as to assist in valve positioning, machining of valve sections, sealing of valves and / or assemblies, to name just a few.

[0078] In the aforementioned example shown in Figure 2c, each side 6c' is provided as a quadrilateral. In the example described with reference to Figure 2d, side 6d' is close to a hexagon (two of the sides are elliptical arcs). It will be understood that such sides 6d' arranged together as described still result in a frustum pyramidal shape for the intake valve section 6d.

[0079] This truncated pyramidal shape significantly improves the usable area of ​​the intake valve section 6d compared to the examples shown in Figures 2a and 2b. The usable area of ​​the intake valve section is approximately 70 cm² on each side 6d'. 2 In the example described, there are six sides. Therefore, the total usable area for the intake valve section 6d is approximately 420 cm². 2 The discharge valve section 7d is provided as a flat area at a 90-degree angle to the longitudinal axis of the cylinder. The usable area for the discharge valve section is approximately 200 cm². 2 Therefore, the total usable area for the intake valve section and the discharge valve section is 620 cm². 2 That is the case.

[0080] In the truncated pyramidal shapes shown in Figures 2c and 2d, there are six and twelve sides, respectively, but it will be understood that in other examples, any number of sides, three or more, may be provided.

[0081] Referring now to Figures 3 and 4, the use of a truncated pyramidal intake valve section in a valve arrangement for a piston compressor will be described. Referring to Figure 3, a valve arrangement 100 for a piston compressor (not shown) is shown. The valve arrangement 100 comprises the main components of an intake valve section 200 and a discharge valve section 300. The valve arrangement 100 is located in the cylinder head 400 of the piston compressor. It is shown as being used within the structure. It will be understood that the intake valve section 200 allows the working fluid to be drawn into the working chamber 2' of the piston compressor (only partially shown in Figure 3) when in use. Similarly, the discharge valve section 300 allows the working fluid to be discharged from the working chamber 2' of the piston compressor when in use.

[0082] The intake valve section 200 and the discharge valve section 300 together form the working chamber head section 1200. In other words, when the valve arrangement 100 is assembled in the piston compressor for use, the intake valve section 200 and the discharge valve section 300 together form the upper portion of the working chamber 2' of the piston compressor.

[0083] The arrangement of the intake valve section 200 improves the fluid flow through the intake valve section 200 without substantially affecting the dead volume, thereby improving the compressor's performance, which, as mentioned above, has a significant impact on the overall performance.

[0084] In this regard, the intake valve section 200 has a truncated pyramidal shape with a plurality of sides 210, including a first side 211, a second side 212, a third side 213, a fourth side 214, a fifth side 215, and further sides that are not visible in the cross-sectional view shown in Figure 3.

[0085] Although not shown in the diagram, it will be understood that the piston in the piston compressor can stroke into the working chamber head section from below without obstruction. In this regard, the piston used with the valve arrangement described may be optimally configured to match the shape of the valve arrangement described. That is, since the intake valve section 200 has a truncated pyramidal shape, the piston may also have a truncated pyramidal shape that matches the shape of the intake valve section 200. In other words, the piston crown may be formed in a shape complementary to the shape of the working chamber head section 1200.

[0086] Each of the multiple sides 210 is substantially flat so that a valve requiring a flat surface can be positioned on one or more of the sides 210. Continuing to refer to Figure 3, the first side 211 includes a plurality of suction ports 220, including a first suction port 221, a second suction port 222, a third suction port 223, a fourth suction port 224, a fifth suction port 225, and a sixth suction port 226. The suction ports 220 are configured to provide fluid communication through the suction valve section 200 so that working fluid can be drawn into the working chamber through the suction ports 220 when in use.

[0087] As shown in Figure 4, the intake valve section 200 includes a first self-operating check valve in the form of a first reed valve 231. The first reed valve 231 includes a first finger blade 231' and a second finger blade 231'' arranged to open and close the intake port 220 (not visible in Figure 4), as described herein.

[0088] The first finger blade 231' is positioned to open and close the first intake port 221, the second intake port 222, and the third intake port 223, and the second finger blade 231'' is positioned to open and close the fourth intake port 224, the fifth intake port 225, and the sixth intake port 226. In the example described above, the first finger blade 231' and the second finger blade 231'' are integrated. This results in a larger first reed valve 231 compared to the case where the first finger blade 231' and the second finger blade 231'' are provided separately, as well as easier and faster production and assembly. This makes it possible. However, in some (not shown) alternatives, the first finger blade 231' and the second finger blade 231'' are provided separately, i.e., non-integrated.

[0089] The configuration shown, comprising three ports 221, 222, and 223 arranged with an associated first finger blade 231', and another three ports 224, 225, and 226 arranged with an associated second finger blade 231'', is merely an example. Alternative examples may include fewer or more ports, and / or fewer or more finger blades. For example, there may be one finger blade arranged to open and close six ports. In some examples, the finger blades may be arranged to open and close a square or rectangular array of ports, rather than a single row of ports as in the example described above.

[0090] As mentioned above, the reed valve requires some form of retainer, typically provided in the form of a stop plate. The retainer is typically a curved, relatively rigid sheet of metal, which is shaped to "roll" the reed element against its curved surface, for the purpose of restricting the movement of the reed element and thus guiding it, and otherwise preventing damage that may occur due to excessive bending during operation. As mentioned above, other prior art retainers are in the form of a retainer plate, which is fixed at a certain distance from the reed element and often has a spring element between the plate and the reed element. The reed element in the example described above is a finger blade 231', 231'' that is held without the use of a separate retainer as in the prior art, as will be described.

[0091] A brief reference to the plan view shown in Figure 5 reveals that the discharge valve section 300 is equipped with a plurality of discharge ports 320. The plurality of discharge ports 320 include a first discharge port 321, a second discharge port 322, a third discharge port 323, a fourth discharge port 324, and so on. Each of the plurality of discharge ports 320 is configured to provide fluid communication through the discharge valve section 300 so that the working fluid can be discharged from the working chamber through the discharge port 320 during use.

[0092] In the example described above, the discharge port 320 is provided as a curved slot in the discharge valve section 300. It will be understood that in alternative examples, the discharge port 320 may be provided as a circular hole, a rectangular slot, or any other shape, provided that fluid communication is provided throughout the entire discharge valve section 300 when in use.

[0093] Referring again to Figures 3 and 4, the discharge valve section 300 includes a stopper plate 331. The stopper plate 331 is positioned to prevent movement of a reed valve element (not shown) configured to open and close the discharge port 320.

[0094] In the example described above, the discharge valve section 300 is substantially flat and perpendicular to the longitudinal axis of the cylinder. In other alternative examples, it will be recognized that the discharge valve section 300 may be frustoconical or truncated. Alternatively, the discharge valve section 300 may have a wedge-shaped cross-section, as previously mentioned.

[0095] As can be seen in Figures 3 and 4, the first discharge port 321 is configured to prevent the movement of the first finger blade 231'. Thus, the first discharge port 321 is not prevented by a dedicated retainer or stop plate as in the prior art example. This provides a typical retaining function. However, since the first discharge port 321 is configured to prevent the movement of the first finger blade 231', a dedicated retainer or stop plate is not required. In the prior art, the dedicated retainer or stop plate increases the dead volume in the working chamber, so it is advantageous to remove the dedicated retainer or stop plate, especially when the first finger blade 231' can be stopped by the first discharge port 321 without significantly increasing the dead volume.

[0096] For the sake of brevity, although not described herein, it will be understood that each of the discharge ports 320 may be configured to block the movement of one or more of the finger blades. That is, in some examples, one discharge port may block the movement of multiple finger blades or all of the finger blades. In alternative examples, each discharge port may block the movement of a single finger blade. It will also be understood that not all discharge ports necessarily have to block the movement of any finger blade. Furthermore, it will be understood that combinations may be provided of discharge ports configured to block some of the finger blades and other separate retainers or catches configured to block the movement of other finger blades.

[0097] Figures 3a and 4a show the same arrangement as shown in Figures 3 and 4, but with the cylinder 401 visible. As previously mentioned, the working chamber 2' is defined by the (not shown) piston, cylinder 401, and working chamber head section 1200. The piston is not shown for clarity because it reciprocates (i.e., moves up and down) within the cylinder 401 during use.

[0098] The working chamber 2' has an upper portion 401A and a lower portion 401B. In Figure 3a, it can be seen that the third intake port 223 is oriented toward the upper portion 401A of the working chamber 2'. It can also be seen that the first intake port 221 and the second intake port 222 are oriented toward the lower portion 401B of the working chamber 2'.

[0099] It will be understood that, during use, when the piston compressor is performing the intake stroke, the piston strokes from the upper portion 401A to the lower portion 401B, from the so-called "top dead center" (TDC) to the so-called "bottom dead center" (BDC). In this regard, as the piston moves away from the TDC position, the majority of the flow of working fluid due to intake into the working chamber 2' should be directed toward the upper portion 401A of the working chamber 2'. By providing an upward inclination of the third intake port 223, the working fluid is delivered from the third intake port 223 through the third intake port 223 to the upper portion 401A of the working chamber 2'.

[0100] As the piston continues to move downward, the working chamber 2' expands, which will be filled with working fluid from the multiple intake ports 220. In this regard, as the piston continues to move downward (i.e., toward and into the lower portion 401B), the working fluid is delivered to the working chamber 2' from the first port 221 and the second port 222, which are conveniently oriented toward the lower portion 401B of the working chamber 2'. By providing a downward inclination of the first intake port 221 and the second intake port 222, the working fluid is delivered from the first intake port 221 and the second intake port 222 through the first intake port 221 and the second intake port 222 to the lower portion 401B of the working chamber 2'.

[0101] Furthermore, in the described example, the first finger blade 231' is positioned such that it opens from the side closer to the upper portion 401A of the working chamber 2'. It is advantageous to orient the port positioned at the open end of the finger blade so that it moves away from the finger blade as the finger blade opens. Yes. In other words, the improvement in fluid flow can be achieved by directing the flow through the third port 223 upward while the first finger blade 231' is open downward. To put it another way, the flow through the third port 223 is directed toward the upper portion 401A while the first finger blade 231' is open toward the lower portion 401B.

[0102] In some examples, each of the multiple inhalation ports 220 may be oriented to a specific inclination (either upward or downward). Alternatively, in some alternative examples, only some of the multiple inhalation ports 220 may be oriented to a specific inclination (either upward or downward).

[0103] The term "inclination" is intended to mean that the intake port in question is oriented into the working chamber, not perpendicular to the longitudinal axis Le. The term "upward" is intended to refer to the example illustrated with reference to the figure and the orientation being viewed provided. More generally, the term "upward" refers to the direction of the intake port toward the upper portion 401A, while the term "downward" refers to the direction of the intake port toward the lower portion 401B.

[0104] It will be understood that each of the multiple intake ports 220 may be provided as a substantially straight port, or that one or more of the multiple intake ports 220 may have a portion that is perpendicular to the cylinder longitudinal axis Le. In this regard, an intake port may have a portion perpendicular to the cylinder longitudinal axis Le and may be arranged to allow working fluid to flow through the intake port in a fluid passage that is not perpendicular to the cylinder longitudinal axis Le. For example, an intake port may have a perpendicularly positioned portion, which may further change into a curved or inclined portion along the passage through the intake port.

[0105] Accordingly, in this disclosure, the terms inclined, upward, and downward refer to the fluid path as the fluid leaves the intake port, rather than the inherent configuration of the intake port, i.e., the inherent shape of the port within the material in which the intake port is perforated.

[0106] The terms upward tilt and downward tilt are used for the orientations shown in Figures 3a and 3b. It will be understood that these terms are intended to mean that each port is oriented toward the upper portion 401A or the lower portion 401B of the working chamber 2'. The exact tilt provided will depend on many factors related to the precise geometric shape and configuration of the working chamber head section 1200 and cylinder 401.

[0107] Referring now to Figures 3b and 3c, a detailed view of the intake valve section 200 shown in Figure 4 is provided. It will be understood again that the intake valve section 200 allows the working fluid to be drawn into the working chamber 2' of the piston compressor (only partially shown in Figures 3b and 3c) during use. Similarly, the discharge valve section 300 allows the working fluid to be discharged from the working chamber 2' of the piston compressor during use.

[0108] The arrangement of the intake valve section 200 improves the performance of the compressor by improving the fluid flow through the intake valve section 200 without substantially affecting the dead volume.

[0109] As mentioned above, and as can be clearly seen here in Figures 3b and 3c The first side 211 is provided with a plurality of intake ports 220, including a first intake port 221, a second intake port 222, a third intake port 223, and further intake ports (not visible in Figures 3b and 3c). The intake ports 220 are configured to provide fluid communication through an intake valve section 200 so that working fluid can be drawn into the working chamber 2' through the intake ports 220 when in use.

[0110] Figures 3b and 3c show the first finger blades 231' of the first reed valve 231 in the closed and open positions, respectively. The first finger blade 231' is held without the use of a separate retainer, as in the prior art, as will be described in more detail here.

[0111] The discharge valve section 300 includes a first discharge port 321, a second discharge port 322, a third discharge port 323, and so on. As previously mentioned, the first discharge port 321 is configured to prevent the movement of the first finger blade 231'. In this regard, the first discharge port 321 may be matched to the shape of the first finger blade 231' so that when in use the first finger blade 231' can be received within the first discharge port 231 and its movement can be prevented. Thus, the first discharge port 321 provides a retaining function that is typically provided by a dedicated retainer or stop plate in the prior art examples. However, because the first discharge port 321 is configured to prevent the movement of the first finger blade 231', a dedicated retainer or stop plate is not required.

[0112] Specifically, referring to Figure 3c, we can see that when the first finger blade 231' moves to the open position, the first finger blade 231' is held by the first discharge port 321.

[0113] The first discharge port 321 may also be specifically molded and positioned to align with the orientation and geometric shape of the first finger blade 231' during operation, thereby achieving optimal blade movement. Furthermore, this may reduce friction and wear.

[0114] As mentioned above, the first finger blade 231' is positioned such that it opens from the side closer to the upper portion 401A of the working chamber 2'. It is advantageous to orient the port located at the open end of the finger blade so that it moves away from the finger blade as the finger blade opens. In other words, the improvement in fluid flow can be achieved by orienting the flow through the third port 223 upward while the first finger blade 231' is open downward. To put it another way, the flow through the third port 223 is directed towards the upper portion 401A while the first finger blade 231' is open toward the lower portion 401B.

[0115] As can be seen most clearly in the detailed views provided in Figures 3b and 3c, the first port 221 and the second port 222 are positioned such that their respective longitudinal port axes 221A and 222B are perpendicular to the first finger blade 231' and the internal shape of the intake valve section 200 located inside the working chamber 2'. In contrast, the third port 223 is positioned such that its longitudinal port axis 223A is not perpendicular to the first finger blade 231' and the internal shape of the intake valve section 200 located inside the working chamber 2'.

[0116] Provides an upper port oriented non-perpendicular to the first finger blade 231'. Thus, the arrangement currently described allows the lower port to direct the fluid to the lower portion of the working chamber 2', while the aforementioned port directs the fluid to the upper portion 401A of the working chamber 2'. As the working chamber 2' expands (i.e., as the piston moves downward), which will be filled with working fluid from the multiple intake ports 220, the lower ports (in this case, the first port 221 and the second port 222) work to supply the working fluid to the lower portion of the working chamber 2', while one or more upper ports (in this case, the third port 223) work to supply the working fluid to the upper portion 401A.

[0117] Referring here to Figures 3d and 3e, alternative arrangements of the first finger blade 231'1 are provided, where Figure 3d shows the first finger blade 231'1 in the closed position and Figure 3e shows the first finger blade 231'1 in the open position. This arrangement is similar to the arrangement described above, provided in Figures 3b and 3c. However, the first finger blade 231'1 is arranged to open from the side closer to the lower portion 401'B of the working chamber 2'1. The first finger blade 231'1 is arranged to open and close the first port 2211, the second port 2221, and the third port 2231, as in the previously described example. However, in the example described herein shown in Figures 3d and 3e, the first finger blade 231'1 is not blocked and held by the discharge port. Instead, as shown in Figure 3e, a stopper catch 231'A is provided, configured to prevent the movement of the first finger blade 231'1. The stopper catch 231'A is a relatively small catch that protrudes from the inner surface of the intake valve section 201 and is configured to prevent further opening of the first finger blade 231'1. In this regard, a dedicated retainer or stop plate is not required. In the example of the prior art, a dedicated retainer or stop plate increases the dead volume in the working chamber, so it is advantageous to remove the dedicated retainer or stop plate and instead use the stopper catch 231'A to prevent the first finger blade 231'1 from moving without significantly increasing the dead volume.

[0118] Although not described herein for the sake of brevity, in some examples, multiple stopper catches 231'A may be provided, configured to prevent the movement of one or more finger blades. That is, in some examples, one stopper catch 231'A may prevent the movement of multiple finger blades or all finger blades. In alternative examples, each stopper catch 213'2 may prevent the movement of a single finger blade.

[0119] Referring here to Figures 3f and 3g, an alternative arrangement of the second finger blade 231'2 is provided, where Figure 3f shows the second finger blade 231'2 in the closed position and Figure 3g shows the second finger blade 231'2 in the open position. This arrangement is similar to the arrangement described above, provided in Figures 3d and 3e. The second finger blade 231'2 is arranged to open and close the first port 2212, the second port 2222, and the third port 2232, as in the previously described example. However, in the example described herein shown in Figures 3f and 3g, the second finger blade 231'2 is not provided with a stopper catch that protrudes from the inner surface of the intake valve section and is configured to prevent further opening of the finger blade. Instead, as can be clearly seen in Figures 3f and 3g, the second finger blade 231'2 is arranged together with a hook 231'B attached to the open end of the second finger blade 231'2. In the example described above, the hook 231'B is a separate component attached to the end of the second finger blade 231'2. In alternative examples (not shown), the second finger blade 231'2 and the hook 231'B may be formed integrally. (None) In alternative examples, the blocking of the finger blade 231'2 may be provided by a non-hook structure, such as a pin, needle, notch, or any other suitable structure, formed or attached to the open end of the finger blade 231'2. Such a structure may also be matched with a recess 231'C or another geometric shape formed for the purpose of capturing such a structure.

[0120] Continuing to refer to Figures 3f and 3g, the intake valve section 202 includes a recess 231'C, which is configured to match the shape of the hook 231'B such that the hook 231'B can move within the recess 231'C but is prevented from moving outward. By connecting the hook 231'B to the second finger blade 231'2, the movement of the second finger blade 231'2 is also prevented in a similar manner to the previously described example, but without the need to form a feature that protrudes into the working chamber 2'2.

[0121] In the prior art, a dedicated retainer or stop plate inside the working chamber increases the dead volume inside the working chamber; therefore, it is advantageous to remove the dedicated retainer or stop plate and instead use a hook 231'B and a correspondingly formed recess 231'C to prevent the second finger blade 231'2 without significantly increasing the dead volume. Referring to Figures 5 and 6, further details of feasible arrangements of the cylinder head 400 are provided. Figure 5 shows a plan view of the cylinder head 400, and Figure 6 shows an isometric view of the cylinder head 400.

[0122] The cylinder head 400 comprises the aforementioned intake valve section 200 (not visible in Figures 5 and 6) and discharge valve section 300. The cylinder head 400 comprises a plurality of cylinder head bolt bosses 410, including a first cylinder head boss 411, a second cylinder head boss 412, a third cylinder head boss 413, a fourth cylinder head boss 414, a fifth cylinder head boss 415, and a sixth cylinder head boss 416, each of which is configured to receive (not shown) cylinder head bolts in use and fasten the cylinder head 400 to (not shown) cylinders.

[0123] The cylinder head 400 further includes an extension cup 500 which forms a discharge channel 510. The discharge channel 510 allows the discharged working fluid to be removed from the working chamber 2' (not visible in Figures 5 and 6) through the discharge channel 510, as will be described in more detail later. The extension cup 500 includes a plurality of discharge valve section bolt bosses 520, each of which is configured to receive a discharge valve section bolt (not shown) in use and fasten the top plate 600 (shown in Figures 3 and 4) to the cylinder head 400.

[0124] Referring to Figures 3 to 6, we can see that the intake valve section 200 is extended at its upper end to form an extension cup 500. Extending the intake valve section 200 eliminates the need to extend the multiple discharge valve section bolt bosses 520 on the front of the intake valve section 200, which would otherwise obstruct the flow path of the working fluid into the intake valve section 200. Therefore, the extension cup 500 keeps the flow path of the working fluid into the intake valve section 200 unobstructed, allowing for optimized fluid flow and leading to better performance of the piston compressor.

[0125] Continuing to refer to Figures 3 to 6, the cylinder head 400 has a plurality of outer bolt bosses 420, including 12 outer bolt bosses (including one boss 420' located in a more central part of the cylinder head 400), each of which receives an outer bolt (not shown) in use to connect the top plate 600 and the cylinder (not shown in Figures 3 and 4). You can see that the head 400 is configured to be fastened to the main compressor block (not shown).

[0126] Here, it will be noted that an intake channel 200A is formed, which allows for a smooth fluid flow of the working fluid being drawn into the working chamber during use, without obstruction. As mentioned above, the discharge channel 510 can also be clearly seen in Figures 3 and 4.

[0127] In summary, the cylinder head 400 is attached to the cylinder in use by means of cylinder head bolts (not shown) provided via cylinder head bolt bosses 410. The top plate 600 is attached to the extension cup 500 by discharge valve section bolts (not shown) provided via discharge valve section bolt bosses 520. The top plate 600 is attached to the cylinder head 400 at the outer portion of the cylinder head 400 by means of outer bolts (not shown) provided via outer bolt bosses 420, 420'.

[0128] In some (not shown) alternatives, a separate discharge pipe may be provided in the discharge channel 510, which can be advantageously secured to the cylinder head 400 and top plate 600 by the same discharge valve section bolts that are tightened within the discharge valve section bolt boss 520.

[0129] Since a very tight seal is formed between the extension cup 500 and the top plate 600, it is highly desirable to provide a first gasket (not shown) between the extension cup 500 and the top plate 600. Furthermore, since a very tight seal is formed between the cylinder head 400 and the top plate 600 at the outer bolts, it is highly desirable to provide a second gasket (not shown) between the cylinder head 400 and the top plate 600.

[0130] Referring here to Figures 3 to 5, the discharge valve section 300 is provided with a hydrolock prevention means in the form of a spring 700. As previously mentioned, the discharge valve section 300 includes a stopper plate 331. The stopper plate 331 is positioned to prevent the movement of a reed valve element (not shown) configured to open and close the discharge port 320. During normal operation of the compressor, the spring 700 attaches the stopper plate 331 to the cylinder head 400, instead of using, for example, a threaded bolt. In the event that a malfunction of the compressor causes a large amount of liquid to be present in the working chamber during the compression stroke and / or discharge stroke, the stopper plate 311 will lift up by pushing the spring 700 upward, thereby preventing serious damage to the compressor resulting from the excessive force that would have been applied to the stopper plate 311 if it had not been lifted.

[0131] In alternative examples (not shown), the hydrolock prevention means may be provided in the form of multiple springs. In some examples, the multiple springs may be spaced apart near the periphery of the stopper plate 331. In some examples, only multiple springs located near the periphery of the stopper plate 331 may be provided, while in other examples, one or more springs may be present at the center of the stopper plate 331 along with multiple springs located near the periphery of the stopper plate 331. When using multiple springs, it will be recognized that the force required for each spring is reduced because the load is shared across all of the springs. By providing some or all of the springs near the periphery of the stopper plate 331, an improvement in flow within the discharge channel 510 may be achieved compared to a single spring 700 located in the center.

[0132] Referring again to Figures 3 and 4, between the discharge channel 510 and the suction channel 200A An additional insulating element 800 is provided. When the piston compressor is used in a high-temperature heat pump, it will be recognized that the intake channel 200A carries the low-temperature working fluid and the discharge channel 510 carries the high-temperature working fluid. The insulating element 800 is provided to reduce or eliminate heat leakage between the intake channel 200A and the discharge channel 510.

[0133] In the example described above, the intake valve section 200 is provided as a whole in a frustum-shaped section, and the discharge valve section 300 is provided as a whole in the same section at a 90-degree angle to the longitudinal axis of the cylinder. However, it will be understood that in alternative examples, any part of the frustum-shaped section may be used as part of the discharge valve section, and / or any part of the section at a 90-degree angle to the longitudinal axis of the cylinder may be used as part of the intake valve section. Therefore, it is emphasized here that the terms frustum-shaped and frustum-cone are used herein to refer to the schematic shape of the intake section and do not exclude the possibility that a part, such as two or four sides, may be used as part of the discharge valve section. In addition, the terms frustum-shaped and frustum-cone do not exclude the possibility that a part, such as two or four sides, may be used for another purpose or may be absent; that is, in this context, the shape is still considered frustum-shaped or frustum-cone in such cases.

[0134] Referring to Figure 7, an alternative valve arrangement 100' for a piston compressor (not shown) is shown. Valve arrangement 100' comprises the main components of an intake valve section 200' and a discharge valve section 300'. Valve arrangement 100' is shown as being used within the cylinder head 400' of a piston compressor. Most of the arrangements of the alternative valve arrangement 100' are the same as those described with reference to Figures 3 to 6, and therefore, for the sake of brevity, a detailed description is not given. The difference between the arrangements described with reference to Figures 3 to 6 and the alternative arrangement shown in Figure 7 is that the discharge valve section 300' is configured in an overall flat arrangement in Figures 3 to 6, while in Figure 7 it is configured in part at an angle. In this regard, it can be seen that the discharge valve section 300' has a frustoconical first part 300'A and a second part 300'B that is flat and perpendicular to the cylinder axis. As mentioned above, the discharge valve section 300' in other examples may be provided in various configurations. For example, the discharge valve section 300' may be provided as a cone, pyramidal

[0135] As previously stated, a frustum in geometric form is a three-dimensional geometric shape formed by the volume between two parallel planes and a polyhedron, often a pyramidal or conical pyramid. Therefore, in geometric form, a truncated cone is the same as a frustum, and a truncated pyramidal pyramid is the same as a frustum. In this disclosure, the terms frustum and frustum are not limited to geometric shapes between two parallel planes. Although it may often be convenient to provide the geometric shape of a valve section between two parallel planes, the terms frustum and frustum are not limited to truncated portions between two parallel planes. Rather, it will be understood that truncated portions can be formed between two non-parallel planes.

[0136] As previously stated, a compressor may have one or more cylinders, each cylinder having its corresponding set of intake valve sections and discharge valve sections. Throughout the above disclosure, for clarity and brevity, we refer to a single cylinder (and its corresponding piston, intake valve section, and discharge valve section, etc.). It will be understood that any single cylinder may be a single cylinder in a system of multiple cylinders (and its corresponding piston, intake valve section, and discharge valve section, etc.). In this regard, one or more cylinders in a multi-cylinder system may be as described herein. In some cases, all cylinders in a multi-cylinder system may be as described herein. In some cases, all cylinders in a multi-cylinder system may be as described herein and may have substantially the same configuration.

[0137] Referencing Figures 8 and 9, alternative arrangements of the cylinder head 4000 are described here. The cylinder head 4000 is configured to be positioned with two cylinders. For the sake of brevity, only a two-cylinder cylinder head 4000 is described, but it will be recognized that other examples (not shown) may provide cylinder heads for assemblies with three, four, five, six, or more cylinders.

[0138] Figure 8 shows a cross-sectional view through the cylinder head 4000, and Figure 9 shows an isometric view of the cylinder head 4000. The cylinder head 4000 comprises a first head section 4001 and a second head section 4002. The first head section 4001 is configured to flow and receive working fluid from the working chamber of a first cylinder (not shown) attached to the first head section 4001 during use, and the second head section 4002 is configured to flow and receive working fluid from the working chamber of a second cylinder (not shown) attached to the second head section 4002 during use.

[0139] The first head section 4001 comprises a first intake valve section 2001 and a first discharge valve section 3001. Similarly, the second head section 4002 comprises a second intake valve section 2002 and a second discharge valve section 3002. Since the first intake valve section 2001 and the second intake valve section 2002, as well as the first discharge valve section 3001 and the second discharge valve section 3002, are substantially the same as the intake valve section 200 and the discharge valve section 300 described above, the repetition of their details is omitted here for the sake of brevity.

[0140] Furthermore, as in the example described above, the first head section 4001 includes a first extension cup 5001 that forms a first discharge channel 5101, and the second head section 4002 includes a second extension cup 5002 that forms a second discharge channel 5102.

[0141] As mentioned above, the discharge channels 5101 and 5102 allow for the removal of the discharged working fluid from the working chamber. As shown in Figure 8, a first discharge funnel 5201 and a second discharge funnel 5202 are provided, configured to receive the discharged working fluid and remove it from the discharge channels 5101 and 5102. Optionally, in some examples, a common manifold (not shown) connecting the first discharge funnel 5201 and the second discharge funnel 5202 may be provided.

[0142] Referring now to Figure 9, in the isometric view, the cylinder head 4000 is shown without the top plate or discharge funnel for clarity. The cylinder head 4000 includes a first intake passage 4000A, a second intake passage 4000B, a third intake passage 4000C, and a fourth intake passage 4000D. Although the example described here has four intake passages 4000A, 4000B, 4000C, and 4000D, it will be understood that in alternative examples, any number of intake passages may be provided. Advantageously, each of the intake passages 4000A, 4000B, 4000C, and 4000D allows the working fluid to flow from a common intake chamber (not shown) to the first intake valve section. It works to flow to both the first intake valve section 2001 and the second intake valve section 2002. That is, when the working fluid is flowed to the first intake valve section 2001, the working fluid may be drawn in from a common intake chamber (not shown) through any or all of the four intake passages 4000A, 4000B, 4000C, and 4000D.

[0143] During the periodic operation of two adjacent cylinders (not shown) supplied with working fluid from cylinder head 4000, flow limiting can be reduced. Furthermore, the described arrangement may result in a larger working fluid buffer, which in turn can reduce pressure fluctuations within cylinder head 4000. Moreover, as can be clearly seen in Figure 9, the working fluid flowing through the intake passages 4000A, 4000B, 4000C, 4000D to the first intake valve section 2001 or the second intake valve section 2002 can flow more freely to each intake valve section 2001, 2002 and between each intake valve section 2001 and each intake valve section 2002 compared to the aforementioned arrangement where each intake valve section is not in direct open fluid communication with another intake valve section, thereby mitigating flow limiting and, consequently, pressure fluctuations.

Claims

1. A valve arrangement (100) for a piston compressor, Intake valve section (200) and Discharge valve section (300) and Equipped with, The intake valve section (200) and the discharge valve section (300) together form an operating chamber head section (1200), The intake valve section (200) has a truncated pyramidal shape. A valve arrangement (100) characterized by the above.

2. The valve arrangement (100) according to claim 1, The suction valve section (200) comprises a valve arrangement (100) including at least a first self-operating check valve (231).

3. The valve arrangement (100) according to claim 2, The truncated pyramidal shape of the intake valve section (200) comprises a plurality of sides (210), Valve arrangement (100), wherein the first self-operating check valve (231) is located on the first side surface (211) of the plurality of sides (210) of the intake valve section (200).

4. A valve arrangement (100) according to claim 2 or 3, The valve arrangement (100) includes the first self-operating check valve (231) and a first reed suction valve (231).

5. The valve arrangement (100) according to claim 4, The intake valve section (200) includes at least a first intake port (221) configured to provide fluid communication through the intake valve section (200), Valve arrangement (100), wherein the first reed intake valve (231) comprises at least a first finger blade (231') arranged to open and close the first intake port (221).

6. The valve arrangement (100) according to claim 5, The intake valve section (200) includes a second intake port (222) configured to provide fluid communication through the intake valve section (200), The first finger blade (231') is arranged to open and close the second intake port (222) in a valve arrangement (100).

7. The valve arrangement (100) according to claim 5, The intake valve section (200) includes a second intake port (224) configured to provide fluid communication through the intake valve section (200), Valve arrangement (100), wherein the first reed intake valve (231) comprises a second finger blade (231'') arranged to open and close the second intake port (224).

8. The valve arrangement (100) according to claim 7, The first finger blade (231') and the second finger blade (231'') are integrally formed valve arrangement (100).

9. The valve arrangement (100) according to claim 7, The first finger blade (231') and the second finger blade (231'') are not integrated in the valve arrangement (100).

10. A valve arrangement (100) according to any one of claims 5 to 9, further, Valve arrangement (100) comprising a first finger catch (231'A) configured to prevent the movement of the first finger blade (231'1).

11. A valve arrangement (100) according to any one of claims 5 to 10, further, Valve arrangement (100) comprising a second finger catch configured to prevent the movement of the second finger blade (231'').

12. A valve arrangement (100) according to any one of claims 5 to 9, The valve arrangement (100) comprises a discharge valve section (300) and a first discharge port (321) configured to allow fluid communication through the discharge valve section (300) and to prevent the movement of the first finger blade (231').

13. A valve arrangement (100) according to any one of claims 7 to 9, The valve arrangement (100) comprises a second discharge port (322) configured to allow fluid communication through the discharge valve section (300) and to prevent the movement of the first finger blade (231') and / or the second finger blade (231'').

14. A valve arrangement (100) as described in claim 3, or as described in any of claims 4 to 13 when dependent on claim 3, further, Valve arrangement (100) comprising a second self-operating check valve located on a second side (212) of the plurality of sides (210) of the intake valve section (200).

15. The valve arrangement (100) according to claim 14, The second self-operating check valve is equipped with a second reed suction valve, in a valve arrangement (100).

16. The valve arrangement (100) according to claim 15, The intake valve section (200) includes at least a third intake port configured to provide fluid communication through the intake valve section (200), Valve arrangement (100), wherein the second reed intake valve comprises at least a third finger blade arranged to open and close the third intake port.

17. The valve arrangement (100) according to claim 16, The intake valve section (200) includes a fourth intake port configured to provide fluid communication through the intake valve section (200), The third finger blade is arranged to open and close the fourth intake port, in a valve arrangement (100).

18. The valve arrangement (100) according to claim 16, The intake valve section (200) includes a fourth intake port configured to provide fluid communication through the intake valve section (200), Valve arrangement (100), wherein the second reed intake valve comprises a fourth finger blade positioned to open and close the fourth intake port.

19. The valve arrangement (100) according to claim 18, The first finger blade and the second finger blade are integrally formed valve arrangement (100).

20. The valve arrangement (100) according to claim 18, The first finger blade and the second finger blade are not integrated in the valve arrangement (100).

21. A valve arrangement (100) according to any of the preceding claims, The valve arrangement (100) has a central axis configured to be aligned with the longitudinal axis (Le) of the cylinder (401) of the piston compressor when in use. The discharge valve section (300) is configured perpendicular to the central axis, so that when in use, the discharge valve section (300) is at a 90-degree angle, or substantially 90-degree angle, with respect to the longitudinal axis (Le) of the cylinder (401), in the valve arrangement (100).

22. A valve arrangement (100) for a piston compressor, Intake valve section (200) and Discharge valve section (300) and Equipped with, The intake valve section (200) and the discharge valve section (300) together form an operating chamber head section (1200), The intake valve section (200) has a substantially frustoconical shape with at least a first flat side surface. A valve arrangement (100) characterized by the above.

23. The valve arrangement (100) according to claim 22, The intake valve section (200) comprises a valve arrangement (100) including at least a first self-operating check valve (231) located on the first flat side surface (211).

24. A valve arrangement (100) according to either claim 22 or 23, The valve arrangement (100) includes the first self-operating check valve (231) and a first reed suction valve (231).

25. The valve arrangement (100) according to claim 24, The intake valve section (200) includes at least a first intake port (221) configured to provide fluid communication through the intake valve section (200), Valve arrangement (100), wherein the first reed intake valve (231) comprises at least a first finger blade (231') arranged to open and close the first intake port (221).

26. The valve arrangement (100) according to claim 25, further, Valve arrangement (100) comprising a first finger catch (231'A) configured to prevent the movement of the first finger blade (231').

27. A valve arrangement (100) according to claim 25 or 26, The valve arrangement (100) comprises a discharge valve section (300) and a first discharge port (321) configured to allow fluid communication through the discharge valve section (300) and to prevent the movement of the first finger blade (231').

28. A valve arrangement (100) according to any one of claims 22 to 27, The valve arrangement (100) has a central axis configured to be aligned with the longitudinal axis (Le) of the cylinder (401) of the piston compressor when in use. The discharge valve section (300) is configured perpendicular to the central axis, so that when in use, the discharge valve section (300) is at a 90-degree angle, or substantially 90-degree angle, with respect to the longitudinal axis of the cylinder (401), in the valve arrangement (100).

29. A valve arrangement (100) for a piston compressor, Intake valve section (200) and A discharge valve section (300) having a truncated pyramidal shape, Equipped with, The intake valve section (200) and the discharge valve section (300) together form the working chamber head section (1200). A valve arrangement (100) characterized by the above.

30. A valve arrangement (100) for a piston compressor, Intake valve section (200) and A discharge valve section (300) having a substantially frustoconical shape with at least a first flat side surface (211), Equipped with, The intake valve section (200) and the discharge valve section (300) together form the working chamber head section (1200). A valve arrangement (100) characterized by the above.

31. It is a piston compressor, A cylinder (401) having a longitudinal axis (Le), A piston mounted within the cylinder (401) and capable of moving linearly along the longitudinal axis (Le), A valve arrangement (100) according to any one of claims 1 to 30, A piston compressor equipped with this feature.

32. A piston compressor according to claim 31, A piston compressor wherein the piston has a piston head section matched to the working chamber head section (1200).

33. A method for optimizing fluid flow through a valve arrangement (100), a. A step of providing a valve arrangement (100) according to any one of claims 1 to 30, b. A step of drawing in working fluid through the intake valve section (200), c. A step of discharging the working fluid through the discharge valve section (300), A method that includes [the following features].

34. A method for operating a piston compressor, a. A step of providing a piston compressor according to either claim 31 or 32, b. A step of drawing the working fluid into the cylinder (401) via the intake valve section (200), c. A step of compressing the working fluid by moving the piston linearly along the longitudinal axis (Le), d. A step of discharging the working fluid from the cylinder (401) via the discharge valve section (300), A method that includes [the following features].

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