Piston compressor valve arrangement and method of using same

Abstract

A valve arrangement for a piston compressor, the valve arrangement comprising: a suction valve section (200); and a discharge valve section (300); wherein the suction valve section (200) and the discharge valve section (300) together form a working chamber head section (1200), and the suction valve section (200) has the form of a truncated pyramid.

Description

Technical Field

[0001] The present invention relates to a valve arrangement for a piston compressor. More specifically, the present invention relates to the optimization of flow areas in the suction valve section and the discharge valve section of a piston compressor. The present invention has particular applicability in the field of high temperature heat pumps, but can be used for piston compressors in any machine, not just high temperature heat pumps. Background Art

[0002] Heat engines such as heat pumps are known devices. Heat pumps are often used to heat indoor spaces or to supply hot water, steam or hot air to users. The use of heat pumps is desirable because they provide more sustainable heat than heating devices using fossil fuels or direct electrical heating (e.g., by 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 temperature heat, for example in the form of steam or hot water, and producing such heat is extremely energy intensive, especially when using primary energy sources. Examples of industries that utilize high temperature heat include pulp and paper, food and beverage, chemicals, automotive, metals, plastics, engineering, textiles, and wood. For example, in the food and beverage industry, high temperature heat is used for processes such as drying, evaporation, pasteurization, sterilization, boiling, distillation, blanching, blanching, concentration, tempering, and smoking, to name just a few.

[0004] Industrial waste heat is often not utilized due to its low temperature which is lower than that required in many industrial processes. This waste heat can be upgraded using high temperature heat engines such as high temperature heat pumps and thus reused, which has obvious economic and environmental benefits.

[0005] Heat pumps are known technology in domestic and industrial environments. The working principle of a heat pump is described in German patent application DE102011086476A1 of Siemens AG. Conveniently, this patent application describes the principle of a high temperature heat pump.

[0006] A heat pump generally comprises an evaporation unit, a condensation unit, an expansion unit and an electrically driven compressor. The compressor is arranged to compress a working fluid circulating in a closed-loop working flow path.

[0007] The working fluid is supplied to the compressor in gaseous state from the evaporation unit. The compressor usually sucks in the working fluid and compresses it to a relevant pressure, so that after the compression of the gaseous working fluid in the compressor, the temperature of the working fluid has increased to a level that is usable by the heat consumer.

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

[0009] Reciprocating compressors are well known and understood not only in the field of heat pump technology, but also in many applications. Reciprocating compressors are very suitable for operation at temperatures above 100 °C due to their close similarity to the construction of internal combustion engines, which are designed for working chamber temperatures of up to several hundred degrees Celsius and lubricant temperatures of up to about 100 °C.

[0010] The basic operating principle of a reciprocating compressor is to provide a movable piston in a working chamber. The movable piston draws in a gaseous working fluid on the downward stroke. The working fluid is drawn from the suction chamber into the working chamber through the suction valve section. The working fluid is compressed and then discharged through the discharge valve section to the discharge passage. This operation is very well understood by those skilled in the art and forms a very basic mode of operation of a well-known reciprocating compressor.

[0011] The piston in the piston compressor reciprocates on the longitudinal axis of the cylinder. In this regard, the piston travels up and down along the longitudinal axis of the cylinder, thereby providing the reciprocating motion. In the context of this disclosure, the compressor described is referred to as a piston compressor.

[0012] It will be appreciated that piston compressors are most often combined with other components when used in heat pump systems. For example, piston compressors are often combined with a drive unit, which in most cases is an electric motor. In addition, piston compressors are often combined with a lubricant reservoir to continuously provide lubricant to the piston compressor during use. Lubricants are often required to lubricate components of the piston compressor, such as the piston itself and / or bearings, cylinders, etc.

[0013] The most basic design of a piston compressor provides a working chamber with a flat working chamber head section. The suction valve section and the discharge valve section are arranged at the flat working chamber head section and perpendicular to the cylinder longitudinal axis, as will be described in more detail later.

[0014] What all compressor types have in common is that they are powered by a working fluid (also commonly referred to as a refrigerant or simply a gas). In some examples, the working fluid can be a condensable gas. In other examples, the working fluid never changes phase, so the working fluid only operates in a gaseous state. In other examples, there is a combination of the above two modes. Throughout this disclosure, when referring to a working fluid, it means any working fluid in any phase including, but not limited to: partially liquid; gaseous; and supercritical.

[0015] The performance of a heat pump compressor (more specifically, a gas / vapor compressor) depends primarily on the following three characteristics:

[0016] 1. Mechanical efficiency

[0017] 2. Volumetric efficiency

[0018] 3. Isentropic efficiency

[0019] The mechanical efficiency is primarily the result of the internal mechanical friction, or rather the lack thereof. The volumetric efficiency is primarily the result of the internal so-called dead volume (also called clearance volume, in the working chamber of the compressor, i.e. the minimum achievable internal volume in the cylinder of its working chamber during compression of the compressor). Finally, the isentropic efficiency is primarily the result of the effectiveness of the gas exchange processes, including the suction process and the discharge process.

[0020] Apart from this, there are other factors that affect the above characteristics, such as heat leakage / unwanted heat exchange through internal surfaces (e.g. cylinder walls), which affects the isentropic efficiency, and gas leakage through sealing elements, etc., which affects the isentropic efficiency as well as the volumetric efficiency.

[0021] The operation of a compressor consists of four main processes (or steps) that are performed cyclically. For a piston compressor, these processes are performed once for each revolution of the crankshaft (or other piston drive device, such as a swash plate):

[0022] 1. Inhalation process.

[0023] 2. Compression process.

[0024] 3. Discharge process

[0025] 4. Re-expansion process.

[0026] The suction and discharge processes include the gas exchange process during which the working fluid, usually in gaseous / vapor form, is sucked into or discharged from the cylinder. The gas exchange process is controlled by the suction valve and the discharge valve: the suction valve controls the flow of new uncompressed gas into the cylinder during the suction process, while the discharge valve controls the outflow of compressed gas during the discharge process.

[0027] The compressor may have one or more cylinders, and each cylinder has its corresponding set of suction valves and discharge valves, and the suction valves / discharge valves may each be composed of multiple valves working in parallel, which is very common. Throughout this disclosure, for the sake of clarity and brevity, reference is made to a single cylinder (and corresponding piston, suction valve section and discharge valve section, etc.). It should be understood that any single cylinder may be a single cylinder within a system of multiple cylinders (and corresponding pistons, suction valve sections and discharge valve sections, etc.).

[0028] In conventional compressor designs, the suction / discharge valve is usually in the form of a so-called reed valve, which constitutes a simple but effective main component for many compressor applications.

[0029] The reed valve in principle comprises at least a valve plate or a valve port portion, which has a reed element (also called a reed valve blade) and a retainer (sometimes also called a stop plate). The reed element is usually in the form of a thin metal sheet, which is sometimes also made of a spring material, wherein the reed element performs the actual opening and closing of the valve by covering or exposing a port opening, a groove or the like in the valve plate or the valve port portion. Sometimes a separate spring element is provided, which is made to continuously push the reed element and thus exert a force on the reed element in the closing direction. This helps the closure of the valve and prevents the fluid from passing through the valve when the valve should be closed. The retainer can usually be a curved, relatively rigid sheet metal part, which is shaped to "roll" the reed element against its curved surface to limit the movement of the reed element, thereby guiding the reed element and also preventing damage that may be caused by excessive bending during operation. Other times, the retainer is in the form of a retaining plate, which is fixed at a certain distance from the reed element and usually has a spring element between the two. The main function is the same, but the design may be different.

[0030] Reed valves are passively operated, meaning they open and close solely due to a pressure differential (or lack of a pressure differential) across the reed element in the opening direction.

[0031] Reed valves are compact and lightweight, their design is generally simple, and they are simple and inexpensive to manufacture. However, for some applications reed valves have some disadvantages: it is difficult to design a reed valve with the same effective flow area as some other valve types, and it is also difficult to design a compressor with very low dead volume, especially when the suction valve is of the reed type and a corresponding suction valve retainer (stop plate) is provided, because this will lead to the formation of some non-displaceable dead volume. As a result, compressors equipped with reed valves usually have a higher dead volume and a smaller effective flow area than required. This in turn leads to lower volumetric efficiency and isentropic efficiency, respectively.

[0032] One area where improvement may be made in piston compressors is the placement of the suction and discharge valve sections. Flow through these valve sections may be optimized in different ways. One such way is to increase the available area of ​​each valve section. Attempts to optimize performance have been provided in the prior art. More specifically, attempts have been made to optimize performance by placing the suction and discharge valves at angles other than 90 degrees relative to the cylinder axis.

[0033] That is, the valve section forms a wedge-shaped cross section at the head section. This provides an increased surface area for the valve section when compared to the flat head section described previously.

[0034] Chinese utility model document CN201739117U describes an acetylene compressor utilizing a wedge-shaped cross section.

[0035] It is difficult to further optimize the arrangement of the valve sections to further improve the performance of the piston compressor. The optimization of performance is based on many different parameters, which are affected by changes in the head section design. The surface area of ​​the suction valve section and the discharge valve section can be greatly increased, however, this usually results in a greatly increased dead volume. In this regard, it is very desirable to increase the suction valve and discharge valve area without greatly increasing the dead volume, thereby providing an optimized piston compressor valve arrangement.

[0036] In addition, the configuration of the specific valves used in the suction valve section and the discharge valve section may have a great impact on the performance of the piston compressor. For example, the specific valves used may increase the dead volume in the head section, thereby affecting the performance of the piston compressor.

[0037] Thus, a piston compressor can be described as a complex system whereby optimization of its performance depends on many interrelated components and design considerations.

[0038] It would therefore be highly desirable to provide a piston compressor valve arrangement that provides for optimization of the performance of the piston compressor rather than merely optimizing one parameter at the expense of another.

[0039] Patent document SE354505B discloses a piston compressor, in particular the arrangement of a pressure valve in such a compressor. The compressor comprises a cylinder, in which a piston moves up and down by the action of a crankshaft. The cylinder is provided with a valve plate. An intake duct is arranged on the side of the cylinder head, and the intake duct is covered by an expansion valve flap.

[0040] Patent document US231059A discloses a vertically positioned pump barrel or cylinder, the lower part of whose interior is made in the form of a frustum of a cone or pyramid, with its lower end closed and having a series of openings through its inclined side, which are arranged at intervals around its circumference and are suitable for being covered by one or more valves, which are arranged to rest on an inclined seat in the pump barrel and open inwardly.

[0041] Patent document US2004 / 163713A discloses a suction reed valve, which includes a central annular body having a pair of radially outwardly extending lobes. One of the pair of lobes is fixed to the valve plate, while the other lobes are free to move. A necked area is located between the fixed lobes and the central annular body to facilitate bending / deflection of the suction reed valve.

[0042] 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 in the cylinder head housing. The pressure valve channel connects the compression chamber arranged below the compressor cylinder head to the pressure chamber inside the compressor cylinder head. In addition, the compressor cylinder head has one or more channel portions, which have a first coolant channel system inside the cylinder head housing, and the first coolant channel system can be filled with coolant flowing around the pressure chamber. Via a casting method, the cylinder head housing is integrally molded with the first coolant channel system arranged therein, and additional coolant channels are arranged on either side of at least one pressure valve channel.

[0043] At least one object of the present invention is to obviate or at least mitigate one or more disadvantages of the prior art. Summary of the invention

[0044] According to a first aspect of the present invention, a valve device for a piston compressor is provided, the valve device comprising: a suction valve section; and a discharge valve section; wherein the suction valve section and the discharge valve section together form a working chamber head section, and the suction valve section has a frustopyramidal form.

[0045] The suction valve section may include at least a first self-actuated check valve.

[0046] The frusto-pyramidal form of the suction valve section may include a plurality of sides, wherein the first self-actuated check valve is located on a first side of the plurality of sides of the suction valve section.

[0047] The first self-actuated check valve may include a first reed suction valve.

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

[0049] The suction valve section may include a second suction port configured to provide fluid communication through the suction valve section; and the first finger blade is arranged to open and close the second suction port.

[0050] The suction valve section may include a second suction port configured to provide fluid communication through the suction valve section; and the first reed suction valve may include a second finger blade arranged to open and close the second suction port.

[0051] The first finger-shaped blade and the second finger-shaped blade may be integral.

[0052] The first finger-shaped blade and the second finger-shaped blade may be non-integral.

[0053] The valve device may further include a first finger stop configured to prevent movement of the first finger blade.

[0054] The valve device may further include a second finger stop configured to prevent movement of the second finger blade.

[0055] The discharge valve section may include a first discharge port configured to provide fluid communication through the discharge valve section and prevent movement of the first finger blade.

[0056] The discharge valve section may include a second discharge port configured to provide fluid communication through the discharge valve section and prevent movement of the first finger blade and / or the second finger blade.

[0057] The valve arrangement may further include a second self-actuated check valve located on a second side of the plurality of sides of the suction valve section.

[0058] The second self-actuated check valve may include a second reed suction valve.

[0059] The suction valve section may include at least a third suction port configured to provide fluid communication through the suction valve section; and the second reed suction valve includes at least a third finger blade arranged to open and close the third suction port.

[0060] The suction valve section may include a fourth suction port configured to provide fluid communication through the suction valve section; and the third finger blade is arranged to open and close the fourth suction port.

[0061] The suction valve section may include a fourth suction port configured to provide fluid communication through the suction valve section; and the second reed suction valve includes a fourth finger blade arranged to open and close the fourth suction port.

[0062] The first finger-shaped blade and the second finger-shaped blade may be integral.

[0063] The first finger-like blade and the second finger-like blade may be non-integral.

[0064] The valve device may have a central axis, which is configured to be aligned with the longitudinal axis of the cylinder of the piston compressor during use, wherein the discharge valve section is configured to be perpendicular to the central axis so that the discharge valve section is 90 degrees or approximately 90 degrees to the longitudinal axis of the cylinder during use.

[0065] According to a second aspect of the present invention, a valve device for a piston compressor is provided, the valve device comprising: a suction valve section; and a discharge valve section; wherein the suction valve section and the discharge valve section together form a working chamber head section, and the suction valve section has a generally frustoconical form including at least a first flat side surface.

[0066] The suction valve section may include at least a first self-actuated check valve located on the first planar side surface.

[0067] The first self-actuated check valve may include a first reed suction valve.

[0068] The suction valve section may include at least a first suction port configured to provide fluid communication through the suction valve section; and the first reed suction valve includes at least a first finger blade arranged to open and close the first suction port.

[0069] The valve device may further include a first finger stop configured to prevent movement of the first finger blade.

[0070] The discharge valve section may include a first discharge port configured to provide fluid communication through the discharge valve section and prevent movement of the first finger blade.

[0071] The valve device may have a central axis, which is configured to be aligned with the longitudinal axis of the cylinder of the piston compressor during use, wherein the discharge valve section is configured to be perpendicular to the central axis so that the discharge valve section is 90 degrees or approximately 90 degrees to the longitudinal axis of the cylinder during use.

[0072] According to a third aspect of the present invention, a valve device for a piston compressor is provided, the valve device comprising: an intake valve section; and an exhaust valve section; wherein the intake valve section and the exhaust valve section together form a working chamber head section, and the exhaust valve section has a truncated pyramid form.

[0073] According to a fourth aspect of the present invention, a valve device for a piston compressor is provided, the valve device comprising: an intake valve section; and a discharge valve section; wherein the intake valve section and the discharge valve section together form a working chamber head section, and the discharge valve section has a substantially truncated conical form including at least a first flat side surface.

[0074] According to a fifth aspect of the present invention, a piston compressor is provided, comprising: a cylinder comprising a longitudinal axis; a piston mounted in the cylinder and linearly movable along the longitudinal axis; and a valve device according to any one of the first to fourth aspects of the present invention.

[0075] The piston may include a piston head section that matches the working chamber head section.

[0076] According to a sixth aspect of the present invention, a method for optimizing fluid flow through a valve device is provided, comprising the following steps: providing a valve device according to any one of the first to fourth aspects of the present invention; inhaling a working fluid through the suction valve section; and discharging the working fluid through the discharge valve section.

[0077] According to a seventh aspect of the present invention, a method for operating a piston compressor is provided, comprising the following steps: providing a piston compressor according to the fifth aspect of the present invention; sucking a working fluid into the cylinder through the suction valve section; compressing the working fluid by linearly moving the piston along the longitudinal axis; and discharging the working fluid from the cylinder through the discharge valve section. BRIEF DESCRIPTION OF THE DRAWINGS

[0078] Embodiments of the present invention will now be described with reference to the following drawings, in which:

[0079] Figure 1 shows a cross-sectional view of a prior art piston compressor;

[0080] Figure 2a A computer-aided design model of a first improved working chamber having a first inclined surface and a second inclined surface is shown;

[0081] Figure 2b A computer-aided design model of a second improved working chamber having a first inclined surface and a second inclined surface and a third surface perpendicular to the cylinder axis is shown;

[0082] Figure 2c A computer-aided design model of a third improved working chamber having a truncated conical form is shown;

[0083] Figure 2dA computer-aided design model of a fourth improved working cavity in the form of a truncated pyramid is shown;

[0084] Figure 3 A cross-sectional view of a cylinder head including a piston compressor valve arrangement is shown, wherein the suction valve is not shown;

[0085] Figure 4 Shows Figure 3 The same cross-sectional view of the cylinder head shown in , showing the suction valve;

[0086] Figure 3a and 4a Shows Figure 3 and 4 The cross-section shown in , in which the cylinder is visible;

[0087] Figure 3b and 3c Shows Figure 4 A detailed view of the suction valve section shown in;

[0088] Figure 3d and e show a first alternative finger blade arrangement;

[0089] Figure 3f and 3g A second alternative finger blade arrangement is shown;

[0090] Figure 5 Shows Figure 3 A plan view of the cylinder head shown in ;

[0091] Figure 6 Shows Figure 3 An isometric view of the cylinder head shown in;

[0092] Figure 7 A cross-sectional view of an alternative cylinder head is shown;

[0093] Figure 8 shows a cross-sectional view of a multi-cylinder cylinder head; and

[0094] Fig. 9 Shows Figure 8 An isometric view of a multi-cylinder cylinder head shown in FIG.

[0095] It should be understood that for the sake of brevity and clarity, many 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 the cylinder. It should be understood that these components are missing from the drawings because the exact construction of the missing components is not important to the present invention described herein involving the valve device.

[0096] Detailed description of the accompanying drawings

[0097] Throughout this specification, reference is made to truncated pyramids, truncated pyramidal shapes, truncated pyramidal forms, truncated pyramidal forms, truncated cones, truncated conical shapes, truncated conical forms, truncated conical forms, etc. In geometry, a pyramid is a polyhedron formed by connecting a polygonal base and points called vertices. Each base edge and vertex form a triangle, which is called a side.

[0098] A regular pyramid has a regular polygonal base. An irregular pyramid has an irregular polygonal base. A pyramid based on a triangle is often referred to as a tetrahedron. However, in the present disclosure, pyramids with a triangular base are included within the general term pyramid, rather than being referred to as tetrahedrons alone. In this regard, pyramids, as well as other shapes derived from the pyramids discussed herein, can have a polygonal base including three or more edges and three or more sides. As will be discussed later, the number of sides is not critical to the present invention.

[0099] Still referring to general geometric shapes, truncation is the operation of cutting the vertices of a polyhedron in any dimension, creating new faces in place of each vertex. More simply, a truncated shape is one that has one of its parts or corners cut off.

[0100] As previously mentioned, reference is made to a truncated pyramid throughout this disclosure. The truncated pyramid described may have a large number of sides so that it appears generally similar to a truncated cone. As will be described in more detail later, even though there are many sides that make up the truncated pyramid, each side has a generally flat surface, as will be described later.

[0101] A cone is a geometric shape that tapers smoothly from a flat base to a point called the vertex. Most commonly, the base of a cone is a perfect circle. However, in this context, the base does not need to be a perfect circle to form a cone. In common use, a cone is usually a true circle, where the base is a circle and the axis of the cone passes through the center of the base at right angles to its plane. This can be contrasted with an oblique cone, where the axis of the cone passes through the center of the base non-perpendicularly. As mentioned earlier, the base can be of any shape, and the vertex can be located anywhere in the cone. As mentioned earlier, a cone with a polygonal base is called a pyramid.

[0102] A frustum in geometry is a three-dimensional geometric shape formed by the volume between two parallel planes and a polyhedron (usually a pyramid or cone). Thus, geometrically, a truncated cone shape is the same as a truncated cone shape, and a truncated pyramid shape is the same as a truncated pyramid shape.

[0103] It should be understood that cones and pyramids can be solid or hollow. In this article, reference is made primarily to valve sections in the form of truncated cones or truncated pyramids. It is obvious that the valve sections within a piston compressor cannot be solid pyramids or solid cone shapes. Instead, as will be shown in the upcoming specification and with reference to the accompanying drawings, the valve sections are shell-like hollow structures. The use of "truncated" as a prefix to indicate the primary shape can generally be considered to eliminate the requirement that the shape has a vertex. In this regard, throughout this disclosure, truncated cones and truncated pyramid forms generally refer to truncated cones and truncated pyramids that are open at their top and bottom truncations, thereby allowing the working fluid to flow through their top and bottom truncations.

[0104] Although it may often be convenient to provide a truncated cone and truncated pyramid form between two parallel planes, the terms truncated pyramid and truncated cone are not limited to truncation between two parallel planes. On the contrary, it should be understood that the truncation may be formed between two non-parallel planes.

[0105] Furthermore, a solid cone or pyramid will block the above-mentioned stroke of the piston in the cylinder at the head section of the cylinder.

[0106] Figure 1 A prior art compressor 1 in the form of a piston compressor using a condensable working fluid is shown. The compressor 1 comprises a working chamber 2 and a reciprocating piston 3 arranged in a cylinder 4. The working chamber 2 is defined by the piston 3, the cylinder 4 and the working chamber head section 5. The working chamber 2 is used to compress the compressible working fluid therein. Figure 1 As can be seen in FIG. 1 , the working chamber head section 5 is formed by the suction valve section 6 and the discharge valve section 7. The working chamber head section 5 is substantially flat. That is, the suction valve section 6 and the discharge valve section 7 are arranged so that they substantially share the same plane and are not angled relative to each other, as shown in FIG. Figure 1 As can be clearly seen in the Figure 1 , the suction valve section and the discharge valve section are arranged perpendicular to the cylinder longitudinal axis L of the cylinder 4. In this arrangement, the available flow area through the suction valve section and the discharge valve section is relatively small. As mentioned above, the reduced available flow area has an adverse effect on the overall performance of the compressor.

[0107] Reference now Figure 2a and 2b , Computer Aided Design (CAD) models of the working chamber volume are shown in the figures, these models are provided purely to help explain the invention which will be described in due course. Figure 2a and Figure 2bLabelled as "prior art" because they are based on models of well known valve arrangement designs. For the following explanation of the flow through the top section of the working chamber, these models are provided as a basic modified working chamber volume.

[0108] First reference Figure 2a , providing a first working chamber volume 2a. Also provided is an intake valve section 6a and an exhaust valve section (in Figure 2a The suction valve section 6a and the discharge valve section are arranged at a non-90 degree angle relative to the cylinder axis La, thereby providing a wedge-shaped cross section at the head section shown.

[0109] The exemplary first working chamber volume 2a has a diameter d2a of 210 mm, and the suction valve section 6a and the discharge valve section cover a height of 75 mm in the longitudinal direction l2a from the top of the head section. The usable area of ​​the suction valve section 6a is approximately 210 cm 2 , and the available area of ​​the discharge valve section is approximately 210cm 2 Therefore, the total available area of ​​the suction valve section and the discharge valve section is about 420cm 2 .

[0110] Reference now Figure 2b , providing a second working chamber volume 2b. A suction valve section 6b is also provided, which is partially arranged at Figure 2b The suction valve section 6b is arranged at a non-90 degree position relative to the cylinder axis Lb, and the discharge valve section 7b is arranged at 90 degrees to the cylinder axis.

[0111] The cylinder 2b has a diameter d2b of 210 mm and the suction valve section 6b covers a height of 75 mm in the longitudinal direction l2b from the top of the head section. The usable area of ​​the suction valve section 6b is approximately 130 cm on either side. 2 , so the total available area of ​​the suction valve section 6b is about 260cm 2 , and the available area of ​​the discharge valve section is approximately 200cm 2 Therefore, the total available area of ​​the suction valve section and the discharge valve section is approximately 460 cm 2 .

[0112] Reference now Figure 2c and 2d , CAD models of working chamber volumes are shown, purely to aid in the explanation of the invention. For the subsequent explanation of flow through the valve device of the invention, these models are provided as basic modified working chamber volumes.

[0113] Reference now Figure 2c, providing a third working chamber volume 2c. A suction valve section 6c is also provided, which is partially arranged at Figure 2c 2c, and are partially arranged in the same manner on the invisible side. That is, the suction valve section 6c extends around the circumference of the working chamber volume 2c in the invisible part. A discharge valve section 7c is also provided. The suction valve section 6c is arranged at a non-90 degree angle relative to the cylinder axis Lc, and the discharge valve section 7b is arranged at 90 degrees to the cylinder axis.

[0114] The diameter d2c of the cylinder 2c is 210 mm, and the suction valve section 6c covers a height of 75 mm in the longitudinal direction l2c from the top of the head section. The suction valve section 6c has a truncated pyramidal form including a plurality of side faces 6c'. Each of the plurality of side faces 6c' is a substantially flat surface that tapers toward the top. In this regard, the suction valve section 6c can be said to have a truncated pyramidal form because the plurality of side faces 6c' together form a truncated pyramid.

[0115] By providing this truncated pyramidal form, the usable area of ​​the suction valve section 6c is greatly improved. The usable area of ​​the suction valve section is approximately 38 cm on each side 6c'. 2 In the example currently described, twelve sides are provided. Therefore, the total available area of ​​the suction valve section 6c is approximately 450 cm 2 The outlet valve section 7c is arranged as a flat area at 90 degrees to the longitudinal axis of the cylinder. As will be explained later, it is not necessary for the outlet valve section 7c to be arranged at 90 degrees to the longitudinal axis of the cylinder, and this is presented here only as an example. In the present example, the available area of ​​the outlet valve section is approximately 200 cm 2 Therefore, the total available area of ​​the suction valve section and the discharge valve section is about 650cm 2 .

[0116] Reference now Figure 2d , providing a fourth working chamber volume 2d. A suction valve section 6d is also provided, which is partially arranged at Figure 2d d, and is partially arranged on the invisible side in the same manner. That is, the suction valve section 6d extends around the circumference of the working chamber volume 2d in the invisible part. A discharge valve section 7d is also provided. The suction valve section 6d is arranged at a non-90 degree angle relative to the cylinder axis Ld, and the discharge valve section 7d is arranged at 90 degrees to the cylinder axis Ld. Once again, in other examples, the discharge valve section 7d does not need to be 90 degrees to the cylinder axis Ld, which is provided only as an exemplary angle in this example.

[0117] The cylinder 2d has a diameter d2d of 210 mm, and the suction valve section 6d covers a height of 75 mm from the top of the head section in the longitudinal direction l2d. The suction valve section 6d has a truncated pyramidal form including a plurality of side faces 6d'. Each of the plurality of side faces 6d' is a substantially flat surface that tapers toward the top. In this regard, the suction valve section 6d can be said to have a truncated pyramidal form because the plurality of side faces 6d' together form a truncated pyramid. It should be understood that truncated pyramids and truncated cones mean approximately truncated pyramids and approximately truncated cones, respectively, and imperfect truncated pyramids and imperfect truncated cones are included in the terms truncated pyramids and truncated cones. Truncated pyramids and truncated cones may be imperfect due to a variety of design reasons, such as to help valve positioning, valve section processing, valve sealing and / or assembly, just to name a few examples.

[0118] exist Figure 2c In the previously described example shown, each side surface 6c' is configured as a quadrilateral. Figure 2d In the example described, the side faces 6d' approximate a hexagon (with two sides being elliptical arcs). It will be appreciated that such side faces 6d' arranged together as described still provide the suction valve section 6d with a truncated pyramidal form.

[0119] By providing this truncated pyramid form, relative to Figure 2a and 2b In the example shown, the usable area of ​​the suction valve section 6d is greatly improved. On each side 6d', the usable area of ​​the suction valve section is about 70 cm 2 In the example currently described, six sides are provided. Therefore, the total available area of ​​the suction valve section 6d is approximately 420 cm 2 The outlet valve section 7d is arranged as a flat area at 90 degrees to the longitudinal axis of the cylinder. The available area of ​​the outlet valve section is about 200 cm 2 Therefore, the total available area of ​​the suction valve section and the discharge valve section is 620 cm 2 .

[0120] Despite Figure 2c and 2d In the presently described truncated pyramidal forms shown in , six and twelve sides are provided, but it should be understood that any number of sides equal to or greater than three may be provided in other examples.

[0121] Reference now Figure 3 and Figure 4 The use of a truncated pyramidal intake valve segment in a valve arrangement for a piston compressor is described.

[0122] refer to Figure 3, a valve device 100 for a piston compressor (not shown) is shown. The valve device 100 comprises the main components of a suction valve section 200 and a discharge valve section 300. The valve device 100 is shown to be used in a cylinder head 400 of a piston compressor. It should be understood that the suction valve section 200 allows working fluid to be sucked into the working chamber 2' (in the piston compressor) in use. Figure 3 Similarly, the discharge valve section 300 allows the working fluid to be discharged from the working chamber 2' of the piston compressor in use.

[0123] The suction valve section 200 and the discharge valve section 300 together form a working chamber head section 1200. That is, when the valve device 100 is assembled in a piston compressor for use, the suction valve section 200 and the discharge valve section 300 together form the upper part of the working chamber 2' of the piston compressor.

[0124] The arrangement of the suction valve section 200 provides improved performance of the compressor by improving fluid flow through the suction valve section 200 without substantially affecting the dead volume which has a significant impact on overall performance as previously discussed.

[0125] In this regard, the suction valve section 200 includes a truncated pyramid form including 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 a Figure 3 Further side faces are not visible in the cross-section shown.

[0126] Although not shown in the drawings, it should be understood that the piston in the piston compressor can rush into the working chamber head section from below without obstruction. In this regard, the piston used with the valve device described herein can be optimally configured to match the shape of the described valve device. That is, since the suction valve section 200 includes a truncated pyramid form, the piston can also include a truncated pyramid form consistent with the form of the suction valve section 200. In other words, the piston top can be formed into a shape complementary to the shape of the working chamber head section 1200.

[0127] Each of the plurality of sides 210 is substantially flat such that a valve requiring a flat surface may be located on one or more of the sides 210 .

[0128] Still reference Figure 3The 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 the working fluid can be sucked into the working chamber through the suction ports 220 during use.

[0129] like Figure 4 As shown, the suction valve section 200 includes a first self-actuated 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", which are arranged to open and close the suction port 220 (at Figure 4 ), as now explained.

[0130] The first finger-like blade 231' is arranged to open and close the first suction port 221, the second suction port 222 and the third suction port 223, and the second finger-like blade 231" is arranged to open and close the fourth suction port 224, the fifth suction port 225 and the sixth suction port 226. In the example currently described, the first finger-like blade 231' and the second finger-like blade 231" are integral. This provides a larger first reed valve 231 and allows easier and faster production and assembly when compared to the first finger-like blade 231' and the second finger-like blade 231" provided separately. However, in some alternative examples (not shown), the first finger-like blade 231' and the second finger-like blade 231" are provided separately, that is, not integrally.

[0131] The arrangement shown, including three ports 221, 222, 223 arranged with associated first finger blades 231' and another three ports 224, 225, 226 arranged with associated second finger blades 231", is merely an example. In alternative examples, there may be a fewer or greater number of ports and / or a fewer or greater number of 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 row of ports as in the currently described examples.

[0132] As previously mentioned, reed valves require some form of retainer, typically provided in the form of a stop plate. The retainer is typically a curved, relatively rigid sheet metal piece that is shaped to cause the reed element to "roll" against its curved surface to limit the movement of the reed element, thereby guiding the reed element and also preventing damage that might otherwise be caused by excessive bending during operation. As previously mentioned, other prior art retainers are in the form of a retaining plate that is fixed at a certain distance from the reed element and typically has a spring element between the plate and the reed element. The reed elements in the example currently described are finger-like blades 231', 231", which can be retained without the use of a separate retainer, as in the prior art, as will be explained.

[0133] Brief reference Figure 5 From the plan view shown in FIG. 3 , it can be seen that the discharge valve section 300 includes 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 the like. The plurality of discharge ports 320 are each 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.

[0134] The outlet port 320 in the presently described example is provided as an arcuate slot in the outlet valve segment 300. It will be appreciated that the outlet port 320 in alternative examples may be provided as a circular hole, a rectangular slot or any other shape as long as fluid communication through the outlet valve segment 300 is provided in use.

[0135] Reference again Figure 3 and Figure 4 , the discharge valve section 300 includes a stopper plate 331. The stopper plate 331 is arranged to prevent movement of a reed valve element (not shown) configured to open and close the discharge port 320.

[0136] In the example currently described, the discharge valve section 300 is substantially flat and disposed perpendicular to the longitudinal axis of the cylinder. It should be appreciated that in other alternative examples, the discharge valve section 300 may be provided in the form of a truncated pyramid or a truncated cone. Alternatively, the discharge valve section 300 may include a wedge-shaped cross section as previously described.

[0137] like Figure 3 and Figure 4As shown, the first discharge port 321 is configured to prevent the movement of the first finger-like blade 231'. Therefore, the first discharge port 321 provides the retention function that is usually provided by a dedicated retainer or stop plate in the prior art examples. However, since the first discharge port 321 is configured to prevent the movement of the first finger-like blade 231', a dedicated retainer or stop plate is not required. In the prior art examples, 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-like blade 231' can be stopped by the first discharge port 321 without significantly increasing the dead volume.

[0138] Although not described herein, for the sake of brevity, it should be understood that each of the discharge ports 320 can be configured to prevent movement of one or more of the finger blades. That is, in some examples, one discharge port can prevent movement of multiple finger blades or all of the finger blades. In alternative examples, each discharge port can prevent movement of a single finger blade. It should also be understood that not all discharge ports must prevent movement of the finger blades. In addition, it should be understood that while a combination of discharge ports is provided to prevent movement of some finger blades, other separate retainers or latches can also be provided to prevent movement of other finger blades.

[0139] Figure 3a and Figure 4a Shown with Figure 3 and Figure 4 The same arrangement is shown, in which the cylinder 401 can now be seen. As previously described, the working chamber 2' is defined by the piston (not shown), the cylinder 401 and the working chamber head section 1200. For clarity, the piston is not shown because the piston reciprocates (i.e. moves up and down) in the cylinder 401 during use.

[0140] The working chamber 2' has an upper portion 401A and a lower portion 401B. Figure 3a It can be seen that the third suction port 223 points to the upper portion 401A of the working chamber 2'. It can also be seen that the first suction port 221 and the second suction port 222 point to the lower portion 401B of the working chamber 2'.

[0141] It should be understood that in use, when the piston compressor performs a suction stroke, the piston rushes 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, when the piston leaves the TDC position, most of the working fluid that flows into the working chamber 2' by suction should be directed to the upper portion 401A of the working chamber 2'. By tilting the third suction port 223 upward, the working fluid is delivered from the third suction port 223 to the upper portion 401A of the working chamber 2' through the third suction port 223.

[0142] As the piston continues to move downward, the working chamber 2' is filled and expanded by the working fluid from the plurality of suction 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 directed toward the lower portion 401B of the working chamber 2'. By tilting the first suction port 221 and the second suction port 222 downward, the working fluid is delivered to the lower portion 401B of the working chamber 2' from the first suction port 221 and the second suction port 222 through the first suction port 221 and the second suction port 222.

[0143] Furthermore, in the described example, the first finger blade 231' is arranged so that the first finger blade 231' opens from a side of the upper portion 401A closer to the working chamber 2'. When the finger blade is open, it is advantageous to direct the port located at the open end of the finger blade away from the finger blade. That is, an improvement in fluid flow can be provided by directing the flow through the third port 223 in an upward direction while the first finger blade 231' is open in a downward direction. In other words, the flow through the third port 223 is directed toward the upper portion 401A while the first finger blade 231' is open in a direction toward the lower portion 401B.

[0144] In some examples, each of the plurality of suction ports 220 may be oriented at a specific inclination (upward or downward). Alternatively, in some alternative examples, only some of the plurality of suction ports 220 may be oriented at a specific inclination (upward or downward).

[0145] The term "inclined" is intended to indicate that the suction port referred to is not directed into the working chamber perpendicular to the longitudinal axis Le. The term "upward" is intended to refer to the examples described with reference to the accompanying drawings and the viewing orientations provided. Therefore, more commonly, the term "upward" refers to the direction of the suction port towards the upper part 401A, while the term "downward" refers to the direction of the suction port towards the lower part 401B.

[0146] It should be understood that each of the plurality of suction ports 220 may be configured as a substantially straight port, or alternatively, one or more of the plurality of suction ports 220 may be provided with a portion arranged perpendicular to the longitudinal axis Le of the cylinder. In this regard, the suction port may include a portion perpendicular to the longitudinal axis Le of the cylinder, and may be arranged to convey the working fluid therethrough in a fluid flow path that is not perpendicular to the longitudinal axis Le of the cylinder. For example, the suction port may include a vertically arranged portion that further transitions into a curved or inclined portion along the flow path through the suction port.

[0147] Thus, in this disclosure, the terms oblique, upward, and downward refer to the fluid flow path as the fluid exits the intake port, rather than the specific configuration of the intake port - i.e., the specific shape of the port within the material in which it is bored, for example.

[0148] The terms upward and downward slope are relative to Figure 3a and 3b It should be understood that these terms are intended to indicate that the corresponding port is directed toward the upper portion 401A or the lower portion 401B of the working chamber 2'. The exact inclination provided will depend on many factors related to the exact geometry and configuration of the working chamber head section 1200 and the cylinder 401.

[0149] Reference now Figure 3b and 3c , provides Figure 4 A detailed view of the intake valve section 200 is shown in FIG.

[0150] Likewise, it will be appreciated that the suction valve section 200 allows working fluid to be drawn into the working chamber 2' (at Figure 3b and Figure 3c Similarly, the discharge valve section 300 allows the working fluid to be discharged from the working chamber 2' of the piston compressor in use.

[0151] The arrangement of the suction valve section 200 provides improved performance of the compressor by improving fluid flow through the suction valve section 200 without substantially affecting the dead volume.

[0152] As mentioned previously, and now available in Figure 3b and 3c It is clearly seen that the first side 211 includes a plurality of suction ports 220, and the plurality of suction ports 220 include a first suction port 221, a second suction port 222, a third suction port 223 and another suction port (in Figure 3b and 3c The suction port 220 is configured to provide fluid communication through the suction valve section 200 so that the working fluid can be sucked into the working chamber 2' through the suction port 220 in use.

[0153] Figure 3b and 3c The first finger blade 231 ′ of the first reed valve 231 is shown in a closed position and an open position, respectively.

[0154] As described in the prior art, the first finger blade 231 ′ is held without using a separate holder, which will now be explained in further detail.

[0155] The discharge valve section 300 includes a first discharge port 321 , a second discharge port 322 , a third discharge port 323 and the like.

[0156] As previously described, the first discharge port 321 is configured to prevent movement of the first finger-like blade 231'. In this regard, the first discharge port 321 can match the form of the first finger-like blade 231' so that the first finger-like blade 231' can be received in the first discharge port 231 and prevent movement of the first finger-like blade 231' during use. Therefore, the first discharge port 321 provides a retention function that is typically provided by a dedicated retainer or stop plate in prior art examples. However, since the first discharge port 321 is configured to prevent movement of the first finger-like blade 231', a dedicated retainer or stop plate is not required.

[0157] Specific reference Figure 3c It can be seen that when the first finger-like blade 231 ′ moves to the open position, the first finger-like blade 231 ′ is held by the first discharge port 321 .

[0158] The first discharge opening 321 may also be specifically formed and arranged to match the orientation and geometry of the first finger blade 231 ' during operation so that optimal blade movement can be achieved. In addition, this can reduce friction and wear.

[0159] As previously mentioned, the first finger blade 231' is arranged so that the first finger blade 231' opens from the side of the upper portion 401A closer to the working chamber 2'. When the finger blade is open, it is advantageous to direct the port located at the open end of the finger blade away from the finger blade. That is, an improvement in fluid flow can be provided by directing the flow through the third port 223 in an upward direction while the first finger blade 231' opens in a downward direction. In other words, the flow through the third port 223 is directed toward the upper portion 401A, while the first finger blade 231' opens in a direction toward the lower portion 401B.

[0160] As in Figure 3b and 3c As can be seen most clearly in the detailed view provided in , the first and second ports 221, 222 are arranged so that their respective longitudinal port axes 221A, 222B are perpendicular to the first finger blade 231' and the internal form of the suction valve section 200 within the working chamber 2'. In contrast, the third port 223 is arranged so that the longitudinal port axis 223A is not perpendicular to the first finger blade 231' and the internal form of the suction valve section 200 within the working chamber 2'.

[0161] The arrangement currently described provides that the arrangement of the upper ports that are not perpendicular to the first finger blade 231' allows the ports to direct fluid to the upper portion 401A of the working chamber 2', while the lower ports direct fluid to the lower portion of the working chamber 2'. When the working chamber 2' is filled with working fluid from the plurality of suction ports 220 and expands (i.e., when the piston moves downward), the lower ports (in this case, the first port 221 and the second port 222) are used to provide working fluid to the lower portion of the working chamber 2', while the upper port or ports (in this case, the third port 223) are used to provide working fluid to the upper portion 401A.

[0162] Reference now Figure 3d and 3e , an alternative first finger blade 231'1 arrangement is provided, wherein Figure 3d The first finger blade 231'1 is shown in a closed position, and Figure 3e The first finger blade 231'1 is shown in an open position. This arrangement is similar to Figure 3b and 3c The above arrangement provided in. 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, similar to the previously described example. However, in Figure 3d and 3e In the example shown in the present description, the first finger blade 231'1 is not blocked and held by the discharge port. Figure 3e As shown, a stopper 231'A is provided, which is configured to prevent movement of the first finger-like blade 231'1. The stopper 231'A is a relatively small stopper protruding from the inner surface of the suction valve section 201, and is configured to prevent further opening movement of the first finger-like blade 231'1. In this regard, no dedicated retainer or stop plate is required. In examples of 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 and instead provide the stop of the first finger-like blade 231'1 with the stopper 231'A without significantly increasing the dead volume.

[0163] Although not described herein, for the sake of brevity, it should be understood that in some examples, multiple stop latches 231'A may be provided, which are configured to prevent movement of one or more finger blades. That is, in some examples, one stop latch 231'A may prevent movement of multiple finger blades or all finger blades. In alternative examples, each stop latch 213'2 may prevent movement of a single finger blade.

[0164] Reference now Figure 3f and 3g , provides an alternative second finger blade 231'2 arrangement, wherein Figure 3f The second finger blade 231'2 is shown in a closed position, and Figure 3g The second finger blade 231'2 is shown in an open position. This arrangement is similar to Figure 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, similar to the previously described example. However, in Figure 3f and 3g In the example shown in the present description, the second finger-like blade 231'2 is not provided with a stopper protruding from the inner surface of the suction valve section and configured to prevent further opening movement of the finger-like blade. Figure 3f and 3g As can be clearly seen in the figure, the second finger-like blade 231'2 is arranged with a hook 231'B, which is attached to the open end of the second finger-like blade 231'2. In the example currently described, the hook 231'B is a separate component attached to the end of the second finger-like blade 231'2. In an alternative example (not shown), the second finger-like blade 231'2 and the hook 231'B can be formed integrally. In an alternative example (not shown), the stop of the finger-like blade 231'2 can be provided by a structure other than a hook, such as a pin, a needle, a notch or any other suitable structure formed or attached at the open end of the finger-like blade 231'2. Such a structure can be similarly matched with a recess 231'C or other geometric shape formed to retain such a structure.

[0165] Still reference Figure 3f and 3g , the suction valve section 202 includes a recess 231'C, which is configured to match the shape of the hook 231'B, so that the hook 231'B can move within the recess 231'C, but is blocked when it moves outward. Through the connection of the hook 231'B to the second finger-like blade 231'2, the movement of the second finger-like blade 231'2 is also blocked in a manner similar to the previously described examples, but without the need to form a protruding feature in the working chamber 2'2.

[0166] In prior art examples, dedicated retainers or stop plates within the working chamber increase the dead volume within the working chamber, so it is advantageous to remove the dedicated retainers or stop plates and instead provide for the use of hooks 231'B and correspondingly formed recesses 231'C to stop the second finger blade 231'2 without significantly increasing the dead volume. Figure 5 and Figure 6 , further details of a possible arrangement of cylinder head 400 are now provided. Figure 5 A plan view of a cylinder head 400 is shown, and Figure 6 An isometric view of a cylinder head 400 is shown.

[0167] The cylinder head 400 includes the previously described intake valve section 200 (in Figure 5 and Figure 6 The cylinder head 400 includes 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 cylinder head boss being configured to receive a cylinder head bolt (not shown) to secure the cylinder head 400 to a cylinder (not shown) in use.

[0168] The cylinder head 400 also includes an extended cup 500 forming a discharge passage 510. The discharge passage 510 allows the exhausted working fluid to be discharged from the working chamber 2' (at Figure 5 and Figure 6 The extension cup 500 includes a plurality of discharge valve segment bolt bosses 520, the plurality of discharge valve segment bolt bosses 520 including twelve discharge valve segment bosses, each of which is configured to receive a discharge valve segment bolt (not shown) to remove the top plate 600 (not shown) in use. Figure 3 and Figure 4 ) is fixed to the cylinder head 400.

[0169] Reference now Figures 3 to 6 , it can be seen that the suction valve section 200 is extended at its upper end to form the extension cup 500. By extending the suction valve section 200, the plurality of discharge valve section bolt bosses 520 do not need to extend in front of the suction valve section 200, which would block the working fluid flow path entering the suction valve section 200. Therefore, the extension cup 500 allows the working fluid flow path entering the suction valve section 200 to remain unobstructed, so that the fluid flow can be optimized, resulting in better performance of the piston compressor.

[0170] Still reference Figures 3 to 6 , it can be seen that the cylinder head 400 includes a plurality of external bolt bosses 420, the plurality of external bolt bosses 420 including twelve external bolt bosses (including a boss 420' disposed at a more central position of the cylinder head 400), each of the external bolt bosses being configured to receive an external bolt (not shown) to secure the top plate 600 (in use) Figure 3 and Figure 4 ) and cylinder head 400 are fixed to the main compressor cylinder block (not shown).

[0171] It should now be understood that the unobstructed suction passage 200a is formed to allow smooth fluid flow of the working fluid being sucked into the working chamber during use. As previously described, the discharge passage 510 may also be provided in Figure 3 and Figure 4 Clearly seen in.

[0172] In summary, the cylinder head 400 is attached to the cylinder in use by means of cylinder head bolts (not shown) disposed through the cylinder head bolt bosses 410. The top plate 600 is attached to the extension cup 500 by means of discharge valve section bolts (not shown) disposed through the discharge valve section bolt bosses 520. The top plate 600 is attached to the cylinder head 400 on the outside of the cylinder head 400 by means of external bolts (not shown) disposed through the external bolt bosses 420, 420'.

[0173] In some alternative examples (not shown), the exhaust passage 510 may be provided with a separate exhaust pipe which may advantageously be secured to the cylinder head 400 and the top plate 600 by the same exhaust valve segment bolts secured in the exhaust valve segment bolt bosses 520 .

[0174] It is highly desirable to form a very tight seal between the extension cup 500 and the top plate 600, so a first gasket (not shown) is provided between the extension cup 500 and the top plate 600. In addition, it is highly desirable to form a very tight seal between the cylinder head 400 and the top plate 600 at the outer bolts, so a second gasket (not shown) is provided between the cylinder head 400 and the top plate 600.

[0175] Reference now Figures 3 to 5 , the discharge valve section 300 is provided with a water lock prevention device in the form of a spring 700. As previously mentioned, the discharge valve section 300 includes a stop plate 331. The stop plate 331 is arranged to prevent the movement of a reed valve element (not shown), which is configured to open and close the discharge port 320. During normal operation of the compressor, the spring 700 fixes the stop plate 331 to the cylinder head 400 instead of using, for example, bolts. If a large amount of liquid is present in the working chamber during the compression and / or discharge stroke due to a fault in the operation of the compressor, the stop plate 311 will be lifted by pushing the spring 700 upwards, and thus prevent significant damage to the compressor due to excessive force on the stop plate 311.

[0176] In an alternative example (not shown), the water lock prevention device can be provided in the form of multiple springs. In some examples, multiple springs can be spaced apart near the circumference of the stop plate 331. In some examples, only multiple springs located near the circumference of the stop plate 331 can be provided, while in other examples, there can be springs located near the circumference of the stop plate 331 and one or more springs at the center of the stop plate 331. In the case of using multiple springs, it should be understood that the force required for each spring is reduced as the load is shared on multiple springs. Compared with a single centrally positioned spring 700, arranging some or all springs near the circumference of the stop plate 331 can improve the flow in the discharge channel 510.

[0177] Reference again Figure 3 and Figure 4 , a heat insulating element 800 is also provided, which is arranged between the discharge channel 510 and the suction channel 200A. It should be understood that when the piston compressor is used in a high-temperature heat pump, the suction channel 200A conveys a low-temperature working fluid, and the discharge channel 510 conveys a high-temperature working fluid. The heat insulating element 800 is provided to reduce or eliminate heat leakage between the suction channel 200a and the discharge channel 510.

[0178] Although in the example currently described, the suction valve section 200 is completely arranged in the truncated pyramid section, and the discharge valve section 300 is completely arranged in the section at 90 degrees to the longitudinal axis of the cylinder, it should be understood that in alternative examples, some of the truncated pyramid sections can be used as part of the discharge valve section and / or some of the sections at 90 degrees to the longitudinal axis of the cylinder can be used as part of the suction valve section. Therefore, it is now emphasized that the terms truncated pyramid and truncated cone are used in this article to refer to the general shape of the suction section, and do not exclude the possibility that a part (such as two or four sides, for example) is used as part of the discharge valve section. In addition, the terms truncated pyramid and truncated cone do not exclude the possibility that a part (such as two or four sides, for example) is used for another purpose or is missing - in this context, in this case, the form is still considered to be a truncated pyramid or a truncated cone.

[0179] refer to Figure 7 , shows an alternative valve device 100' for a piston compressor (not shown). The valve device 100' comprises the main components of a suction valve section 200' and a discharge valve section 300'. The valve device 100' is shown for use in a cylinder head 400' of a piston compressor. Most of the features of the alternative valve device 100' are similar to those of the reference Figures 3 to 6 The valve arrangements described are identical and therefore, for the sake of brevity, a detailed description is not provided. Figures 3 to 6 The layout described Figure 7The difference between the alternative arrangement shown in FIG. 1 and FIG. 2 is that the outlet valve section 300 ′ is Figures 3 to 6 In a completely flat arrangement, and in Figure 7 The outlet valve section 300' is configured as an angled portion in the middle. In this regard, it can be seen that the outlet valve section 300' has a first portion 300'A that is truncated cone and a second portion 300'B that is flat and disposed perpendicular to the cylinder axis. As previously mentioned, in other examples, the outlet valve section 300' can be disposed in various configurations. For example, the outlet valve section 300' can be configured as a cone, a pyramid, a truncated cone, or a truncated pyramid.

[0180] As previously mentioned, a geometric frustum is a three-dimensional geometric shape formed by a volume between two parallel planes and a polyhedron (usually a pyramid or cone). Therefore, geometrically, a truncated cone shape is the same as a truncated cone shape, and a truncated pyramid shape is the same as a truncated pyramid shape. In the present disclosure, the terms truncated cone and truncated pyramid are not limited to geometric shapes between two parallel planes. Although it may be generally convenient to set the valve section geometry between two parallel planes, the terms truncated pyramid and truncated cone are not limited to truncations between two parallel planes. On the contrary, it should be understood that truncations can be formed between two non-parallel planes.

[0181] As previously mentioned, the compressor can have one or more cylinders, and each cylinder has its corresponding set of suction valve sections and discharge valve sections. Throughout the above disclosure, for the sake of clarity and brevity, reference is made to a single cylinder (and corresponding pistons, suction valve sections and discharge valve sections, etc.). It should be understood that any single cylinder can be a single cylinder within a system of multiple cylinders (and corresponding pistons, suction valve sections and discharge valve sections, etc.). In this regard, one or more cylinders of a multi-cylinder system can be as described herein. In some examples, all cylinders of a multi-cylinder system can be as described herein. In some examples, all cylinders of a multi-cylinder system can be as described herein and have substantially the same configuration.

[0182] Reference now Figure 8 and Fig. 9 , an alternative arrangement of a cylinder head 4000 is now described. The cylinder head 4000 is configured to be arranged with two cylinders. For the sake of brevity, only a two-cylinder cylinder head 4000 is described, but it should be understood that in other examples (not shown), a cylinder head for assembly with three, four, five, six or more cylinders may be provided.

[0183] Figure 8 A cross-sectional view of a cylinder head 4000 is shown, and Fig. 9 An isometric view of cylinder head 4000 is shown.

[0184] The cylinder head 4000 comprises a first head section 4001 and a second head section 4002. The first head section 4001 is configured to deliver and receive working fluid from a working chamber of a first cylinder (not shown) attached to the first head section 4001 in use, and the second head section 4002 is configured to deliver and receive working fluid from a working chamber of a second cylinder (not shown) attached to the second head section 4002 in use.

[0185] The first head section 4001 includes a first suction valve section 2001 and a first discharge valve section 3001. Similarly, the second head section 4002 includes a second suction valve section 2002 and a second discharge valve section 3002. The first suction valve section 2001 and the second suction valve section 2002 and the first discharge valve section 3001 and the second discharge valve section 3002 are substantially the same as the suction valve section 200 and the discharge valve section 300 described previously, so for the sake of brevity, repetition of these details is omitted here.

[0186] Furthermore, as in the previously described examples, the first head section 4001 includes a first extension cup 5001 forming a first discharge channel 5101 , and the second head section 4002 includes a second extension cup 5002 forming a second discharge channel 5102 .

[0187] Exhaust channels 5101 , 5102 allow exhaust working fluid to be removed from the working chamber as previously described.

[0188] like Figure 8 As shown, a first discharge funnel 5201 and a second discharge funnel 5202 are provided, and the first discharge funnel 5201 and the second discharge funnel 5202 are configured to receive and remove the discharged working fluid from the discharge channels 5101, 5102. Optionally, in some examples, a common manifold (not shown) may be provided, and the first discharge funnel 5201 and the second discharge funnel 5202 lead to the common manifold.

[0189] Reference now Fig. 9 , for clarity, cylinder head 4000 is shown in an isometric view without a top plate or drain funnel.

[0190] Cylinder head 4000 comprises first suction channel 4000A, second suction channel 4000B, third suction channel 4000C and fourth suction channel 4000D. Although four suction channels 4000A, 4000B, 4000C, 4000D are provided in the example of current description, it should be understood that in alternative examples, any number of suction channels can be provided. Advantageously, each of suction channels 4000A, 4000B, 4000C, 4000D is used to deliver working fluid from a common suction chamber (not shown) to the first suction valve section 2001 and the second suction valve section 2002. That is to say, when working fluid is to be delivered to the first suction valve section 2001, working fluid can be sucked from the common suction chamber (not shown) by any one or all of the four suction channels 4000A, 4000B, 4000C, 4000D.

[0191] During the cyclic operation of two adjacent cylinders (not shown) supplied by working fluid from the cylinder head 4000, flow restriction can be reduced. In addition, the described arrangement can provide a greater buffer of working fluid, which in turn can reduce pressure fluctuations in the cylinder head 4000. In addition, as in Fig. 9 As can be clearly seen in the drawing, compared to the previously described arrangement, the working fluid delivered to the first suction valve section 2001 or the second suction valve section 2002 through the suction channels 4000A, 4000B, 4000C, 4000D can flow more freely to each suction valve section 2001, 2002 and between each suction valve section 2001, 2002, whereby each suction valve section is not directly open to fluid communication with another suction valve section, so that flow restriction and thus pressure fluctuations can be alleviated.

Claims

1. A valve device (100) for a piston compressor, the valve device (100) comprising: a suction valve section (200); and A discharge valve section (300); The invention is characterized in that the suction valve section (200) and the discharge valve section (300) together form a working chamber head section (1200), and The suction valve section (200) has a truncated pyramidal form.

2. The valve device (100) according to claim 1, wherein: The suction valve section (200) comprises at least a first self-actuated check valve (231).

3. The valve device (100) according to claim 2, wherein: The truncated pyramidal form of the suction valve section (200) includes a plurality of side surfaces (210), wherein the first self-actuated check valve (231) is located on a first side surface (211) of the plurality of side surfaces (210) of the suction valve section (200).

4. The valve device (100) according to claim 2 or 3, wherein: The first self-actuated check valve (231) comprises a first reed suction valve (231).

5. The valve device (100) according to claim 4, wherein: The suction valve section (200) includes at least a first suction port (221) configured to provide fluid communication through the suction valve section (200); and The first reed suction valve (231) comprises at least a first finger-like blade (231'), and the first finger-like blade (231') is arranged to open and close the first suction port (221).

6. The valve device (100) according to claim 5, wherein: The suction valve section (200) includes a second suction port (222) configured to provide fluid communication through the suction valve section (200); and The first finger-like blade (231') is arranged to open and close the second suction port (222).

7. The valve device (100) according to claim 5, wherein: The suction valve section (200) includes a second suction port (224) configured to provide fluid communication through the suction valve section (200); and The first reed suction valve (231) includes a second finger-like blade (231"), and the second finger-like blade (231") is arranged to open and close the second suction port (224).

8. The valve device (100) according to claim 7, wherein: The first finger-shaped blade (231') and the second finger-shaped blade (231") are integrated.

9. The valve device (100) according to claim 7, wherein: The first finger-shaped blade (231') and the second finger-shaped blade (231") are non-integral.

10. The valve device (100) according to any one of claims 5 to 9, further comprising a first finger-shaped stopper (231'A), wherein the first finger-shaped stopper (231'A) is configured to prevent movement of the first finger-shaped blade (231'1).

11. The valve device (100) according to any one of claims 5 to 10, further comprising a second finger-like stop, wherein the second finger-like stop is configured to prevent movement of the second finger-like blade (231 ").

12. The valve device (100) according to any one of claims 5 to 9, wherein: The discharge valve section (300) includes a first discharge port (321) configured to provide fluid communication through the discharge valve section (300) and to prevent movement of the first finger blade (231').

13. The valve device (100) according to any of claims 7 to 9, wherein: The discharge valve section (300) includes a second discharge port (322) configured to provide fluid communication through the discharge valve section (300) and prevent movement of the first finger-like blade (231') and / or the second finger-like blade (231").

14. The valve device (100) according to claim 3 or any one of claims 4 to 13 when dependent on claim 3, further comprising a second self-actuated check valve, wherein the second self-actuated check valve is located on a second side (212) of the multiple side surfaces (210) of the suction valve section (200).

15. The valve device (100) according to claim 14, wherein: The second self-actuated check valve includes a second reed suction valve.

16. The valve device (100) according to claim 15, wherein: The suction valve section (200) includes at least a third suction port, the third suction port being configured to provide fluid communication through the suction valve section (200); as well as The second reed suction valve comprises at least a third finger-like blade arranged to open and close the third suction port.

17. The valve device (100) according to claim 16, wherein: The suction valve section (200) includes a fourth suction port configured to provide fluid communication through the suction valve section (200); and The third finger-like blade is arranged to open and close the fourth suction port.

18. The valve device (100) according to claim 16, wherein: The suction valve section (200) includes a fourth suction port configured to provide fluid communication through the suction valve section (200); and The second reed suction valve includes a fourth finger-like blade arranged to open and close the fourth suction port.

19. The valve device (100) according to claim 18, wherein: The first finger-shaped blade and the second finger-shaped blade are integral.

20. The valve device (100) according to claim 18, wherein: The first finger-shaped blade and the second finger-shaped blade are non-integral.

21. The valve device (100) according to any of the preceding claims, wherein: The valve device (100) has a central axis, which is configured to be aligned with the longitudinal axis (Le) of the cylinder (401) of the piston compressor in use, The discharge valve section (300) is configured to be perpendicular to the central axis, so that in use, the discharge valve section (300) is at 90 degrees or approximately 90 degrees to the longitudinal axis (Le) of the cylinder (401).

22. A valve device (100) for a piston compressor, the valve device (100) comprising: a suction valve section (200); and A discharge valve section (300); The invention is characterized in that the suction valve section (200) and the discharge valve section (300) together form a working chamber head section (1200), and The suction valve section (200) has a generally frustoconical form including at least a first flat side surface.

23. The valve device (100) according to claim 22, wherein: The suction valve section (200) comprises at least a first self-actuated check valve (231), which is located on the first flat side surface (211).

24. The valve device (100) according to any of claims 22 or 23, wherein: The first self-actuated check valve (231) comprises a first reed suction valve (231).

25. The valve device (100) according to claim 24, wherein: The suction valve section (200) includes at least a first suction port (221) configured to provide fluid communication through the suction valve section (200); and The first reed suction valve (231) comprises at least a first finger-like blade (231'), and the first finger-like blade (231') is arranged to open and close the first suction port (221).

26. The valve device (100) according to claim 25, further comprising a first finger-like stopper (231'A), the first finger-like stopper (231'A) being configured to prevent movement of the first finger-like blade (231').

27. The valve device (100) according to claim 25 or 26, wherein: The discharge valve section (300) includes a first discharge port (321) configured to provide fluid communication through the discharge valve section (300) and to prevent movement of the first finger blade (231').

28. The valve device (100) according to any of claims 22 to 27, wherein: The valve device (100) has a central axis, which is configured to be aligned with the longitudinal axis (Le) of the cylinder (401) of the piston compressor in use, The discharge valve section (300) is configured to be perpendicular to the central axis, so that in use, the discharge valve section (300) is at 90 degrees or approximately 90 degrees to the longitudinal axis of the cylinder (401).

29. A valve device (100) for a piston compressor, the valve device (100) comprising: a suction valve section (200); and a discharge valve section (300), the discharge valve section (300) having a truncated pyramidal form; The invention is characterized in that the suction valve section (200) and the discharge valve section (300) together form a working chamber head section (1200).

30. A valve device (100) for a piston compressor, the valve device (100) comprising: a suction valve section (200); and a discharge valve section (300) having a substantially frustoconical form including at least a first flat side surface (211); The invention is characterized in that the suction valve section (200) and the discharge valve section (300) together form a working chamber head section (1200).

31. A piston compressor comprising: A cylinder (401), the cylinder (401) comprising a longitudinal axis (Le); a piston mounted in the cylinder (401) and linearly movable along the longitudinal axis (Le); as well as A valve device (100) according to any of claims 1 to 30.

32. The piston compressor according to claim 31, wherein: The piston includes a piston head section that matches the working chamber head section (1200).

33. A method of optimizing fluid flow through a valve device (100), comprising the steps of: a. Providing a valve device (100) according to any one of claims 1 to 30; b. sucking in a working fluid through the suction valve section (200); and c. Discharge the working fluid through the discharge valve section (300).

34. A method of operating a piston compressor, comprising the steps of: a. Providing a piston compressor according to any of claims 31 or 32; b. sucking the working fluid into the cylinder (401) through the suction valve section (200); c. compressing the working fluid by linearly moving the piston along the longitudinal axis (Le); as well as d. Expelling the working fluid from the cylinder (401) through the discharge valve section (300).

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