Apparatus for compressing gaseous fluid and method for operating the same

Abstract

The object of the present invention is to provide an apparatus for compressing a gas phase fluid, and to operate said apparatus with maximum safety, thereby preventing electrical voltages from being generated within the apparatus and being applied from said apparatus to the electrical system of a motor vehicle when the electric drive operation of said apparatus is stopped. The present invention relates to a device (1) for compressing a gaseous fluid, in particular a refrigerant in a refrigerant circuit, in particular in an air conditioning system of a motor vehicle, the device (1) comprising a housing (2), a compression mechanism (3) for compressing the gaseous fluid, and an electric motor (4) for driving the compression mechanism (3). The housing (2) includes a suction pressure chamber (11) and a high pressure chamber (12).

Description

Technical Field

[0001] The present invention relates to an apparatus for compressing a vapor-phase fluid and a method for operating the same, and more particularly, to an apparatus for compressing a vapor-phase fluid, particularly a refrigerant in a refrigerant circuit, for use in a vehicle air conditioning system, and a method for operating the apparatus.

Background Art

[0002] Conventionally known compressors for vehicles, particularly for vehicle air conditioning systems, for supplying refrigerant through a refrigerant circuit, are also called refrigerant compressors and are often formed as piston compressors having a variable stroke volume regardless of the refrigerant, or scroll compressors. The compressor is driven by a pulley or electrically.

[0003] A conventional electric-driven scroll compressor is designed to include an electric motor disposed within a housing and a compression mechanism mechanically connected to the electric motor.

[0004] The compression mechanism of a scroll compressor has a disk-shaped base plate, a fixed scroll having a spiral wall extending from the base plate, and a orbiting scroll having a disk-shaped base plate and a spiral wall extending from the base plate. The fixed scroll and the orbiting scroll, also called an orbiting spiral, interact. The base plates are arranged relative to each other such that the spiral walls coincide with each other. The spiral walls form a continuous closed working chamber.

[0005] The orbiting scroll moves in a circular path via an eccentric connected to a drive shaft such that the orbiting scroll orbits around the fixed spiral wall of the fixed scroll. The working chamber is formed small, and the fluid is compressed by the opposing movement of the two overlapping spiral walls. The vapor-phase fluid to be compressed is sucked into the compression mechanism, compressed within the compression mechanism, and discharged from the discharge port.

[0006] An electric motor has a stator having a substantially cylindrical stator core, coils wound around the stator core, and a rotor located inside the stator. The rotor is coaxially positioned within the stator so as to be rotatable with respect to the axis of rotation and is set to rotate when electrical energy is applied to the coils of the stator. A drive shaft, which is connected to an orbital scroll of a compression mechanism on one side and drives the orbital scroll to compress a water vapor fluid, is designed to be either integrally formed with the rotor or formed on the other side as a separate component of the electric motor.

[0007] Using a compression mechanism driven by an electric motor, under certain circumstances after the end of operation, such as an unintended interruption of the supply of electrical energy to the electric motor due to an intended switch-off or a particular event, an undesirable electrical voltage can be induced in the electric motor. In this case, the electric motor temporarily operates as a generator.

[0008] When the electric motor is switched off, a possible cause of operation deviating from compressor mode is the fluid passing through the compression mechanism that drives the compression mechanism. Therefore, the compression mechanism is driven not by the electric motor, but by the fluid passing through it. During normal operation of the compressor in compressor mode, the fluids in a vehicle's air conditioning system, particularly the refrigerant in the refrigerant circuit, are compressed from low-pressure levels to high-pressure levels as they pass through the compression mechanism.

[0009] Mass flow rates of refrigerant generated during compressor operation that deviates from the compressor mode operation when the electric motor is switched off can be caused by refrigerant detaching from the refrigerant circuit, which includes the compressor as a component. Mass flow rates of refrigerant passing through the compressor can cause movement of the compression mechanism, particularly the orbital scroll connected to the drive shaft, and thus the movement of the magnetic rotor relative to the stator of the electric motor. As a result, an electrical voltage may be induced inside the coils of the electric motor's stator. To prevent such voltage induction exceeding a set threshold, the entire air conditioning system, especially the refrigerant circuit including the compressor, needs to be protected.

[0010] Solutions based on the electric drive aspect are known from prior art and can improve the operational safety of the compressor by preventing or at least limiting the induction of voltage within the coil of the electric motor caused by the movement of the compression mechanism after the electric motor is switched off. However, electrical circuits for such active or passive discharges are expensive to manufacture and maintain and require considerable effort for verification and documentation.

[0011] Patent Document 1 discloses a fluidizing device having a scroll-type expansion device that operates using a high-pressure refrigerant. The refrigerant is heated using waste heat from a vehicle engine. The fluidizing device also has a motor generator for generating electrical energy. The motor generator is driven using the rotational force provided by the expansion device, and the rotating shaft of the motor generator is coupled to the orbiting scroll of the expansion device. [Prior art documents] [Patent Documents]

[0012] [Patent Document 1] U.S. Patent Application Publication No. 2006 / 0254309 [Overview of the project] [Problems that the invention aims to solve]

[0013] The object of the present invention is to provide a device for compressing a gaseous fluid and to ensure that the device operates with maximum safety. In particular, it is to prevent electrical voltage from being generated inside the device and applied from the device to the electrical system of a motor vehicle when the device's electric drive operation stops. The device is intended to have a simple design that meets minimum space requirements and the minimum number of components. Furthermore, the costs of production, maintenance, assembly, and operation must be minimized. [Means for solving the problem]

[0014] The aforementioned objective is achieved by a subject having the characteristics of an independent term. An example of improvement is explicitly shown in the dependent term.

[0015] The aforementioned objective is achieved by an apparatus according to the present invention for compressing a gaseous fluid, particularly a refrigerant in a refrigerant circuit, especially a refrigerant in a refrigerant circuit of an air conditioning system in a motor vehicle. The apparatus comprises a housing, a compression mechanism for compressing the gaseous fluid, and an electric motor for driving the compression mechanism. The housing is formed including an intake pressure chamber and a high-pressure chamber.

[0016] According to the design of the present invention, a device for compressing a gaseous fluid has a bypass channel and a fluid flow control device that passes through the bypass channel. The bypass channel is specifically designed solely for the fluidic connection of the suction pressure chamber and the high-pressure chamber to each other. The fluid flow control device ensures that the fluid flows in the flow direction from the suction pressure chamber motor to the high-pressure chamber motor, depending on the respective pressure levels of the fluid in the suction pressure chamber motor and the high-pressure chamber motor. bypass It is designed solely to open the flow path. The fluid diversion control device is preferably mechanically actuated only by different pressure levels and the pressure difference between those pressure levels.

[0017] Therefore, a device for compressing a gaseous fluid opens and closes a bypass channel from the original suction side to the pressure side in a pressure-dependent manner. The bypass channel is opened only when the fluid pressure in the suction pressure chamber is higher than the pressure in the high-pressure chamber. If the fluid pressure in the suction chamber is equal to or lower than the fluid pressure in the high-pressure chamber, the bypass channel remains closed.

[0018] bypass The fluid flow control device for the fluid flowing through the channel uses valves, especially when necessary, to direct the fluid flow from the suction pressure chamber to the high-pressure chamber. bypass Open the flow path and direct the flow from the high-pressure chamber to the suction pressure chamber. bypass It is advantageously designed as a backflow prevention valve that keeps the flow path closed at all times.

[0019] The gas-phase fluid compression device is preferably designed as an electrically driven refrigerant compressor.

[0020] According to a modification of the present invention, the compression mechanism of the gas-phase fluid compression device includes a fixed screw and a rotating spiral as components of a scroll compressor. The fixed or immovable screw and the rotating spiral are designed with a base plate and a threaded wall extending from the base plate, respectively. The walls are arranged to engage with each other to form a processing chamber.

[0021] The flow direction of the fluid through the compression mechanism is restricted from flowing in a specific direction, particularly from the suction side to the pressure side, using the provided components. When the pressure on the pressure side is higher than the pressure on the suction side, reverse flow of the fluid through the pipe through the compression mechanism is prevented.

[0022] According to the present invention, the electric motor has a stator and a rotor, and the rotor is arranged inside the stator. The stator is designed to include coils to generate an electromagnetic field, and serves to drive the rotor. In particular, it is arranged coaxially inside the stator and rotatably with respect to the rotation axis.

[0023] The rotor has a drive shaft or can be connected to a drive shaft, and the drive shaft is arranged rotatably with respect to the rotation axis. Further, the drive shaft is preferably mechanically connected to the rotating spiral of the compression mechanism of the scroll compressor.

[0024] The bypass flow path can be formed at an appropriate location inside or outside the gas-phase fluid compression device, near both the high-pressure region and the low-pressure region of the device.

[0025] According to the present invention, the bypass flow path is formed inside the fixed scroll, inside the wall of the housing, or outside the housing. When the bypass flow path is arranged inside the fixed scroll of the compression mechanism of the scroll compressor, the bypass flow path is designed as a through-opening penetrating the base plate of the fixed scroll, in particular.

[0026] bypassA fluid flow control device for fluids passing through a flow path can be designed with any type of pressure-dependent opening mechanism, such as valves or lamellae.

[0027] According to the present invention, the device for controlling the flow of fluid through a bypass channel is designed with a lamellar valve.

[0028] In the closed position, the lamellar valve supports the surface of the base plate of the fixed scroll facing the high-pressure chamber, thereby closing the bypass channel.

[0029] Lamella valve type devices for controlling the flow of fluid through pipes preferably have fastening and closing regions connected to each other via neck-type connecting regions. Similar to lamella valve type devices, at least one outlet valve of a lamella valve type can be connected to each other at first ends that form fastening regions to form an integrated unit. The lamella valve type devices and at least one outlet valve are preferably oriented toward a common plane.

[0030] According to the present invention, a lamellar valve type device for pipe flow control is fixed at the first end with a base plate of fixing screws in a fastening region. The pipe flow control device is formed from the first end to the end and utilizes a free second end having a closed region. bypass It is positioned so that the flow path can be closed.

[0031] It is advantageous that the connection region of the pipe flow control device is formed over a length having a constant width that is substantially smaller than the diameter of the circular closed region. The connection region can have a constant outer diameter so that the connection region is designed with a circular ring-shaped cross-section.

[0032] The outer diameter of the connection region preferably matches the value obtained by subtracting the distance required for relative motion with respect to the fixed scroll from the inner diameter of the annular rise that protrudes from the surface of the base plate of the fixed scroll facing the high-pressure chamber.

[0033] The ratio of the width of the connection area to the longitudinal extension of the pipe flow control device is favorably 0.1. The ratio of the longitudinal extension to the radius of the connection area of ​​the pipe flow control device is particularly favorably within the range of 0.1 to 10.

[0034] According to another embodiment, a fluid pipe flow control device includes a closure member and a spring member. The spring member is oriented to apply a spring force to the closure member to block the bypass flow. The closure member may have a hemispherical or circular truncated cone shape. The spring member may be designed as a cylindrical spiral spring or a spring plate.

[0035] Furthermore, the object of the present invention is achieved by a method for operating a gas-phase fluid compressor that includes a housing comprising an intake pressure chamber and a high-pressure chamber, a bypass channel connecting the intake pressure chamber and the high-pressure chamber to each other in a fluid flow manner, and a fluid flow control device for the fluid passing through the bypass channel. The method comprises the following steps

[0036] - The step of closing the bypass passage while the gas phase fluid compressor is operating in compressor mode, and

[0037] - The fluid is to flow through in the direction of flow from the suction pressure chamber to the inside of the high-pressure chamber. bypass The stage of opening the flow path

[0038] The direction of fluid flow is always determined by the fluid pressure levels in the suction pressure chamber and the high-pressure chamber.

[0039] This method ensures that the operationally stopped compression mechanism does not move unintentionally or be actuated by fluid passing through it. Since the fluid flows through a bypass channel instead of the compression mechanism, the compression mechanism, particularly the swirling spiral, is not set to rotate, and if it were set to rotate, it could be transmitted through the drive shaft to the rotor of an electric motor, potentially inducing undesirable high voltages in the stator coils. To prevent undesirable high voltages from being induced in the stator coils of an electric motor via a rotor designed to move, at least a small mass flow of fluid flows through the compression mechanism.

[0040] In particular, with respect to the minimum number of components for minimum space requirements, an advantageous embodiment of the present invention enables the use of a gas-phase fluid compressor in the refrigerant circuit of an air conditioning system for a motor vehicle.

[0041] The gas-phase fluid compressor can be advantageously used with a variety of refrigerants, including R134a, R1234yf, R1234ze, R744, R600a, R290, R152a, and R32.

[0042] In summary, the gas phase fluid compressor according to the present invention is advantageous in that it is constructed with a simple design that requires minimal costs for manufacturing, assembly, and operation. [Brief explanation of the drawing]

[0043] Details, features, and advantages of embodiments of the present invention are described below in the description of preferred embodiments. The drawings are as follows.

[0044] [Figure 1a] This shows a cross-section of an electrically driven compressor having an electric motor as a device for driving a compression mechanism having a bypass flow path between the suction pressure chamber and the high-pressure chamber. [Figure 1b] Figure 1a shows a detailed cross-sectional view of the compression mechanism of the compressor. [Figure 2a]This is a cross-sectional view of a bypass channel formed within the base plate of a fixed scroll of a compression mechanism formed between an intake pressure chamber and a high-pressure chamber, which have a pipe flow control device according to a first alternative embodiment. [Figure 2b] This figure shows a view from above of the pipe flow control device of the first alternative embodiment shown in Figure 2a. [Figure 2c] This figure shows a view from above of the pipe flow control device of the first alternative embodiment shown in Figure 2a. [Figure 2d] This is a cross-sectional view of a bypass channel formed between the suction pressure chamber and the high-pressure chamber, which have a pipe flow control device according to the embodiment shown in Figure 2c. [Figure 3a] This is a detailed view from above of a bypass channel formed inside the base plate of a fixing screw of a compression mechanism with a pipe flow control device. [Figure 3b] Figure 2a is a detailed cross-sectional view showing the open / closed state of a bypass channel formed inside the base plate of a fixed scroll in a compression mechanism with a pipe flow control device. [Figure 3c] Figure 2a is a detailed cross-sectional view showing the open / closed state of a bypass channel formed inside the base plate of a fixed scroll in a compression mechanism with a pipe flow control device. [Figure 4] This is a cross-sectional view showing a pipe flow control device according to a second alternative embodiment. [Modes for carrying out the invention]

[0045] Figure 1a shows a cross-section of an electric drive device (1) for compressing a gaseous fluid, including an electric motor (4) located in a housing (2) as a device for driving a compression mechanism (3) for drawing in, compressing, and discharging a gaseous fluid refrigerant. The device will hereafter be named compressor (1). The electric motor (4) supplies electrical energy. Figure 1b shows a detailed cross-section of the compression mechanism (3) of compressor 1 in Figure 1a.

[0046] The electric motor (4) has a stator (4b) having a substantially hollow cylindrical stator core, coils wound around the stator core, and a rotor (4a) disposed inside the stator (4b). The rotor (4a) is configured to rotate when electrical energy is supplied to the coils of the stator (4b). The rotor (4a) is coaxially positioned inside the stator (4b) and rotatable with respect to a rotation shaft (5). The drive shaft (6) may be formed integrally with the rotor (4a) or as a separate component.

[0047] The formed compression mechanism, which includes an electric motor (4) and a fixed scroll (3a) and a revolving spiral (3b), is located within a volume enclosed by a housing (2). The housing (2) includes a first housing member (2a) for housing the compression mechanism (3) and a second housing member (2b), which is preferably made of metal, particularly aluminum, for housing the electric motor (4).

[0048] The swirling spiral (3b) of the compression mechanism (3), in which a vapor fluid, particularly a refrigerant, is compressed, is driven via a drive shaft (6) connected to the rotor (4a) of an electric motor (4).

[0049] The fixed scroll (3a) and the orbiting spiral (3b) each have base plates (3a-2, 3b-2) and helical walls (3a-1, 3b-1) extending from the base plates (3a-2, 3b-2). The base plates (3a-2, 3b-2) are positioned relative to each other such that the helical walls (3a-1, 3b-1) coincide with each other. The fixed scroll (3a) is formed within or as part of the housing (2). The orbiting spiral (3b) is coupled to a drive shaft (6) that rotates relative to a rotation axis via an eccentric portion (7) and is guided along a circular path. The drive shaft (6) is supported in the housing (2) using radial bearings (8a, 8b). The orbiting spiral (3b) is held in place by the drive shaft (6), particularly by radial bearings (9) located above the eccentric portion (7).

[0050] When the revolving spiral (3b) moves relative to the fixed scroll (3a), the helical walls (3a-1, 3b-1) of the fixed scroll (3a) and the revolving spiral (3b) come into contact with each other at multiple points, forming a continuous, closed machining chamber (10) within the helical walls (3a-1, 3b-1). The adjacent machining chambers (10) each define a range of different volume sizes. As a result of the relative movement of the revolving spiral (3b) with respect to the fixed scroll (3a), the volume and position of the machining chambers (10) change. The volume of the machining chambers (10) gradually decreases towards the center of the helical walls (3a-1, 3b-1).

[0051] The gaseous fluid to be compressed, particularly the gaseous refrigerant, passes through a suction chamber, also called the suction pressure chamber (11), is drawn into the processing space (10) by the pressure of the refrigerant, is compressed by its relative motion with respect to the stationary scroll (3a), and is released into a discharge chamber, also called the high-pressure chamber (12), by the pressure of the refrigerant. At the high-pressure level of the refrigerant circuit, the refrigerant present in the high-pressure chamber (12) is sent outside the compressor (1) and into the refrigerant circuit. The bypass passage (13) is located inside the fixed scroll (3a). The bypass passage (13) is designed as a through-opening and extends through the base plate (3a-2) of the fixed scroll (3a) to connect the intake chamber (11) of the compressor (1) to the high-pressure chamber (12). During operation of the compressor (1) in compressor mode and during normal operation of the compressor (1) thereafter, the bypass passage (13) is closed by the bypass flow control device (14-1), as shown in Figures 1a and 1b.

[0052] The pipe flow control device (14-1) is designed as a backflow prevention valve that allows fluid to flow through the bypass channel (13) in only one fluid flow direction, from the suction pressure chamber (11) to the high-pressure chamber (12), and prevents fluid flow in the reverse direction from the high-pressure chamber (12) into the suction pressure chamber (11). The device (14-1) is open while there is flow through the bypass channel (13) from the suction pressure chamber (11) to the high-pressure chamber (12). In particular, while the compressor (1) is operating in compressor mode, it is impossible for there to flow through the bypass channel (13) from the suction pressure chamber (11) to the high-pressure chamber (12).

[0053] Figure 2a shows the inside of the base plate (3a-2) of the fixed scroll (3a) of the compression mechanism (3) formed between the suction pressure chamber (11) and the high-pressure chamber (12), which has a pipe flow control device (14-1) according to the first alternative embodiment. bypass Figure 2b and Figure 2c show a cross-section of the flow path (13). Figures 2b and 2c show a top view of the pipe flow control device (14-1) of the first alternative embodiment according to Figure 2a, respectively. Figure 2d further shows the pipe flow control device (14-1) of the embodiment according to Figure 2c, formed between the suction pressure chamber (11) and the high-pressure chamber (12). bypass A cross-section of the channel (13) is shown.

[0054] The lamellar valve type device (14-1) is positioned on the upper surface of the base plate (3a-2) of the fixed scroll (3a) facing the high-pressure chamber (12) and closes the bypass passage (13). While the compressor (1) is operating in compressor mode, the lamellar valve, acting as a backflow prevention valve, prevents the compressed fluid discharged from the processing chamber (10) at high pressure (HP) levels and toward the high-pressure chamber (12) from flowing back into the suction pressure chamber (11). In the end region facing the high-pressure chamber (12), the bypass passage (13) is designed as a closed opening (13-1) oriented axially, particularly toward the rotation axis (5).

[0055] The perforated plate-shaped device (14-1) has a finger-like shape and is fixed to the base plate (3a-2) of the fixed scroll (3a), particularly the fixed scroll (3a) of the compression mechanism (3), within a region at the first end, also called the fastening region (14-1a). The plate supports the base plate (3a-2) with its surface facing the high-pressure chamber (12) and is fixed to the base plate (3a-2) within the fastening region (14-1a). At the second end formed from the first end to the terminal, the device (14-1) has a closing region (14-1b) in the form of a through-opening for closing the end of the bypass channel (13). The ends of the device (14-1) are connected to each other via a neck-shaped connecting region (14-1c). The connecting region (14-1c) is designed to be substantially narrower than the closing region (14-1b), so that the device (14-1) has a spoon-shaped shape when viewed from above.

[0056] The connection area (14-1c) is designed with a constant width (B) and a constant radius (R) in the longitudinal direction, and therefore the connection device (14-1c) of the device (14-1) is designed with a circular ring cross-section. The outer diameter (R) of the connection area (14-1c) substantially coincides with the inner diameter of the circular ring-shaped riser (3a-3) of the fixed scroll (3a). The riser (3a-3) is designed as a wall that protrudes from the surface of the base plate (3a-2) facing the high-pressure chamber (12) and has an inner diameter (D4) of the side facing inward. The space for moving the device (14-1) is provided between the outer diameter (R) of the connection area (14-1c) and the inner diameter or inner diameter (D4) of the riser (3a-3).

[0057] The apparatus (14-1) in the embodiment shown in Figure 2b is designed as a single component, while the apparatus (14-1) in the embodiment shown in Figure 2c is connected at the fastening region (14-1a) to another valve, such as an outlet valve similarly designed with lamellae. The valve and apparatus (14-1) are designed as a combined component, also called an integrated component or composite material.

[0058] Figures 2c and 2d show, in one embodiment, the ratio of the dimensions of the bypass channel (13) formed in the base plate (3a-2) and the device (14-1) that closes the bypass channel (13). According to other embodiments, the ratio may vary in the range of 0.1 to 10 due to various factors.

[0059] The first ratio of the diameter (D1) of the closed region (14-1b) of the device (14-1) to the diameter (D2) of the closed opening (13-1) of the axially oriented bypass channel (13) is in the range of 1.25 to 1.75, which ensures the sealing function of the device (14-1).

[0060] bypass The diameter (D3) of the flow path (13) bypass The second ratio to the length (L) of the flow path (13) is greater than 0.25. Therefore, the fluid bypass By flowing through the passage (13), it is possible to reduce the pressure inside the suction pressure chamber (11) without rotating the compression mechanism (3) of the compressor (1).

[0061] The third ratio of the closing opening (13-1) of the bypass channel (13) to the channel diameter (D3) of the bypass channel (13) is in the range of 1.05 to 2.1. In an alternative embodiment having an axially extending bypass channel (13) without a closing opening (13-1), the ratio of the diameter (D1) of the closing region (14-1b) of the device (14-1) to the channel diameter (D3) of the bypass channel (13) is in the range of 1.25 to 1.75. Also, the second ratio of the channel diameter (D3) of the bypass channel (13) to the length (L) of the bypass channel (13) is greater than 0.25.

[0062] The longitudinal extension (A) of the device (14-1) depends on the position of the bypass channel (13) in the base plate (3a-2) of the fixed scroll (3a). The width (B) of the connection region (14-1c) has a ratio of 0.1 to the longitudinal extension (A). The device (14-1) has a curvature of radius (R) that has a ratio of 0.5 to diameter (D4). In other embodiments, the ratio of the longitudinal extension (A) to radius (R) of the device (14-1) is in the range of 0.1 to 10. In particular, if the device (14-1) is designed to be straight in the connection region (14-1c) and has an infinite radius (R), the ratio of radius (R) to diameter (D4) is in the range of 0.3 to infinity.

[0063] In an alternative linear design of the device (14-1), the ratio of the width (B) of the connection region (14-1c) to the longitudinal extension (A) is preferably 0.2.

[0064] The compressed refrigerant in the high-pressure chamber (12) is at the high-pressure (HP) level, while the refrigerant in the suction pressure chamber (11) and bypass passage (13) is at the low-pressure (LP) level in the suction state. Therefore, the lamellar device (14-1) is pressurized on the surface of the base plate (3a-2) due to the pressure difference. The pressure at the high-pressure (HP) level is greater than the pressure at the low-pressure (LP) level.

[0065] Figure 3a shows the inside of the base plate (3a-2) of the fixed scroll (3a) of the compression mechanism (3) having the device (14-1) bypass A detailed view of the flow path (13) from above is shown. Figures 3b and 3c show the interior of the base plate (3a-2) of the fixed scroll (3a) of the compression mechanism (3) having the pipe flow control device (14-1) as shown in Figure 2a. bypass This is a detailed cross-sectional view showing the open and closed states of the flow path.

[0066] Figure 3b is a schematic diagram showing the operation of the compressor (1) in compressor mode and the arrangement of the device (14-1) in Figure 2a. The refrigerant compressed in the high-pressure chamber (12) at high pressure (HP) pressurizes the lamellar valve type device (14-1) against the surface of the base plate (3a-2), thus closing the bypass passage (13). The refrigerant prevents the internal refrigerant from flowing back from the high-pressure chamber (12) through the bypass passage (13) into the low-pressure (LP) level suction pressure chamber (11).

[0067] Figure 3c shows the operation of the compressor (1) outside of compressor mode, with the electric motor (4) off and the refrigerant flowing by mass in the direction of flow (15) through the bypass passage (13). The bypass passage (13) is open. The device (14-1) is separated from the surface of the base plate (3a-2) of the fixed scroll (3a). An open gap is formed between the surface of the base plate (3a-2) of the fixed scroll (3a) and the device (14-1).

[0068] In contrast to the operation of the compressor (1) in compressor mode, the refrigerant in the suction pressure chamber (11) has a higher pressure than the refrigerant in the high-pressure chamber (12), so the refrigerant pushes the lamellar valve device (14-1) away from the surface of the base plate (3a-2), thus opening the bypass passage (13). Due to their respective different pressure levels, the refrigerant passes through the bypass passage (13) and flows from the suction pressure chamber (11) into the high-pressure chamber (12).

[0069] Such pressure conditions within the compressor (1) can occur, for example, when the operation of the electric motor (4) stops due to an intentional switch-off, particularly an unintended interruption of the electrical energy supply to the electric motor (4) due to an accident. When the rotor (4a) of the electric motor (4) is driven and moved inside the stator (4b) by the compression mechanism (3), and this induces an electrical voltage in the coils of the stator (4b), causing a voltage to be applied to the electrical system of the motor vehicle, for example, when the compressor (1) is operating in compressor mode, and during the driving process of the compression mechanism (3), at least a portion of the mass flow of refrigerant is redirected in the flow direction (15) that passes through the bypass flow path (13), and as a result toward the periphery of the compression mechanism (3), in order to prevent the flow of refrigerant from completely passing through the compression mechanism (3). This prevents the voltage induced in the coils of the stator (4b) of the electric motor (4) from exceeding a certain threshold.

[0070] The bypass passage (13) is formed at a suitable location inside or outside the compressor (1) and connects the intake chamber (11) to the high-pressure chamber (12). The bypass passage (13) may have any type of pressure-dependent opening mechanism, such as a valve or a lamellar type, for opening and closing.

[0071] Figure 4 is a cross-sectional view of the pipe flow control device (14-2) according to a second alternative embodiment during the operation of the compressor (1) in compressor mode. The device (14-2), designed with a backflow prevention valve, is closed. The refrigerant pressure in the high-pressure chamber (12) is greater than the refrigerant pressure in the intake chamber (11).

[0072] The device (14-2) has a ball-shaped closing member (16) and a spring member (17). The spring member (17) is designed as a cylindrical spiral spring. The bypass channel (13) is closed via the ball-shaped closing member (16). The spring force of the spring member (17) acts on the upper part of the closing member (16) to close the bypass channel (13).

[0073] When the refrigerant pressure level inside the suction pressure chamber (11) rises relative to the refrigerant pressure level inside the high-pressure chamber (12), the closing member (16) is pressurized in the opposite direction, towards the high-pressure chamber (12), by the spring force of the spring member (17). The closing member (16) pressurizes the refrigerant in the direction of the high-pressure chamber (12). bypass To allow passage through the channel (13), bypass The flow path (13) is not blocked. When the refrigerant pressure level in the suction pressure chamber (11) is too low relative to the refrigerant pressure level in the high-pressure chamber (12), the closing member (16) is pressurized by the spring member (17) toward the suction pressure chamber (11) in order to close the bypass flow path (13). For example, the bypass flow path (13) may be formed within the wall of the housing (2) or inside another component located between the suction pressure chamber (11) and the high-pressure chamber (12), such as the base plate (3a-2) of the fixed scroll (3a).

[0074] Alternatively, the closing member may have a truncated cone shape. The truncated cone closing member has a cone cross-section, including a bottom surface and a top surface, and the bottom and top surfaces are parallel to each other. In the closed state, the inclined side surface of the closing member supports the projection formed in the bypass channel (13). The spring force applied by the spring member (17) in the closed state bypass The closing member acts on the bottom surface with its side surface in opposition to the protrusion formed in the flow path (13).

[0075] Furthermore, the spring member can also be designed with a spring plate instead of a cylindrical spiral spring. The spring plate can be combined with both a ball-shaped closing member (16) and a truncated cone-shaped closing member.

[0076] The pipe flow control device that penetrates the bypass channel (13) can also be designed in any form of a backflow prevention valve. [Explanation of symbols]

[0077] 1. Gear, compressor 2 Housing 2a First housing member 2b Second housing member 3 Compression mechanism 3a Fixed scroll 3a-1 Wall surface of fixed scroll (3a) 3a-2 Base plate for fixed scroll (3a) 3a-3 Upper part of fixed scroll (3a) 3b Swirling Spiral 3b-1 Swirling Spiral (3b) Wall 3b-2 Swivel spiral (3b) base plate 4 Electric motor 4a Rotor 4b Stator 5. Rotation axis 6 Drive shaft 7 Eccentricity 8a, 8b Radial bearings of the drive shaft (6) at the top of the housing (2) 9. Radial bearing of the orbital scroll (3b) above the drive shaft (6). 10. Processing Chamber 11. Intake pressure chamber 12. High-pressure chamber 13 Bypass flow road 13-1 Closed opening 14-1, 14-2 Pipe flow control device 14-1a Fastening area 14-1b Closed area 14-1c Neck type Connection area 15 Flow direction 16 Closing member 17 Spring component HP High Pressure LP Low Voltage A. Vertical extension B Width of the connection area (14-1c) D1 Diameter of closed region (14-1b) D2 Diameter of closed opening (13-1) D3 bypass Diameter of the channel (13) D4 Diameter of the rising section (3a-3) L bypass Length of channel (13) R radius

Claims

1. The apparatus (1) for compressing a gaseous fluid includes a compression mechanism (3) for compressing the gaseous fluid and an electric motor (4) for driving the compression mechanism (3), the housing (2) is formed including an intake pressure chamber (11) and a high-pressure chamber (12), and a pipe flow control device (14-1) for the gaseous fluid is formed through a bypass passage (13), the bypass passage (13) is designed to fluidly connect the intake pressure chamber (11) and the high-pressure chamber (12) to each other, and the pipe flow control device (14-1) is designed to open the bypass passage (13) so that the gaseous fluid flows only in the flow direction from the intake pressure chamber (11) to the high-pressure chamber (12), depending on the corresponding pressure levels of the gaseous fluid in the intake pressure chamber (11) and the high-pressure chamber (12). The housing (2) includes a first housing member (2a) for housing the compression mechanism (3) and a second housing member (2b) for housing the electric motor (4). The apparatus is characterized in that the suction pressure chamber (11) is located between the first housing member (2a) and the second housing member (2b).

2. The apparatus according to claim 1, characterized in that the pipe flow control device (14-1) is designed with a lamellar valve.

3. The apparatus according to claim 1, wherein the compression mechanism (3) comprises a fixed scroll (3a) and a revolving spiral (3b), and the fixed scroll (3a) and the revolving spiral (3b) are each formed including a base plate (3a-2, 3b-2) and a helical wall (3a-1, 3b-1) extending from the base plate (3a-2, 3b-2), and the helical walls (3a-1, 3b-1) are arranged to fit together to form a processing chamber (10).

4. The apparatus according to claim 3, characterized in that the bypass channel (13) is formed inside the fixed scroll (3a), inside the wall of the housing (2), or outside the housing (2).

5. The apparatus according to claim 4, characterized in that the bypass channel (13) is designed as a through-opening that penetrates the base plate (3a-2) of the fixed scroll (3a).

6. The apparatus (1) for compressing a gaseous fluid includes a compression mechanism (3) for compressing the gaseous fluid and an electric motor (4) for driving the compression mechanism (3), the housing (2) is formed including an intake pressure chamber (11) and a high-pressure chamber (12), and a pipe flow control device (14-1) for the gaseous fluid is formed through a bypass passage (13), the bypass passage (13) is designed to fluidly connect the intake pressure chamber (11) and the high-pressure chamber (12) to each other, and the pipe flow control device (14-1) is designed to open the bypass passage (13) so that the gaseous fluid flows only in the flow direction from the intake pressure chamber (11) to the high-pressure chamber (12), depending on the corresponding pressure levels of the gaseous fluid in the intake pressure chamber (11) and the high-pressure chamber (12). The housing (2) includes a first housing member (2a) for housing the compression mechanism (3) and a second housing member (2b) for housing the electric motor (4). The suction pressure chamber (11) is positioned between the first housing member (2a) and the second housing member (2b). The compression mechanism (3) comprises a fixed scroll (3a) and a rotating spiral (3b), and the fixed scroll (3a) and the rotating spiral (3b) are each formed including a base plate (3a-2, 3b-2) and a helical wall (3a-1, 3b-1) extending from the base plate (3a-2, 3b-2), and the helical walls (3a-1, 3b-1) are arranged to fit together to form a processing chamber (10). The lamellar valve type pipe flow control device (14-1) is characterized in that it is positioned to support the surface of the base plate (3a-2) of the fixed scroll (3a), to face the high-pressure chamber (12), and to close the bypass flow path (13) when closed.

7. The apparatus (1) for compressing a gaseous fluid includes a compression mechanism (3) for compressing the gaseous fluid and an electric motor (4) for driving the compression mechanism (3), the housing (2) is formed including an intake pressure chamber (11) and a high-pressure chamber (12), and a pipe flow control device (14-1) for the gaseous fluid is formed through a bypass passage (13), the bypass passage (13) is designed to fluidly connect the intake pressure chamber (11) and the high-pressure chamber (12) to each other, and the pipe flow control device (14-1) is designed to open the bypass passage (13) so that the gaseous fluid flows only in the flow direction from the intake pressure chamber (11) to the high-pressure chamber (12), depending on the corresponding pressure levels of the gaseous fluid in the intake pressure chamber (11) and the high-pressure chamber (12). The housing (2) includes a first housing member (2a) for housing the compression mechanism (3) and a second housing member (2b) for housing the electric motor (4). The suction pressure chamber (11) is positioned between the first housing member (2a) and the second housing member (2b). The compression mechanism (3) comprises a fixed scroll (3a) and a rotating spiral (3b), and the fixed scroll (3a) and the rotating spiral (3b) are each formed including a base plate (3a-2, 3b-2) and a helical wall (3a-1, 3b-1) extending from the base plate (3a-2, 3b-2), and the helical walls (3a-1, 3b-1) are arranged to fit together to form a processing chamber (10). The lamellar valve type pipe flow control device (14-1) is characterized by having a fastening region (14-1a) and a closing region (14-1b) connected to each other via a neck-type connection region (14-1c).

8. The apparatus according to claim 7, characterized in that the lamellar valve type pipe flow control device (14-1) and at least one lamellar valve type outlet valve are connected to each other at a first end forming the fastening region (14-1a) in order to form an integrated unit, and the pipe flow control device (14-1) and the at least one outlet valve are oriented toward a common plane.

9. The apparatus according to claim 7, characterized in that the lamellar valve type pipe flow control device (14-1) is fixed at a first end to the base plate (3a-2) of the fixed scroll (3a) via the fastening region (14-1a), and is arranged to close the bypass flow path (13) using a free second end formed from the first end to the end and having the closing region (14-1b).

10. The apparatus according to claim 7, characterized in that the neck-shaped connection region (14-1c) is formed over a length having a constant width (B) which is smaller than the diameter (D1) of the substantially circular closed region (14-1b).

11. The apparatus according to claim 10, characterized in that the neck-shaped connection region (14-1c) has a constant outer diameter radius (R) such that the neck-shaped connection region (14-1c) is designed with an annular cross-section.

12. The apparatus according to claim 11, characterized in that the radius (R) of the outer diameter of the neck-shaped connection region (14-1c) is equal to the value obtained by subtracting the distance for the relative motion of the pipe flow control device (14-1) with respect to the fixed scroll (3a) from the inner diameter of the circular ring-shaped rising portion (3a-3) that protrudes from the surface of the base plate (3a-2) of the fixed scroll (3a) facing the high-pressure chamber (12).

13. The apparatus according to claim 12, wherein the pipe flow control device (14-1) has a vertical extension (A), and the ratio of the width (B) of the neck-shaped connection region (14-1c) to the vertical extension (A) is 0.

1.

14. The apparatus according to claim 13, wherein the pipe flow control device (14-1) has the vertical extension portion (A), and the ratio of the vertical extension portion (A) to the radius (R) of the outer diameter of the neck-shaped connection region (14-1c) is a value in the range of 0.1 to 10.

15. A method for operating an apparatus (1) for compressing a gaseous fluid according to claim 1, comprising: a housing (2) having an intake pressure chamber (11) and a high-pressure chamber (12); a bypass passage (13) connecting the intake pressure chamber (11) and the high-pressure chamber (12) to each other; and a through-pass passage control device (14-1) passing through the bypass passage (13), the method comprising: closing the bypass passage (13) while operating the apparatus (1) in compressor mode; and opening the bypass passage (13) so that the gaseous fluid flows through in the flow direction (15) of the gaseous fluid from the intake pressure chamber (11) to the inside of the high-pressure chamber (12), wherein the flow direction (15) of the gaseous fluid is set by the pressure level of the gaseous fluid inside the intake pressure chamber (11) and the high-pressure chamber (12).

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