Compact volumetric pump

Abstract

Pump for lubrication, including: a nose mounted on and driven by a shaft; a piston that is in contact with the nose; a spring acting on the piston; an inlet check valve located in an inlet port; and an exhaust check valve arranged in an exhaust port, wherein the inlet check valve and the exhaust check valve have no preload springs and are arranged vertically in a normally closed position due to gravity acting on internal balls of the inlet check valve and the exhaust check valve.

Description

TECHNICAL AREA

[0001] The present disclosure relates to a volumetric pump that selectively lubricates mechanical components. BACKGROUND AND BRIEF

[0002] Mechanical systems can include sliding and rotating components (e.g., gears, shafts, bearings, etc.) that are lubricated to reduce friction and wear. In some applications, these components can be passively lubricated by some components splashing lubricant onto other components enclosed in a closed volume (e.g., a gearbox). For example, gears rigidly connected to a gearbox shaft and at least partially immersed in lubricant can fling the lubricant into the gearbox to lubricate gears on another shaft within the gearbox that are not immersed in lubricant. Such component lubrication can impair efficiency. In particular, a large amount of lubricant can be splashed into areas within the gearbox where lubrication is not required, thus reducing the gearbox's efficiency.

[0003] More targeted lubrication can reduce performance losses. Targeted lubrication can be achieved using a pump, with the pump's output directed through channels or pipes to the areas requiring lubrication, thus reducing excess lubrication.

[0004] In such systems, an electrically driven pump can be used, which can be located within the lubricated area. However, electrically driven pumps require more electrical connections and / or wiring and also compromise ease of maintenance. On the other hand, pumps located outside the lubricated area can supply lubricant to the lubricated areas via lines or channels, but these external lines or channels can leak. Another approach can involve pumps driven by a mechanical system, for example, by one or more rotating elements of the mechanical system.

[0005] These mechanically driven pumps can also include flushing pumps, which comprise at least a piston, a spring, a pump body, and an eccentric or cam. The eccentric cam is a protruding nose that contacts the piston, or the cam cam is a cam that contacts the piston. The piston body can act as a guillotine valve for one or more inlet and outlet ports of the pump body, creating a higher differential pressure at the throttling point during a compression stroke than during an expansion stroke, thus producing a non-zero flow. However, such pumps can have lower volumetric efficiency because the initial part of the stroke is used to close the port, preventing fluid from being pumped from the pressure chamber to the outlet.Furthermore, the pressure build-up in the piston's pressure chamber can exceed a desired threshold if the lubricant has to flow through an opening into the pump body or to the outlet. Above the pressure threshold, acute or chronic damage to the pressure chamber, piston, and / or connections can occur.

[0006] The inventors recognized the aforementioned challenges and developed a pump for lubrication. The lubrication pump comprises: a nose mounted on and driven by a shaft; a piston in contact with the nose; a spring acting on the piston; an inlet check valve arranged in an inlet port; and an outlet check valve arranged in an outlet port, wherein the inlet check valve and the outlet check valve have no preload springs and are installed vertically in a normally closed position due to the force of gravity acting on the inner balls of the inlet check valve and the outlet check valve.

[0007] By providing a mechanically driven pump of lower complexity within an area containing lubricated components, highly reliable and targeted lubrication of these components can be achieved. Furthermore, it can reduce the likelihood of leaks from the mechanical system housing and / or the pump body.

[0008] In some cases, the pump can operate independently of the direction of rotation of a drive source, thus ensuring reliable lubrication. Furthermore, the pump can be self-priming regardless of air and lubricant concentrations, maintaining lubricant flow even when used in a dry sump environment.

[0009] For example, a high displacement-to-dead-volume ratio of the pump can be incorporated, enabling the pump to be self-priming. Furthermore, the volumetric efficiency can be improved compared to pumps without check valves. Inlet and outlet check valves can be integrated into the pump body, increasing the pump's compactness.

[0010] It is understood that the above summary serves to present, in simplified form, a selection of concepts that are explained in more detail in the full description. It is not intended to identify the main or essential features of the claimed subject matter, the scope of which is clearly defined by the claims that follow the detailed description. Furthermore, the claimed subject matter is not limited to implementations that overcome disadvantages mentioned above or in any part of this disclosure. BRIEF DESCRIPTION OF THE FIGURES Fig. Figure 1 is a schematic representation of a vehicle comprising one or more lubrication systems of the present disclosure. Fig. 2A is a schematic representation of a first configuration of a lubrication system and a mechanical system lubricated therein. Fig. 2B is a schematic representation of a second configuration of a lubrication system and the mechanical system lubricated therein. Fig. Figure 3A shows a schematic representation of a mechanically driven pump system in a first position. Fig. Figure 3B shows the schematic of the mechanically driven pump system in a second position. Fig. Figure 3C shows the schematic of the mechanically driven pump system in a third position. Fig. 3D shows the schematic representation of the mechanically driven pump system in a fourth position. Fig. Figure 4 is an exploded view of a mechanically driven pump. Fig. Figure 5 shows a method for operating the mechanically driven pump. Fig. Figure 6 shows a method for driving a piston of the mechanically driven pump for an expansion stroke. Fig. Figure 7 shows a method for driving the piston of the mechanically driven pump for a compression stroke. Fig. Figure 8 shows a cross-sectional view of the pump, in which an inlet check valve and an outlet check valve are housed in a wall of the pump body. Fig. Figure 9 shows a cross-sectional view of the piston of the mechanically driven pump. Fig. 10A shows the piston and nose of the pump in a first position, Fig. Figure 10B shows the piston and nose of the pump in a second position. Fig. Figure 10C shows the piston and nose of the pump in a third position. DETAILED DESCRIPTION

[0011] The description refers to a mechanically driven pump with at least two check valves, wherein the at least two check valves comprise an inlet check valve through which fluid can enter a pressure chamber of the pump, and an outlet check valve through which fluid can exit the pressure chamber of the pump. The mechanically driven pump can be driven by a mechanical system, for example, a mechanical system that is lubricated by the mechanically driven pump. The pump can be housed in an enclosed space or casing, such as a gearbox, and driven without an electric motor.

[0012] A plurality of holes can accommodate the inlet and outlet check valves, the holes comprising at least a first hole for accommodating the inlet check valve and at least a second hole for accommodating the outlet check valve. The plurality of holes can be drilled or machined from the pump body, so that modifications, such as changes to the pressure and flow rate through the valves and the valve size, can be made by drilling or other machining processes of the pump body. The pump of this disclosure can reduce the cost of modifying pump features, since modified features, such as fluid passages, can be machined and enlarged. Furthermore, the simplicity of the pump of this disclosure, particularly of the check valves, can reduce the cost of the materials and components used to manufacture the pump.

[0013] A possible embodiment of a compact, mechanically driven pump is described, which can be embedded in a mechanical system as a volumetric flushing pump. In a version with fewer parts, the pump consists of a piston, a spring, a pump body, and an eccentric or cam. Furthermore, the pump remains effective in both directions of rotation. One or more inlet ports are incorporated into the pump body.

[0014] A piston jacket can act as a guillotine valve at one or more inlet ports. The outlet port is shaped like an orifice, and the pump relies on a higher differential pressure across the orifice during the compression stroke compared to the differential pressure during the expansion stroke to achieve a non-zero flow rate. An advantage of this approach is that no special valve is required. The initial part of the stroke serves to close the guillotine port, preventing fluid from reaching the outlet, and a minimal backflow from the outlet to the chamber is also possible during the intake strokes. The flow rate forced through an opening in the pump is so high that the pressure buildup and pressure changes within the pressure chamber of the compact, mechanically driven pump can be so significant as to damage the pump.

[0015] To improve volumetric efficiency and reduce excessive pressure buildup in the chamber above a certain pressure threshold, the configuration of the mechanically driven pump can, for example, minimize the buildup of excessive pressure in the chamber and maintain a high volumetric efficiency through the use of gravity-operated check valves. These check valves can prevent fluid from entering the chamber at the end of a compression stroke and from exiting at the beginning of an expansion stroke, without the piston acting as a guillotine valve.

[0016] Flushing pumps possess characteristics that allow them to operate (e.g., pump) with a mixture of air and liquid in an unknown ratio. Consequently, the pump's performance and efficiency are subject to unpredictable and significant fluctuations. The higher the air content in the mixture, the lower the pressure generated by the pump. For this reason, spring-loaded check valves are unsuitable for this application. In some cases, the pump pressure may be too low to overcome the spring force and open the valve.

[0017] To solve this problem, the mechanically driven pump incorporates at least two springless check valves. These springless check valves are designed without springs, such as preload springs. They are oriented perpendicular to the direction of gravity, so gravity acting on the ball keeps the valve closed. Because the weight of the closing ball is significantly less than that of a preloaded spring, the check valve can operate even at the minimal pressure encountered at low speeds when the piston moves. Furthermore, the lower pressures required to open the springless check valves allow the pump to handle larger volumes of air or other gaseous fluids relative to liquid fluids compared to other check valve configurations that use springs.The springless check valves can include at least the inlet check valve and the outlet check valve described above.

[0018] The pump body can house the piston and spring, with the pressure chamber being the volume between the piston and the pump body that can accommodate the spring. The nose can contact the piston. Rotation of the nose can drive the piston into an up-and-down motion, cyclically compressing and releasing pressure from the spring. By moving the piston, the volume of the pressure chamber can be increased or decreased, thereby decreasing or increasing the pressure. The nose can be driven by the mechanical system, for example, by the torque of a rotating element. A first example: The mechanically driven pump can be a cam-driven, spring-driven pump, where the nose is a cam nose. A second example: The mechanically driven pump can be an eccentrically driven pump, where the nose is an eccentric nose.The mechanically driven pump exerts force on the piston and can simultaneously act as a force transmission mechanism to the piston and as a device for opening and closing the springless check valves by pressure.

[0019] The inlet and outlet check valves are arranged vertically so that they are normally closed by gravity. The inlet and outlet check valves can be integrated into the pump body, increasing compactness compared to pumps with valves located outside the pump body. The pump can be arranged so that the inlet check valve can be closed during a compression stroke and the outlet check valve during the expansion stroke by the differential pressures of the pressure chamber acting against gravity. This arrangement eliminates the need to use the piston as a guillotine valve to open and close the inlets or outlets of the pressure chamber.The first part of the expansion and compression strokes can be used by the mechanically driven pump of this disclosure to close connections while the fluid continues to be pumped into and out of the pressure chamber. The inlet and outlet check valves can increase the volumetric efficiency of the mechanically driven pump of this disclosure compared to another pump with a piston configuration acting as a guillotine valve. A compression stroke can alternatively be referred to as a delivery stroke, since fluid can be pumped out of the pump during the compression stroke. Furthermore, an expansion stroke can also be referred to as a suction stroke, since the pump can draw in fluid during the expansion stroke.

[0020] The mechanically driven pump of the present disclosure has the advantage that it can operate independently of the direction in which energy is supplied to the pump. The mechanically driven pump can also operate without controls or actuators. Furthermore, the mechanically driven pump can be self-priming, so that it can pump a fluid, e.g., a lubricant, even when air is present at the pump. Due to its self-priming capability, the mechanically driven pump can be used as a flushing pump.

[0021] Fig. Figure 1 is a schematic representation of a vehicle comprising one or more lubrication systems of the present disclosure. Fig. 2A is a schematic representation of a first configuration of a lubrication system and a mechanical system lubricated therein. The first configuration of Fig. 2A comprises a pump as described in the present disclosure, which is used as a flushing pump for the dry storage tank, and a second pump, the second pump being fluidically coupled to a quiet storage tank. The second pump selectively pumps lubricant from the quiet storage tank and lubricates one or more components of the mechanical system. Fig. Figure 2B is a schematic representation of a second configuration of a lubrication system and the mechanical system lubricated therein. The second configuration of Fig. 2B contains the pump of the present disclosure, which is used as a flushing pump for the drying tank. The quiescent reservoir of the lubrication system of Fig. 2B is designed to passively lubricate one or more components of the mechanical system and does not have the second pump of Fig. 2A.

[0022] Fig. Figure 3A shows a schematic representation of a mechanically driven pump system in which a piston of the driven pump system is in a first position. The piston can be in the first position during a compression stroke. Fig. Figure 3B shows the schematic of the mechanically driven pump system, in which one piston of the driven pump system is in a second position. The piston can be in the second position at the end of the compression stroke or at the beginning of an expansion stroke. Fig. Figure 3C shows the schematic of the mechanically driven pump system in a third position. The piston can be in the third position during the expansion stroke. Fig. 3D shows a schematic representation of the mechanically driven pump system in a fourth position. The schematic of the mechanically driven pump system of the Fig. 3A-3D has at least one inlet check valve and one outlet check valve, wherein the fluid enters the pump via the inlet check valve and exits the pump via the outlet check valve. The piston can be in the first position at the end of the expansion stroke or at the beginning of the compression stroke. Fig. Figure 4 is an exploded view of a mechanically driven pump, showing that the inlet and outlet check valves are springless (i.e., without springs). The inlet and outlet check valves can be integrated into the pump body, with the inlet and outlet check valves located in the body's openings. The inlet and outlet check valves are vertically oriented so that gravity passively closes them when not opened by hydraulic pressure. Fig. Figure 5 shows a method a for operating the mechanically driven pump. Fig. Figure 5 shows the steps of a pump cycle in which the pump alternates between an expansion stroke and a compression stroke. Fig. Figure 6 shows a method for driving a piston of the mechanically driven pump during the expansion stroke. Fig. Figure 7 shows a method for driving the piston of the mechanically driven pump during the compression stroke. Fig. Figure 8 shows a cross-sectional view of the pump, in which an inlet check valve and an outlet check valve are housed in a wall of the pump body. Fig. Figure 9 shows a cross-sectional view of the piston of the mechanically driven pump.

[0023] Fig. Figure 10A shows the piston and a nose of the pump in a first position. The first position can be a bottom dead center (BDC) position, in which the piston is at BDC. Fig. Figure 10B shows the piston and nose of the pump in a second position. Fig. Figure 10C shows the piston and nose of the pump in a third position. The third position can be top dead center (TDC), where the piston is at TDC. The second position of Fig. 10B is in a stroke position where piston 320 is between top dead center and bottom dead center. The second position could, for example, be a position during an expansion stroke.

[0024] Fig. Figure 1 shows a vehicle 100 with a drivetrain 101 and a drivetrain 103. The vehicle 100 can have a front end 102 and a rear end 104, located on opposite sides of the vehicle 100. Objects, components, and features of the vehicle 100 described as being near the front can be located closest to the front end 102 compared to the rear end 104. Objects, components, and features of the vehicle 100 described as being near the rear can be located closest to the rear end 104 compared to the front end 102. The vehicle 100 can have a longitudinal axis 130. The drivetrain 101 and the drivetrain 103 can have a length parallel to the longitudinal axis 130.

[0025] The drive train 101 comprises a drive motor 106 and a gearbox 108. The drive motor 106 can, for example, be an internal combustion engine (ICE). Alternatively, the drive motor 106 can be an electric motor. The drive motor 106 is operated to supply the gearbox 108 with torque. The gearbox 108 receives the torque generated by the drive motor 106 as input, and the gearbox 108 outputs the torque to the drive train 103 according to a selected gear or setting.

[0026] Vehicle 100 can be a commercial vehicle, a light, medium, or heavy commercial vehicle, a passenger vehicle, an off-road vehicle, a utility vehicle, an agricultural vehicle, and / or a sport utility vehicle. In one embodiment, Vehicle 100 can be a wheeled vehicle, such as an automobile. Additionally or alternatively, Vehicle 100 can also be an aircraft, a boat, or another vehicle system. Additionally or alternatively, Vehicle 100 and / or one or more of its components, such as components of the powertrain 101 and / or the powertrain 103, can be used in industrial, locomotive, military, agricultural, and / or aerospace applications. In one example, Vehicle 100 is a fully electric vehicle or a vehicle with fully electric operation, such as a plug-in hybrid vehicle.The drive machine 106 can be an electric machine, e.g., an electric motor / generator. The vehicle 100 can, for example, be a hybrid vehicle in which multiple torques are introduced into the transmission 108. Thus, in addition to the drive machine 106, there can be at least one other drive machine that feeds into the transmission 108. If the drive machine is an internal combustion engine or another non-electric machine, the other drive machine can be an electric machine, e.g., an electric motor or an electric motor / generator. The vehicle 100 can be equipped with a drive shaft 122. The drive shaft 122 can be rotatably coupled to the transmission 108, so that the transmission 108 can rotate and drive the drive shaft 122.

[0027] The drive motor 106 can be powered by energy from an energy storage device 105. The energy storage device 105 is, for example, a battery, such as a traction battery, that can store electrical energy. An inverter 107 can be arranged between the energy storage device 105 and the drive motor 106 and configured to convert direct current (DC) to alternating current (AC). The inverter 107 can contain a variety of components and circuits with thermal requirements that affect the inverter's efficiency.

[0028] The drivetrain 103 can include an axle assembly 112. The axle assembly 112 can be configured to drive a set of wheels 114. In one example, the axle assembly 112 is located near the rear of the vehicle 100 and thus comprises a rear axle. Another example is that the axle assembly 112 can be located near the front of the vehicle 100 and thus comprises a front axle. A further example is an additional axle assembly that can be located separately from the axle assembly 112 near the front of the vehicle 100. The additional axle assembly can be drive-coupled to the transmission so that it is driven by the transmission 108 or another transmission. The vehicle 100 can have additional wheels that are not connected to the drivetrain 103.

[0029] The gearbox 108 can be driven by the axle assembly 112 via the drive shaft 122. In other words, the gearbox 108 can be driven by the drive shaft 122, and the drive shaft 122 can drive the axle assembly 112. In some configurations, such as in Fig. As shown in Figure 1, the drive train 103 comprises a transfer case 110, which is configured to receive the rotational power supplied by the gearbox 108. The drive shaft 122 can be driven by the transfer case 110 and can be driven by the gearbox 108 via the transfer case 110.

[0030] The axle assembly 112 can include a differential 116 and a first set of axle shafts. The differential 116 can drive the first set of axle shafts by transmitting torque to and driving them. The differential 116 can distribute unequal torque to one or more of the wheels 114 that are drive-coupled at opposite ends of the axle assembly 112. The differential 116 can distribute unequal torque to each of the wheels 114.

[0031] The transmission 108 comprises at least one mechanical element of the mechanical system, wherein the mechanical elements are capable of performing movements such as rotation and / or translation. The mechanical system can here be referred to as the mechanical arrangement 132. The mechanical arrangement 132 can be a transmission comprising gear sets or another train comprising sets with different speeds / ratios. The mechanical arrangement 132 can comprise a series of rotating elements, such as gears, shafts, and couplings. Likewise, the mechanical arrangement 132 can comprise an arrangement of displaceable elements, such as couplings and shift rods. The rotational energy of the drive machine 106 can drive the mechanical arrangement 132, and the mechanical arrangement 132 can drive one or more shafts or other rotating elements that are rotatably connected to the transmission 108.The mechanical arrangement 132 can be one of several mechanical arrangements of the vehicle 100 and is referred to below as the first mechanical arrangement 132.

[0032] Furthermore, the vehicle 100 may be equipped with other transmissions, e.g., a separate gearbox 134. The gearbox 134 may comprise a second mechanical system of mechanical elements, wherein the mechanical elements are capable of movements such as rotation and / or translation. The second mechanical system may be referred to here as the second mechanical arrangement 136. The second mechanical arrangement 136 may be a gearbox comprising sets of gears or another train comprising sets with different speeds / ratios. The second mechanical arrangement 136 may comprise an arrangement of rotating elements such as gears, shafts, and couplings. Likewise, the second mechanical arrangement 136 may comprise an arrangement of sliding elements, such as clutches and shift rods.The transmission 134 and the second mechanical arrangement 136 can constitute a speed reduction system for the vehicle 100 or a part thereof. Rotational energy from rotating elements of the drivetrain 103, for example, downstream of the transmission 108, can drive the transmission 134 via the second mechanical arrangement 136. Likewise, one or more rotating elements can be driven via the transmission 134 and, in particular, via rotating elements of the second mechanical arrangement 136. For example, the transmission 134 can be located downstream of the transmission 108 and upstream of the differential 116. The transmission 134, and in particular the second mechanical arrangement 136, can be rotatably coupled to the drive shaft 122 and the differential 116, so that they are driven by the drive shaft 122 and facilitate the drive of the differential 116.Another example: The gearbox 134 can be located downstream of the differential 116 and upstream of one of the wheels 114. The gearbox 134, and in particular the second mechanical arrangement 136, can be driven by the differential 116 and at least one of the wheels 114, in order to be driven via the differential 116 and to facilitate the drive of at least one of the wheels 114.

[0033] The vehicle 100, in particular the powertrain 103, can comprise a variety of lubrication systems as described in this disclosure, such as a first lubrication system 140. The transmission 108 can incorporate and / or include the components and features of the first lubrication system 140. The first lubrication system 140 can be coupled to the first mechanical arrangement 132 so that it is driven to generate hydraulic energy and a fluid flow over one or more rotating elements of the first mechanical arrangement 132. Furthermore, the transmission 134 can contain and / or include the components and features of a second lubrication system 142. The second lubrication system 142 can be coupled to the second mechanical arrangement 136 so that it is driven to generate hydraulic energy and a fluid flow over one or more rotating elements of the second mechanical arrangement 136.The vehicle 100 and the drivetrain 103 can include a third lubrication system 144. A housing of the drivetrain 103 can accommodate and / or include the components and features of the third lubrication system 144. The third lubrication system 144 can be coupled to one or more rotating elements, such as shafts or gears, of the drivetrain 103, so that it is driven to generate hydraulic energy and a fluid flow across the rotating elements of the second drivetrain 103.

[0034] A first arrow 172, a second arrow 174, and a third arrow 176 can each represent a fluid flow containing lubricant transported via the first lubrication system 140, the second lubrication system 142, and the third lubrication system 144, respectively. The lubricant transported and contained via the first lubrication system 140, the second lubrication system 142, and the third lubrication system 144 can be a liquid fluid, such as oil. The fluid flow transported via the first arrow 172, the second arrow 174, and the third arrow 176 can also contain a gaseous fluid, such as air. The first lubrication system 140 can selectively lubricate rotating elements such as gears, shafts, couplings, and other components of the transmission 108 used to create transmission ratios. Other moving elements of the transmission 108, such as... B. Shift rods, are specifically lubricated by the first lubrication system 140.For example, the first lubrication system 140 can selectively lubricate elements, components, and features of the first mechanical arrangement 132, as indicated by the first arrow 172. The second lubrication system 142 can selectively lubricate rotating elements such as gears, shafts, couplings, and other components of the transmission 134 used to create transmission ratios. Likewise, the second lubrication system 142 can selectively lubricate other moving elements, such as the shift rods of the transmission 134. For example, the second lubrication system 142 can selectively lubricate elements, components, and features of the second mechanical arrangement 136, as indicated by the second arrow 174. The third lubrication system 144 can selectively lubricate elements, components, and features of the drive train 103. For example, the third lubrication system 144 can selectively lubricate the drive shaft 122, as indicated by the third arrow 176.

[0035] The adjustment of the powertrain 103 between the different operating modes, as well as the control of operation within each operating mode, can be based on a vehicle control system 154, including a controller 156. The controller 156 can be a microcomputer, including components such as a microprocessor unit, input / output connectors, an electronic storage medium for executable programs and calibration values ​​(e.g., a read-only memory chip), working memory, diagnostic memory, and a data bus. The storage medium can be programmed with computer-readable data representing instructions that can be executed by a processor to perform the procedures described below, as well as other variations that are expected but not explicitly listed. In one example, the controller 156 can be a powertrain control module (PCM).

[0036] The controller 156 can receive various signals from sensors 158 that are connected to different areas of the vehicle 100. The sensors 158 may include, for example, sensors on the drive motor 106 or another drive motor for measuring the speed and temperature of the drive motor, a pedal position sensor for detecting the actuation of a pedal operated by the driver, e.g., an accelerator or brake pedal, a lever position sensor for detecting the actuation of a lever, e.g., a brake lever, speed sensors on the wheels 114, several fluid level sensors for detecting the fluid level in one or more collection tanks and / or reservoirs, several pressure sensors for estimating the pressure and fluid flow through the fluid lines, etc.The first lubrication system 140, the second lubrication system 142, and the third lubrication system 144 can include one or more pumps and / or reservoirs, which are monitored by the fluid level sensors and the fluid lines monitored by the pressure sensors. After receiving the signals from the various sensors 158... Fig. 1. The control unit 156 processes the received signals and uses various actuators 160 of the vehicle 100 to adjust the operation of the transmission based on the received signals and the instructions stored in the memory of the control unit 156. For example, the control unit 156 can receive a signal indicating the depressurization of the brake pedal, signaling a desire for a decrease in vehicle speed. The vehicle braking can be directly proportional to the position of the accelerator pedal, e.g., the degree of depressurization. Another example is that the control unit 156 receives a signal indicating the depressurization of the accelerator pedal, signaling a desire for a decrease in vehicle speed. The vehicle acceleration can be directly proportional to the accelerator pedal position, e.g., the degree of depressurization. In response, the control unit 156 can command operations such as shifting the gears of the transmission 108.Alternatively, the gears of the 108 transmission can also be shifted manually, e.g. if the 108 transmission is a manual transmission.

[0037] The transmission 108 can be a gear housing. Alternatively, the transmission 108 can also be an axle transmission or a transaxle transmission and can be arranged in or part of an axle assembly such as the axle assembly 112. In some embodiments, the transmission 108 can additionally or alternatively be a first transmission, and the vehicle 100 can have a second transmission. The second transmission can be located closer to the rear or in a different position on the vehicle 100 than the transmission 108.

[0038] The drivetrain 103 is shown in a rear-wheel-drive configuration, although other configurations are possible. In one or more examples, the drivetrain 103 may include a front-wheel-drive, all-wheel-drive, or four-wheel-drive configuration. Furthermore, the drivetrain 103 may include one or more tandem axle arrangements. For example, in addition to the axle arrangement 112, there may be one or more axle arrangements, and in addition to the axle of the axle arrangement 112, there may be one or more axles. Thus, the drivetrain 103 may also have other configurations without deviating from the scope of this disclosure, and those described in Fig. The configuration shown in Figure 1 is for illustrative purposes only and does not represent a limitation. In some embodiments, for example, the transmission 108 may additionally or alternatively be a first transmission, and the vehicle 100 may have a second transmission arranged on the second set of axle shafts. The transmission 108 may be a gearbox. Alternatively, the transmission 108 may also be an axle transmission or a transaxle transmission.

[0039] Fig. Figure 2A shows a schematic representation of a first configuration of an arrangement containing a pump of the present disclosure, here referred to as the first arrangement 200. The first arrangement 200 comprises a first lubrication system 212 and a mechanical system 216. The first lubrication system 212 is an active lubrication system comprising at least one flushing pump and another pump, e.g., a second pump 228. The other pump, e.g., the second pump 228, can be used to pump and pressurize fluid for the targeted lubrication of components and devices of the mechanical system 216 from a still reservoir, e.g., a still reservoir 224.

[0040] The first lubrication system 212 can replace the first lubrication system 140, the second lubrication system 142, or the third lubrication system 144. Fig. 1 or each part thereof. The mechanical system 216 can be an arrangement comprising a plurality of rotational and translational elements, and it can include a gear train. The mechanical system 216 can be the first mechanical arrangement 132, the second mechanical arrangement 136, or another mechanical arrangement of the drive train of the 103. Fig. 1 or each part thereof.

[0041] Fig. Figure 2B shows a schematic representation of a first configuration of an arrangement that includes a pump of the present disclosure and is referred to here as the second arrangement 280. The second arrangement 280 comprises a second lubrication system 282 and the mechanical system 216. The second lubrication system 282 includes at least one flushing pump, which is a pump of the present disclosure. The second lubrication system 282 lacks a pump for pressurizing and conveying fluid from a still reservoir, such as the still reservoir 224, to the mechanical system 216. The second lubrication system 282 also lacks a pump for extracting fluid from the still reservoir 224. The second arrangement 280 and the second lubrication system 282 are passive arrangements that passively remove the lubricant from the still reservoir 224 by passive forces, e.g., by gravity. Gravity can be represented by an arrow 284.

[0042] The second lubrication system 282 can replace the first lubrication system 140, the second lubrication system 142, or the third lubrication system 144. Fig. 1 or each part thereof.

[0043] The in the Fig. The components and features shown in 2A to 2B can be used synonymously here.

[0044] The first and second lubrication systems 212, 282 can transport and pressurize the lubricant 230. The lubricant 230 can be oil.

[0045] The first lubrication system 212 and the second lubrication system 282 can comprise a housing 214. The housing 214 can be a housing or part of another solid element or component of a gearbox, transmission, or drivetrain. For example, the housing 214 can be part of the gearbox 108 or the gearbox 134 of Fig. 1 or a housing or a feature of the drive train 103 of Fig. 1. The first lubrication system 212 and the second lubrication system 282 can comprise a dry sump 222 and the quiet reservoir 224. The lubricant 230 can be contained and / or transported in the dry sump 222 and the quiet reservoir 224. The flow of the lubricant 230 through the first and second lubrication systems 212, 282 can be represented by a variety of arrows 272.

[0046] The dry sump 222 can be fluidically connected to a mechanically driven pump 226, with the mechanically driven pump 226 being located downstream of the dry sump 222. Furthermore, the still reservoir 224 can be fluidically connected to the mechanically driven pump 226, with the mechanically driven pump 226 being located upstream of the still reservoir 224. In other words, the dry sump 222 can be brought into fluid communication with the still reservoir 224 via the mechanically driven pump 226, with the dry sump 222 being on the suction side of the mechanically driven pump 226 and the still reservoir 224 on the pressure side of the mechanically driven pump 226. The mechanically driven pump 226 can be the flushing pump of the dry sump 222.

[0047] In the first arrangement 200 and the first lubrication system 212, the calm reservoir 224 can be fluidically coupled to the second pump 228, the second pump 228 being located downstream of the calm reservoir 224. Furthermore, in the first arrangement 200 and the first lubrication system 212, one or more components and features of the mechanical system 216 can be fluidically coupled to the second pump 228, the second pump 228 being located upstream of the mechanical system 216. In other words, the calm reservoir 224 can be fluidly connected to the mechanical system 216 via the second pump 228, with the calm reservoir 224 being located on the suction side of the second pump 228 and the mechanical system 216 on the pressure side of the second pump 228.

[0048] The mechanical system 216 can comprise a variety of rotating elements, including a first rotating element 242 and a second rotating element 244. The first rotating element 242 and the second rotating element 244 can be parallel. The mechanical system 216 can include a third rotating element 246 or be rotatably coupled to it, such that the third rotating element 246 can be driven by one or more rotating elements of the mechanical system 216. The third rotating element 246 can, for example, be rotated via a trigger of the mechanical system 216. The trigger can include a gear set or other reduction gear that can be driven via a rotating element of the mechanical system 216.

[0049] The first rotating element 242, the second rotating element 244, and the third rotating element 246 can be shafts. At least the first or the second rotating element 242, 244 can be driven by a drive and receive rotational energy, e.g., in the form of torque, from a drive device. For example, the drive machine 106 can be Fig. 1. Either the first or the second rotating element 242, 244 can be driven. The third rotating element 246, and thus also the mechanically driven pump 226, can also be driven without a special drive device. In other words: The third rotating element 246, and thus the mechanically driven pump 226, can only be driven by a drive that drives the mechanical system 216, for example, a drive that drives the first rotating element 242 or the second rotating element 244.

[0050] The source of motion for the mechanically driven pump 226 is the mechanical system 216 itself. The third rotating element 246 can, for example, be coupled to the mechanically driven pump 226 to supply and drive it with rotational energy. The third rotating element 246 can thus be the source of motion for the pumping action of the mechanically driven pump 226. In other words, the mechanically driven pump 226 can generate suction when driven by the third rotating element 246. The pumping cycle can be proportional to the rotational speed of the third rotating element 246, whereby increasing the rotational speed of the third rotating element 246 can increase the reciprocating motion of the mechanically driven pump 226. An increase in the rotational speed of the third rotating element 246 can increase the flow rate and pressure of the mechanically driven pump 226.The third rotating element 246 can have a maximum angular velocity between 1500 and 4000 revolutions per minute (rpm).

[0051] The first rotating element 242, the second rotating element 244 and the third rotating element 246 can be waves.

[0052] The mechanical system 216 comprises at least one gear set 252. The gear set 252 is surrounded by a plurality of dashed lines 254, which are arranged in a rectangle for clarity. The gear set 252 comprises at least two gears, a first gear 262 and a second gear 264. However, it is understood that there may be additional gears that mesh with the first gear 262 and the second gear 264, the additional gears comprising one or more idle gears that mesh with and are arranged between the first gear 262 and the second gear 264. The mechanical system 216 comprises a disconnecting device 248 that can selectively connect the first rotating element 242 to the first gear 262 of the gear set 252. The disconnecting device 248 may be a coupling device with a coupling, for example, a wet coupling.A bearing arrangement 266 can be arranged radially between the first gear 262 and the first rotating element 242. The bearing arrangement 266 can support the first gear 262, allowing the first gear 262 to rotate independently of the first rotating element 242. The second rotating element 244 can rigidly couple another gear of the gear set 252.

[0053] One or more components and features of the mechanical system 216 can be selectively lubricated by the first lubrication system 212 or the second lubrication system 282. In other words, the first lubrication system 212 or the second lubrication system 282 can supply the lubricant 230 to one or more components of the mechanical system 216. In a first set of examples, the lubricant can be supplied to a component and / or feature of the mechanical system 216 via the first lubrication system 212 and the second pump 228. The second pump 228 draws the lubricant from the stationary reservoir 224. In a second set of examples, the lubricant can be supplied to a component and / or feature of the mechanical system via the second lubrication system 282 by gravity acting on the stationary reservoir 224.

[0054] For example, the first lubrication system 212 can provide targeted lubrication of a tooth mesh 268 between the gears of the gear set 252, as indicated by the arrows 272. The tooth mesh 268 can be located between the first gear 262 and the second gear 264 and, for visual clarity, can be surrounded by a multitude of dashed lines 270 arranged in a rectangle. In this or another example, the first lubrication system 212 can selectively lubricate the separating device 248, as indicated by the arrows 272. In these or other examples, the first lubrication system 212 can selectively lubricate the actuator 250, as indicated by the arrows 272. In these or other examples, the first lubrication system 212 can selectively lubricate the bearing arrangement 266, as indicated by the arrows 272.

[0055] The lubricant 230 can be returned to the dry sump 222 after lubricating components or features of the mechanical system 216, as indicated by arrows 272. The mechanically driven pump 226 can draw the lubricant 230 from the dry sump 222 and pressurize it, as indicated by arrows 272. Additionally, the mechanically driven pump 226 can draw a gaseous fluid, e.g., air, from the dry sump along with the lubricant 230 and pressurize it. The mechanically driven pump can direct the lubricant 230 into the still reservoir 224, as indicated by arrows 272. The suction rate of the lubricant 230 from the dry sump 222 and the fluid flow rate through the mechanically driven pump 226 can be proportional to the rotational speed of the third rotating element 246.

[0056] The mechanically driven pump 226 comprises an inlet check valve system 274 and an outlet check valve system 276, each containing a check valve. The inlet check valve system 274 can open the mechanically driven pump 226 to the dry sump 222. In other words, the inlet check valve system 274 can connect the mechanically driven pump 226 to the dry sump 222 with fluid. The outlet check valve system 276 can open the mechanically driven pump 226 to the still reservoir 224. In other words, the outlet check valve system 276 can connect the mechanically driven pump 226, and thus the dry sump 222, to fluid with the still reservoir 224. The inlet check valve system 274 can open during an expansion stroke of the mechanically driven pump 226. The outlet check valve system 276 can open during the compression stroke of the mechanically driven pump 226.

[0057] To compare the views in the Fig. 3A-4 and 8-10C are provided with a set of reference axes 301. The reference axes 301 specify a y-axis, an x-axis, and a z-axis. In one example, the z-axis can be parallel to a direction of gravity, and the xy-plane can be parallel to a horizontal plane on which the mechanically driven pump 226 can rest. The direction of gravity can be represented by the arrow 284, as shown in Fig. 2A-4 and Fig. 8. When referring to a direction, a positive sign can indicate the direction of the arrow on the y-axis, x-axis, and z-axis, and a negative sign can indicate the direction opposite to the arrow on the y-axis, x-axis, and z-axis. A filled circle can represent an arrow and axis pointing towards or positive to a viewing direction. An unfilled circle can represent an arrow and axis pointing away from or negative to a view.

[0058] Fig. Figure 3A-3D shows a schematic representation 300 of a pump system comprising the mechanically driven pump 226, the inlet check valve system 274, and the outlet check valve system 276. The representation is a cross-section. For clarity, the components of the mechanically driven pump 226 are surrounded by a plurality of first dashed lines 304 arranged in a rectangle. For clarity, the components of the inlet check valve system 274 are surrounded by a plurality of second dashed lines 306 arranged in a rectangle. For clarity, the components of the outlet check valve system 276 are surrounded by several dashed third lines 308 arranged in a rectangle. The mechanically driven pump 226 can be fluidically connected to the inlet check valve system 274 and the outlet check valve system 276 via a plurality of fluid couplings 310.In other words, the mechanically driven pump 226 can be fluidically connected to the inlet check valve system 274 and the outlet check valve system 276 via the fluid couplings 310. It is understood that the mechanically driven pump 226 can contain (e.g., include) one, several, or all components of the inlet check valve system 274 and / or the outlet check valve system 276.

[0059] The mechanically driven pump 226, the inlet check valve system 274, and the outlet check valve system 276 can be housed in an enclosed environment 303. The enclosed environment 303 can be a gearbox, transmission, axle, differential, or other area where gears, sliding surfaces, etc., are lubricated. The enclosed environment 303 can, for example, be part of the housing 214 of the Fig. 2A-2B or are located within them.

[0060] The mechanically driven pump 226 has few parts and can be operated without a control system. The mechanically driven pump 226 comprises at least a piston 320, a spring 324, a pump body 318, and a nose 322, which may be eccentric or cam-shaped. The mechanically driven pump 226 may also include check valves of the inlet check valve system 274 or the outlet check valve system 276. The mechanically driven pump 226 may include a filter 396 and / or other parts that facilitate contact between the spring 324 and the other components. The filter 396 and the other facilitating parts may overcome the technological limitations of manufacturing but are not essential to the disclosure. The mechanically driven pump 226 is a two-stroke pump that can generate a flow through the outlet check valve system 276 regardless of whether the nose 322 rotates clockwise or counterclockwise.

[0061] The spring 324 and the piston 320 are configured to slide into a hole in the pump body 318, which is represented and indicated by the arrows 319. The hole represented by the arrows 319 can be a cavity in the pump body 318 and can have a cylindrical shape and volume. The hole represented by the arrows 319 can be located centrally, e.g., radially around the first axis 404. Likewise, the piston 320 and the spring 324 are configured to be centered, e.g., radially around the first axis 404. The first axis 404 can be a vertical axis with respect to the reference axes 301. The hole represented and indicated by the arrows 319 can be a bore machined into the pump body 318. The pump body 318 can have a side wall 330 and a surface 326 that form a perimeter around the hole of the arrows 319.The side wall 330 can curve radially around the hole, and the side wall 330 can have a cylindrical shape. The side wall 330 can have a surface facing the hole represented by arrows 319 and curved radially around it. The surface of the side wall 330 surrounding the hole represented by arrows 319 can have a cylindrical shape. The surface 326 can be flat. The surface 326 can be part of a bottom wall, a base, or another block feature of the pump body 318.

[0062] The piston 320 has a cylindrical shape and contains a cavity, the cavity being a Fig. The cavity shown in Figure 9 can be enclosed by a piston sleeve 328 of the piston 320, the piston sleeve 328 being curved around the cavity. The piston sleeve 328 can have a cylindrical shape. The cavity is designed to receive the spring 324. The spring 324 can contact the piston 320 and exert a spring force on it.

[0063] A first end of the spring 324 is in direct contact with the pump body 318, and a second end of the spring 324 is in direct contact with a surface of the upper inner wall 329 of the piston 320, with the first end facing the second end. In particular, the first end of the spring 324 can touch the surface 326. The spring 324 can press directly against the piston 320 and press the piston 320 against the nose 322. The stiffness of the spring 324 can be selected based on the maximum acceleration, the mass, and the force exerted / applied on the piston 320. The acceleration of the piston 320 and the force exerted on the piston 320 can depend on the angular velocity of the shaft 321 and the nose 322, and on the stroke of the nose 322 and the piston 320, as indicated by the arrows 372. For example, the maximum rotational speed of shaft 321 can be at or below a threshold value for rotational speed.The speed threshold is, for example, 1500 rpm. Another example: The speed threshold is 4000 rpm. The stroke of the nose 322, represented by arrows 372, can be 10 millimeters. The piston 320 can have a mass of 32 grams. The spring 324 can have a minimum spring stiffness (e.g., a threshold for stiffness that the spring 324 can exceed or reach) of 4000 newtons per meter.

[0064] In the Fig. Figures 3A to 3D depict an operating sequence in which the mechanically driven pump 226 is shown in various positions during its reciprocating movement through expansion and compression strokes. In the sequence of Fig. In 3A-3D, a piston 320 moves radially with respect to a pivot point 338, and the nose 322 rotates in a first direction indicated by the arrow 362. The first direction indicated by the arrow 362 can be counterclockwise. The piston 320 can be moved between a top dead center (TDC) 313 and a bottom dead center (BDC) 315. The piston 320 can be moved in a first direction, represented by an arrow 312, towards the top dead center 313 and away from the bottom dead center 315. The piston 320 can be moved in a second direction, represented by an arrow 314, away from top dead center 313 and towards bottom dead center 315. The first direction, represented by the arrow 312, can be upwards, and top dead center 313 can be in its highest position relative to the mechanically driven pump 226.The distance between top dead center 313 and bottom dead center 315 can be one piston stroke of the piston 320, and the piston stroke distance can be represented by arrows 372. The spring 324 can prevent the piston 320 from being pushed deeper than bottom dead center 315 and can prevent contact between the piston and the surface 326.

[0065] Fig. Figure 3A shows that the mechanically driven pump 226 is configured such that the piston 320 is in a first position between top dead center (TDC) and bottom dead center (BDC). In the first position, the piston 320 can be in the middle of an exhaust stroke of a stroke cycle and move towards bottom dead center 315. Fig. Figure 3B shows the mechanically driven pump 226, which is configured such that the piston 320 is in a second position, in which the piston 320 is at bottom dead center 315. In the second position, the piston 320 can be at the end of a compression stroke or at the beginning of an expansion stroke of a stroke cycle. In other words, in the second position, the piston 320 can move back and forth between the intake stroke and the expansion stroke of a pumping operation. Fig. Figure 3C shows a mechanically driven pump 226, configured such that the piston 320 is in a third position, in which the piston 320 is located between top dead center 313 and bottom dead center 315. In the third position, the piston 320 can be in the middle of an expansion stroke of a stroke cycle and move towards top dead center 313. Fig. 3D shows the pump, and in particular the piston 320, in a fourth position, in which the piston 320 is at bottom dead center 315. In the fourth position, the piston 320 can be at the end of an expansion stroke or at the beginning of a compression stroke of a stroke cycle. In other words, in the fourth position, the piston 320 can move back and forth between an expansion stroke and an exhaust stroke of a pumping process. The workflow can also be referred to as process 500 of Fig. 5 will be summarized and visualized.

[0066] The mechanically driven pump 226 has a high displacement-to-clearance volume ratio (e.g., greater than 5 and less than 15), and is self-priming. The clearance volume is the volume between one nearest check valve of the inlet check valve system 274 and another nearest check valve of the outlet check valve system 276 when the piston 320 is at bottom dead center 315. The displacement volume is the volume between one nearest inlet check valve of the inlet check valve system 274 and another nearest check valve of the outlet check valve system 276 when the piston 320 is at top dead center 313, less the clearance volume, as represented by Equation 1. VDisplacement = VOT− VPlay

[0067] V is involved V the displacement volume, V OTis the volume when the mechanically driven pump 226 is at top dead center 313, and V Spiel This is the playing volume. The passage volume and the displacement volume are composed of the volume of the hole represented by arrows 319.

[0068] In other words, the displacement volume or V Verdrängung The cross-sectional area of ​​a surface of the piston 320 (e.g., a piston area) multiplied by the displacement distance represented by the arrows 372. The displacement volume represented by 372 is the piston stroke, or the distance traveled by the piston. The cross-sectional area of ​​the piston 320 can be the area of ​​an inner surface of the upper inner wall 329. Verdrängung can also be represented by equation 2. VDisplacement = Piston * dHub

[0069] In this case, A Kolben the cross-sectional area of ​​the piston and d Hubthe path of the hub and the path of the displacement represented by arrows 372.

[0070] The displacement volume can be the volume of the space traversed by the piston stroke represented by arrows 372.

[0071] Energy can be transferred to the mechanically driven pump 226 via the nose 322, which is rigidly connected to a shaft 321. Specifically, energy can be transferred from the nose 322 to the piston 320. The energy of the nose 322 can be transmitted as a force that displaces the piston 320. The nose 322 and the shaft 321 can rotate either clockwise or counterclockwise to operate the mechanically driven pump 226. In the Fig. In the example shown in 3A-3D, the nose can rotate counterclockwise, as indicated by arrow 362. The nose 322 can be in direct physical contact with the piston 320 and transfer mechanical energy to the piston 320 when the nose 322 rotates. The shaft 321 can be the third rotating element 246 of Fig. 2A-2B can act, or the shaft 321 can be coupled in such a way that it is driven by the third rotating element 246.

[0072] The nose 322 can be an eccentric nose, in which a pivot point (e.g., the pivot point 338) for the nose 322 and the shaft 321 is offset from a center 339 of the nose 322. The pivot point 338 can be located approximately in the center of the shaft 321. Furthermore, the pivot point 338 can be located approximately in the center of a hole or passage in which the shaft 321 may be accommodated. For example, a hole 340 can be centered around the pivot point 338 and an axis 410. The eccentric rotation of the nose 322 can change the position of the piston 320 relative to the pump body 318 as the shaft 321 and the nose 322 rotate. The nose 322 can be arranged such that a surface of the nose 322 contacts the piston 320 during rotation.

[0073] The axis 410 can be a central axis for the hole 340, around which the hole 340 can be radially centered. The axis 410 can be a rotational axis for the shaft 321, around which the shaft 321 can rotate radially. The shaft 321 can be radially centered around the axis 410. The axis 410 can intersect the pivot point 338, where the pivot point 338 is an axial point collinear with the axis 410. The shaft 321 can be received in the hole 340 so that it is rigidly coupled to the nose 322. By changing the distance between a surface of the nose 322 that contacts the piston 320 and the pivot point 338, the position of the piston 320 relative to the pump body 318 can change, with the piston 320 being able to move back and forth and cyclically.

[0074] For example, a rotation of the shaft 321 in which a surface of the nose 322, which is in contact with the piston 320, is closer to the pivot point 338 and the axis 410, can move the piston 320 in the first direction shown by arrow 312 and closer to top dead center 313. Likewise, a rotation of the shaft 321 in which the surface of the nose 322, which is in contact with the piston 320, is farther from the pivot point 338 and the axis 410, can move the piston 320 in the second direction shown by arrow 314, closer to bottom dead center 315.

[0075] The rotation of the shaft 321 and the displacement of the piston 320 towards top dead center 313 can be carried out in the following order: Fig. 3B via Fig. 3C to Fig. It can be displayed in 3D. Shaft 321 can be positioned in... Fig. 3B begins, where the nose 322 contacts the piston 320 and pushes it to bottom dead center 315. The shaft 321 then rotates the nose 322 in one direction. The piston 320 is moved towards top dead center 313 by the rotation of the nose 322 and the extension of the spring 324, as shown in Fig. Figure 3C shows that the shaft 321 can rotate about the pivot point 338 and the axis 410 to rotate the nose 322. The direction of rotation of the nose 322 can be, for example, counterclockwise. The shaft 321 continues to rotate until the nose 322 and the spring 324 move the piston 320 to top dead center 313, as shown in Figure 3C. Fig. 3D representation. As the shaft 321 rotates further from top dead center 313 in the direction of rotation, the spring 324 is compressed and the piston 320 is moved towards bottom dead center 315.

[0076] Another example: The rotation of the shaft 321 and the displacement of the piston 320 towards bottom dead center 315 can be described in the following order: Fig. 3D over Fig. 3A to Fig. 3B can be shown. Wave 321 can be located at one point in Fig. 3D begins where the nose 322 contacts the piston 320 and pushes it to top dead center 313. The shaft 321 rotates the nose 322 in the direction of rotation. The piston 320 is moved towards bottom dead center 315 by the rotation of the nose 322 and the compression of the spring 324, as shown in Fig. Figure 3A shows that the shaft 321 can rotate about the pivot point 338 and the axis 410 to rotate the nose 322. The direction of rotation of the nose 322 can be, for example, counterclockwise. The shaft 321 continues to rotate until the piston 320, as shown in Fig. As shown in Figure 3B, the piston 320 has been moved to the bottom dead center 315. A further rotation of the shaft 321 from the bottom dead center 315 in the direction of rotation allows the spring 324 to expand, which moves the piston 320 towards the top dead center 313.

[0077] It is to be understood that the shaft 321 and the nose 322 can be rotated in a direction that corresponds to the direction in the Fig. The direction shown in 3A-3D is opposite to move the piston 320 towards or away from top dead center 313 and bottom dead center 315, as shown in the Fig. Figures 10A-10C show this. For example, shaft 321 and nose 322 can rotate clockwise instead of counterclockwise.

[0078] Fig. Figures 10A-10C show a schematic representation 1000 of the piston 320 and the nose 322 in various positions. The diagram 1000 shows a cross-section through the piston 320 and the nose 322. Fig. Figure 10A shows the piston 320 and the nose 322 in a first position 1010, the first position 1010 being in a bottom dead center (BDC) position in which the piston 320 is at bottom dead center 315. Fig. Figure 10B shows the piston 320 and the nose 322 in a second position 1020, where the second position 1020 is in a stroke position in which the piston 320 is between top dead center 313 and bottom dead center 315. In this example, the second position 1020 is during an expansion stroke. Fig. 10C shows the piston 320 and the nose 322 in a third position 1030, with the third position 1030 being in a TDC position in which the piston 320 is at TDC 313.

[0079] Between the first position 1010, the second position 1020 and the third position 1030 of Fig. In 10A-10C, shaft 321 rotates around the pivot point and axis 410 in a second direction, indicated by arrow 1050. The shaft 321 within it rotates the nose 322 in the second direction indicated by arrow 1050. The second direction indicated by arrow 1050 is the same as the first direction indicated by arrow 362 in the Fig. 3A-3D is displayed, in the opposite direction. The rotation of the shaft 321 in the second direction and the displacement of the piston 320 from bottom dead center 315 to top dead center 313 can be seen in the following order: Fig. 10A via Fig. 10B to Fig. 10C can be represented. Wave 321 can be in the first position 1010 in Fig. 10A begins, so that the nose 322 touches the piston 320 and pushes it to bottom dead center 315. The shaft 321 then rotates the nose 322 in the second direction, which is represented by the arrow 1050, so that the piston 320 is moved by the rotation of the nose 322 towards top dead center 313, as in the second position 1020 of Fig. Figure 10B shows that the shaft 321 can rotate about the pivot point 338 and the axis 410 to rotate the nose 322. The rotation of the nose 322 in the second direction allows a spring to extend, which contacts the piston 320 and exerts a spring load on it, thereby moving the piston 320 towards top dead center 313. For example, the spring 324 can move the piston 320 into the Fig. 10A-10C touch and load. The shaft 321 and the nose 322 can continue to rotate between the first position 1010 and the second position 1020, moving the piston 320 towards top dead center 313. The nose 322 and the spring move the piston 320 to top dead center 313, as in the third position 1030 of Fig. Figure 10C shows that from the third position 1030, a further rotation of the shaft 321 in the second direction can compress the spring 324 and move the piston 320 in the opposite direction to the bottom dead center 315.

[0080] The rotation of the shaft 321 in a direction opposite to the second direction shown by arrow 1050, and the displacement of the piston 320 from top dead center 313 towards bottom dead center 315 can be carried out successively by Fig. 10°C above Fig. 10B to Fig. Figure 10A shows that by rotating the shaft 321 and the nose 322 in a direction opposite to the second direction, the spring contacting the piston and exerting a load on it can be compressed. The compression of the spring allows the piston to move between the third position 1030 and the first position 1010. After rotating the nose 322 and moving the piston 320 to the first position 1010, a further rotation of the nose 322 in a direction opposite to the second direction allows the spring to extend and the piston 320 to move towards top dead center 313.

[0081] When considering the Fig. Figures 3A-3D clearly show that the configuration of the nose 322 is not limited and that the nose 322 can, for example, be a cam nose that is not circular. In this example, the pivot point 338 and the center 339 can occupy the same point, and the nose 322 can have a projection extending radially from the centers 338 and 339. The projection of the nose 322, acting as a cam nose, can change the position of the piston 320 relative to the pump body 318 as the nose 322 and the shaft 321 rotate. The contact between the projecting surfaces can push and move the piston 320 away from top dead center 313 and compress the spring 324. At the tip of the projection (e.g., at a point on the surface of the projection furthest from the pivot point 338), the piston 320 can be moved to bottom dead center 315.When contact with the surfaces of the projection is broken to touch other surfaces of the nose 322, the piston 320 can be raised towards the top dead center 313 and the spring 324 extended.

[0082] In Fig. Figure 9 briefly shows a scheme 900, which represents a cross-section of the piston 320, where the piston 320 is separated from other components of the mechanically driven pump 226. Fig. 3A-3D is separated. The piston 320 can be equipped with a bucket tappet. In other words, the piston 320 can be a bucket tappet. The piston 320 comprises a top part 902 and a piston side wall 906. The piston 320 also has a bottom 904 and a cavity 920. The cavity 920 extends from the bottom 904 to a surface of the upper inner wall 329. The top part 902 of the piston 320 has a thickness specified as 912 and a piston sleeve length specified by arrows 376. The piston sleeve 328 is the portion of the side wall 906 of the piston that lies below the upper inner wall 329. The piston sleeve 328 can help to keep the piston 320 in the cylindrical cavity or another cavity, such as the one indicated by arrows 319 in Fig. The hole marked 3A-3D remains aligned. When the piston 320 is aligned with a cavity via the piston jacket 328, it can lock into the cavity or other features of the pump body 318. Fig. Avoid 3A-3D. The piston sleeve 328 can have a length indicated and represented by arrows 376. The length of the piston sleeve 328 indicated by arrows 376 can be at least 81% and at most 84% of the diameter of the piston 320. The diameter of the piston 320 can be indicated and represented by arrows 374. In an example, the clearance between the piston 320 and the hole of the pump body 318, indicated by arrows 319 in the Fig. 3A-3D is displayed, the difference must be at least 0.04 millimeters and less than 0.12 millimeters. Furthermore, the piston jacket 328 can be connected to the bore (indicated by arrows 319 in the) at any point during the pump stroke. Fig. (marked 3A-3D) of the pump body 318 in the Fig. 3A-3B must be coupled for at least a predetermined part of the pump stroke (e.g., 4 / 3). The piston 320 in Fig. 9 is shown relative to the reference axes 301.

[0083] The piston 320 can be centered about a central axis 910. More precisely, the piston 320 can be centered radially about the central axis 910, the central axis 910 being coaxial with a centerline of the piston 320 and perpendicular to the upper inner wall 329. A spring load from the spring 324 of Fig. 3A-3D can be applied to a surface 942 of the piston 320. A surface of the upper inner wall 329 can encompass the area 942 of the piston 320 where the spring load is applied, and the area can be centered around the central axis 910 and / or the centerline of the piston 320. The surface encompassing the area 942 can be raised at a distance from one or more other surfaces of the upper inner wall 329. The area where the spring is loaded can have a threshold distance corresponding to a diameter or a width. The threshold distance is represented by arrows 940. For example, the area 942 can have an elliptical, approximately circular shape, and the limit distance represented by arrows 940 can be a diameter. The threshold distance represented by arrows 940 can be approximately 8 mm, with "approximately" varying between 1 mm greater or lesser than the value of the threshold distance.The centrally arranged spring of spring 324 can facilitate the displacement of the piston 320 and the rotation of the nose 322.

[0084] Back to the Fig. 3A-3D: The pump body 318 comprises at least a first opening and a second opening. In particular, the pump body 318 may have one or more inlet openings, such as a pump inlet opening 332. Likewise, the pump body 318 comprises one or more outlet openings, such as a pump outlet opening 334. The pump inlet opening 332, the pump outlet opening 334, and / or other openings of the pump body 318 may be incorporated into the pump body 318. Liquid and gaseous substances can flow into and out of the pressure chamber via the pump inlet opening 332 and the outlet opening 334. Liquid and gaseous media, such as lubricants or air, can flow into and out of the pressure chamber 336. The pump inlet opening 332 and other inlet openings to the pressure chamber 336 can fluidically couple the inlet check valve system 274.Similarly, the pump outlet port 334 and other outlet ports of the pressure chamber 336 can fluidically couple the outlet check valve system 276. In other words, the inlet port 332 can be fluidically connected to the inlet check valve system 274, and the outlet port 334 to the outlet check valve system 276. The fluid couplings 310 can bring the inlet check valve system 274 and the outlet check valve system 276 into fluidic connection with the pump inlet port 332 and the pump outlet port 334, respectively. The fluid couplings 310 can be fluid passages or fluid lines, and the pump body 318 can include one or more of the fluid couplings 310. The inlet opening 332 and the outlet opening 334 can be through holes drilled with their axis tangential to the hole (e.g. the central cavity) of the pump body 318 shown by the arrows 319.

[0085] The pump inlet port 332 and the pump outlet port 334 are located outside the piston stroke of the piston 320, as indicated by arrows 372. The piston 320 can be prevented from blocking and sealing the pump inlet port 332 or the pump outlet port 334, and the piston jacket 328 can be prevented from acting as a guillotine valve.

[0086] When the piston jacket 328 functions as a guillotine valve, it can seal the inlet port 332, the outlet port, and other ports that may be connected to the pressure chamber 336. For example, when the piston jacket 328 comes into contact with the surface 326, it can seal inlet or outlet ports, such as the inlet port 332 or the outlet port 334. In such an arrangement, it is possible that the first part of a stroke will not deliver any fluid to the outlet port because the piston jacket 328 closes and acts as a guillotine valve. In contrast to a configuration where the piston jacket 328 is a guillotine valve, the inlet port 332 and the outlet port 334 are not blocked, so that the inlet port 332 can allow fluid to flow into the pressure chamber 336 during the beginning of a pressure drop and the outlet port 334 can receive fluid during the end of a pressure rise in the pressure chamber 336.Positioning the pump inlet opening 332 and the pump outlet opening 334 outside the stroke shown by the arrows 372 can increase the volumetric efficiency of the pump 226 compared to another pump with the guillotine valve solution.

[0087] The inlet check valve system 274 comprises at least one inlet port 342 and one inlet check valve 344. The inlet port 332 is located downstream of the inlet port 342. In other words, fluid can flow from the inlet port 342 to the inlet port 332. The inlet check valve 344 can seal the inlet port 332 against the inlet port 342. In other words, the inlet check valve 344 can create a fluid-tight seal that prevents fluid flow from the inlet port 332 to the inlet port 342. Additionally, the inlet check valve 344 can create an airtight seal that prevents the flow of gaseous fluid from the inlet port 332 to the inlet port 342. The inlet check valve 344 can also be located within the inlet port 342.The inlet check valve 344 is configured such that a pressure drop or differential pressure below a threshold in the pressure chamber 336 can open the inlet check valve 344. In other words, the inlet check valve 344 can be opened by suction from the pressure chamber 336 and the pump inlet port 332. The inlet check valve 344 is configured to be normally closed, so that under normal pressure and other force conditions (e.g., when the pump 226 is not running or is in stroke mode), the valve is closed by gravity.

[0088] The outlet check valve system 276 comprises at least one outlet port 352 and one outlet check valve 354. The outlet port 352 is located downstream of the outlet port 334. In other words, fluid can flow from port 334 to outlet port 352. The outlet check valve 354 can fluidically seal the outlet port 334 against the outlet port 352. In other words, the outlet check valve 354 can create a fluid-tight seal that prevents fluid flow from outlet port 352 to port 334. Furthermore, the outlet check valve 354 can create an airtight seal that prevents fluid flow from outlet port 352 to port 334. Additionally, the outlet check valve 354 can be located within the outlet port 352.The outlet check valve 354 is configured such that an increase in pressure or differential pressure above a threshold value in the pressure chamber 336 can open the outlet check valve 354. In other words, the outlet check valve 354 can be opened by a blowing force from the pressure chamber 336 and the pump outlet port 334. The outlet check valve 354 is configured to be normally closed, so that under normal pressure and other force conditions (e.g., when the pump 226 is not running or is in a stroke), the valve is closed by gravity.

[0089] In Fig. Figure 8 shows a schematic representation 800 of a configuration of the pump 226 in which the inlet check valve 344 and the inlet port 342 are located and embedded in the side wall 330 of the pump body 318. Likewise, the outlet check valve 354 and the outlet port 352 are located / embedded in the side wall 330. The inlet port 342 and the outlet port 352 extend through the side wall 330. The inlet port 342 and the outlet port 352 can be through holes and can be drilled. The inlet port 342 and the outlet port 352 can be centered about one axis or a plurality of axes, the axis(es) extending radially or tangentially to the hole (e.g., the central cavity) of the pump body 318 shown by the arrows 319.

[0090] The integration of the inlet port 342, the inlet check valve 344, other components of the inlet check valve system 274, the outlet port 352, the outlet check valve 354, and other components of the outlet check valve system 276 into the pump 226, particularly into the pump body 318 and the side wall 330, allows the pump 226 to be more compact compared to other pump configurations that have inlet and outlet check valve systems located outside a pump body. The compactness of the pump 226 can enable its use in smaller packing areas and with smaller packing volumes. Furthermore, the pump's characteristics, such as...Volume, fluid flow and pressure can be adjusted by changing the machining parameters for holes and other volumes of the pump body 318, which can accommodate or be connected to the inlet port 342, the inlet check valve 344, other components of the inlet check valve system 274, the outlet port 352, the outlet check valve 354 and other components of the outlet check valve system 276.

[0091] In the Fig. 3A and Fig. Figure 3B shows the piston 320 in a downward direction (e.g., the second direction) of arrow 314 towards bottom dead center 315. The movement of the piston 320 towards bottom dead center 315 can be represented by arrow 380. By rotating the nose 322, the piston 320 can be pushed downwards in the direction of arrow 380, whereby the piston 320 can compress the spring 324. As the piston 320 moves in the direction of arrow 380 and compresses the spring 324, the pressure in the chamber 336 can rise above one or more threshold values, so that gravity closes the inlet check valve 344 and a blowing force from the pressure opens the outlet check valve 354. Through the opening of the outlet check valve 354, the fluid can exit the pump through an outlet port (e.g., the outlet port 352).The positive pressure difference in the pressure chamber 336 compared to the closed environment 303 can expel fluid through the pressure chamber 336, through the pump outlet 334, and out of the outlet 352. The movement of the gaseous and / or liquid fluids from the pressure chamber through the pump outlet 334 and out of the outlet 352 can be represented by arrows 382.

[0092] In Fig. In Figures 3C-3D, the piston 320 is shown moving upwards (e.g., the first direction) in the direction of arrow 312 towards top dead center 313. The movement of the piston 320 towards top dead center 313 can be represented by arrow 390. As the nose rotates, spring 324 can extend, and the spring force of spring 324 can push piston 320 upwards in the direction of arrow 390. The pressure in the pressure chamber 336 can fall below one or more threshold values, allowing the inlet check valve 344 to be opened by suction and the outlet check valve 354 to be closed by gravity. With the inlet check valve 344 open, fluid can enter the pump through an inlet port (e.g., inlet port 342). The negative pressure difference in the pressure chamber 336 compared to the closed environment 303 can drive fluid into the pressure chamber 336 via the inlet opening 342 and the inlet opening 332 by suction.The movement of the gaseous and / or liquid fluids into the pressure chamber through the inlet opening 342 and out of the inlet opening 332 can be represented by arrows 392.

[0093] In the Fig. Figure 3A-3D depicts an operating sequence in which the mechanically driven pump 226 moves back and forth between different positions. In the sequence of Fig. In 3A-3D, the piston 320 moves radially with respect to the pivot point 338 and the nose 322 in a clockwise direction, as indicated by the arrow 362. The sequence begins with Fig. 3D and then goes sequentially from Fig. 3A via Fig. 3B to Fig. 3C.

[0094] Fig. Figure 3D shows the piston 320 in its fully extended position relative to the pump body 318. One end of the spring 324 is in direct contact with the pump body 318, and the other end of the spring 324 is in direct contact with the upper inner wall 329 of the piston 320. The spring 324 pushes directly against the piston 320 to force it against the nose 322. The spring 324 pushes the piston 320 away from the pump body 318, as indicated by arrow 390, to create a suction that draws the lubricant into the pressure chamber below the piston 320, as indicated by arrow 392. At top dead center 313, however, the piston 320 can no longer move in the direction indicated by arrow 312, preventing an increase in volume and thus interrupting the suction into the pressure chamber 336. At top dead center 313, the piston 320 and the pressure chamber below the piston 320 can experience a dynamic pressure due to the movement of the fluid, which increases the pressure.Additionally or alternatively, preventing an increase in the volume of pressure chamber 336 can cause the pressure within it to equalize with or approach another pressure at the inlet opening 342. At OT 313, 320, the volume of pressure chamber 336 no longer increases and / or the dynamic pressure of the fluid can cause the pressure in pressure chamber 336 to rise above a first pressure threshold. Above the first pressure threshold, the suction force from pressure chamber 336 can be reduced to less than gravity, thereby closing the inlet check valve 344. Closing the inlet check valve 344 can prevent further fluid from flowing into pressure chamber 336. When the piston 320 stops its movement at top dead center 313, some of the fluid from the pressure chamber 336 can flow into one or more volumes between the inlet port 332 and the inlet check valve 344, as shown by arrow 398.

[0095] Fig. Figure 3A shows the piston 320 moving away from top dead center 313 and towards bottom dead center 315, as indicated by arrow 380. The spring 324 can begin to compress due to the movement and force of the piston 320. When the spring 324 is compressed, the volume of the pressure chamber 336 decreases. The movement of the piston 320 towards the pump body 318, more precisely towards the surface 326, as indicated by arrow 380, creates a higher pressure in the pressure chamber 336. When the piston 320 moves into the Fig. When the piston 320 is in the position shown in 3A, the pressure in the pressure chamber 336 has risen to or above the first threshold value, so that the suction force on the inlet check valve 344 becomes less than gravity, causing the inlet check valve 344 to close by gravity. When the piston 320 is in the Fig. When the piston 320 is in the position shown in 3A, the pressure in the pressure chamber 336 has risen to or above a second threshold, so that a blowing force is exerted on the outlet check valve 354. When the piston 320 is in the position shown in Fig. When the piston is in the position shown in Figure 3A, the pressure in the pressure chamber 336 has risen to or above a third threshold value, such that the blowing force is greater than the force of gravity acting on the outlet check valve 354. The outlet check valve 354 can then be opened, so that the positive differential pressure of the pressure chamber 336 and the movement of the piston 320 force the fluid flow through the outlet port 334, the outlet check valve 354, and the outlet port 352 out of the pressure chamber 336, as indicated by arrows 382.

[0096] Fig. Figure 3B shows piston 320 in the TDC position, where piston 320 is at bottom dead center 315. The flow through the outlet port 352 can be reduced to almost zero. An example shows how fluid flows out of the outlet port 352 via arrows 382. The pressure in the pressure chamber 336 can approach or decrease the pressure at the outlet port 352 when piston 320 is at bottom dead center 315. The pressure in the pressure chamber 336 can fall below the third pressure threshold. Below the third threshold, the blowing force to the outlet port 352 can be reduced to less than gravity, thus closing the outlet check valve 354. Closing the outlet check valve 354 can prevent further backflow of fluid into the pressure chamber 336, e.g., from the outlet port 352.When the piston 320 ends its movement at bottom dead center 315, some residual fluid from the volumes between the outlet opening 334 and the outlet check valve 354 can flow back into the pressure chamber 336, as shown by arrow 388.

[0097] As the nose 322 continues to rotate, the piston 320 can be moved in the first direction indicated by arrow 312 via the spring 324 and the surface contact with the nose 322. Fig. Figure 3C shows the piston 320 between the TDC and BDC positions, with the piston 320 located between BDC 315 and TDC 313. When the piston 320 is moved away from the pump body 318, more precisely from the surface 326 (see arrow 390), a lower pressure is created in the pressure chamber 336. When the piston 320 is in the Fig. When the piston 320 is in the position shown in 3C, the pressure in the pressure chamber 336 has dropped below the third pressure threshold, so that the blowing force acting on the outlet check valve 354 becomes less than the force of gravity, causing the outlet check valve 354 to close by gravity. When the piston 320 is in the Fig. When the piston 320 is in the position shown in 3C, the pressure in the pressure chamber 336 has dropped below a second threshold value, so that a suction force is exerted on the inlet check valve 344. When the piston 320 is in the position shown in Fig. When the piston is in the position shown in Figure 3C, the pressure in the pressure chamber 336 has dropped below a first threshold value, so that the suction force is greater than the force of gravity acting on the inlet check valve 344. The inlet check valve 344 can then be opened, so that the negative differential pressure of the pressure chamber 336 and the movement of the piston 320 draw a fluid flow through the inlet port 334, the outlet check valve 354 and the outlet port 352 into the pressure chamber 336, as indicated by arrows 392.

[0098] The piston 320 can be removed from the in Fig. 3C position shown up to the one in Fig. The OT position shown in 3D will continue to rise.

[0099] Fig. Figure 4 shows a view 400 of the mechanically driven pump 226. The mechanically driven pump 226 in Fig. Figure 4 is shown approximately to scale with approximate positioning. The pump 226 has a height parallel to the first axis 404, the height of which can be represented by arrows 462. The first axis 404 can be one of several other axes to which the height of the pump body 318 can be parallel. Furthermore, the height of the pump body 318 can be parallel to a second axis 406 and a third axis 408. In other words, the first axis 404, the second axis 406, and the third axis 408 can be parallel to each other. The first axis 404, the second axis 406, and the third axis 408 can be arranged perpendicular to the z-axis of the reference axes 301.

[0100] Additionally, the components of the inlet check valve 344 and the outlet check valve 354 are shown in exploded view 400. The components of the inlet check valve 344 extend from the pump body 318 along the second axis 406 and are centered about it. Similarly, the components of the outlet check valve 354 extend from the pump body 318 along the third axis 408 and are centered about this axis. For clarity, the components of the inlet check valve 344 can be enclosed by a plurality of first dashed lines 412 arranged in a rectangle. Likewise, for clarity, the components of the outlet check valve 354 can be enclosed by a plurality of second dashed lines 414 arranged in a rectangle. The inlet check valve 344 and the outlet check valve 354 can be ball check valves.The inlet check valve 344 and the outlet check valve 354 are springless check valves, meaning that neither the inlet check valve 344 nor the outlet check valve 354 has any springs, such as preload springs. The inlet check valve 344 and the outlet check valve 354 are vertically oriented, so that they are radially centered about vertical axes. When centered about vertical axes, gravity can close the inlet check valves 344 and 354 and the outlet check valves. A force opposing gravity, such as hydraulic pressure, can open the inlet check valve 344 or the outlet check valve 354.

[0101] The nose 322 is centered about an axis 411. The axis 411 can run parallel to the axis 410. The hole 340 is radially centered about the axis 410. The hole 340 can contain a groove 430. A shaft or other rotating element, such as the shaft 221 in Fig. 3A-3D and Fig. 8, can be rigidly connected to the nose 322 via the groove. For example, the shaft 221 can have a radially outwardly extending projection or extension that fits into the groove 430 and is connected to it via a tongue-and-groove arrangement.

[0102] The pump body 318 can have a first hole 422, a second hole 424, and a third hole 426. The first hole 422 can be centered around the first axis 404 and / or curved radially around it, and the first hole 422 can be the one indicated by the arrows 319 in the Fig. 3A-3D and 8 depicted holes. Likewise, the second hole 424 can be centered about the second axis 406 and / or bent radially about it, and the third hole 426 can be centered about the third axis 408 and / or bent radially about it. The first hole 422, the second hole 424, and the third hole 426 can have a cylindrical shape and volume. The second hole 424 and the third hole 426 can each be part of a check valve system, such as the inlet check valve system 274 and the outlet check valve system 276 of Fig. 2A-3D. Likewise, the second hole 424 and the third hole 426 can be part of the inlet opening 342 of the Fig. 3A-3D or the outlet opening 352, or at least be in fluid communication with it. Furthermore, the second hole 424 can be brought into fluid communication with the first hole 422 via the inlet check valve 344 and one or more openings to the first hole 422. Likewise, the third hole 426 can be brought into fluid communication with the first hole 422 via the outlet check valve 354 and one or more openings to the first hole 422. For example, the second hole 424 can be connected to the pump inlet opening 332 of the Fig. 3A-3B and Fig. 8 can optionally be brought into fluid contact with the first hole 422, e.g., when the inlet check valve 344 is open. Likewise, the third hole 426 can be connected via the outlet opening 334 of the Fig. 3A-3B and 8 can optionally be brought into fluid contact with the first hole 422, for example when the outlet check valve 354 is open.

[0103] The first hole 422 can accommodate the piston 320 and the spring 324. Additionally, the first hole 422 can accommodate an adapter plate 432. The adapter plate 432 can be clamped between the piston 320 and the spring 324 along the first axis 404. The adapter plate 432 can be in contact with the piston 320 and the spring 324. The adapter plate 432 can be positioned perpendicularly between the piston 320 and the spring 324. The inlet check valve 344 can be located in the second hole 424, and the outlet check valve 354 in the third hole 426.

[0104] The adjusting plate 432 can keep the spring 324 centered in the piston 320. In other words, the adjusting plate 432 can prevent the spring 324 from moving out of the center of the first axis 404 and / or the centerline of the piston 320. Additionally, the adjusting plate 432 can exert a spring load from the spring 324 onto the center of the piston 320. The spring load can be applied via the adjusting plate 432 to a region of the piston 320, e.g., an elliptical region. The region for the applied contact load can, for example, be an ellipse located on a region of the upper inner wall 329 of Fig. 3A-3D is located and the arrows 940 from Fig. The threshold spacing shown in Figure 9 is present. The adjustment plate 432 can touch and abut the area with the threshold spacing shown by arrows 940. The surface can be the surface 942 of the upper inner wall 329 of Fig. 9. The centrally arranged spring load by the spring 324 and the adjusting plate 432 can facilitate the displacement of the piston 320 and the rotation of the nose 322.

[0105] The inlet check valve 344 can comprise a first ball 442, a first plug 444, and a first retaining ring 446. The first ball 442, the first plug 444, and the first retaining ring 446 can be radially centered about the second axis 406. The first ball 442 is an inner ball of the inlet check valve 344, and the first ball 442 can be an approximately spherical rolling bearing. The first ball 442 can, for example, be a 17 / 32" rolling element of a ball bearing. The first plug 444 can have a partially cylindrical and partially frustoconical shape. A first part of the first plug 444, which is partially frustoconical, can have surface contact with the first ball 442. Likewise, a second part of the first plug 444, which has a cylindrical shape, can be arranged above the first part. The first retaining ring 446 can be a retaining ring with inwardly or inwardly directed ears, e.g.around an internal retaining ring, around which a groove may be arranged radially. The first retaining ring 446 may be a snap ring. The first plug 444 may have a first groove 448, wherein the first groove 448 is arranged axially between the first section and the second section of the first plug 444 with respect to the second axis 406. The first groove 448 may extend radially inward toward the center of the first plug 444, for example, radially inward toward the second axis 406. The first retaining ring 446 may be fitted into the first groove 448 such that a physical connection is formed. The first retaining ring 446 may physically couple the first plug 444 to the second hole 424, for example, via a tongue-and-groove arrangement, in which the first retaining ring 446 is a tongue that physically couples with and is fitted into another groove of the pump body 318.The other groove can extend radially outwards into the inner surfaces and side walls of the pump body 318 and curve around the second hole 424.

[0106] It is understandable that the in Fig. The configuration of pump 226 and inlet check valve 344 shown in Figure 4 is not limited and may also include fewer parts. For example, the inlet check valve 344 may contain different or fewer parts, including a minimum set of components that constitute a check valve. In these examples, the inlet check valve 344 may include a different fastening element than the first retaining ring 446. For example, the inlet check valve 344 may include a different fastening element than the first retaining ring 446 for securing the first plug 444, such as a different retaining ring, which may have a simpler configuration. Another example is that the inlet check valve does not have a closure separate from other components of the inlet check valve 344. A feature or component of the inlet check valve 344, such as...In another configuration, the first plug 444 may be physically coupled to the pump body 318 via the second hole 424 or may have a fastening feature that can be attached to it. In this or another example, the pump body 318 may have or be coupled to one or more other fastening elements that may extend radially inward or in another direction inward toward the second hole 424. The other fastening elements may be attached to and seal with an element of the inlet check valve 344. The one or more other fastening elements may be attached to a feature or component of the inlet check valve 344 via a groove, such as the first plug 444 via the first groove 448.

[0107] When connected to the pump body 318 via the first retaining ring 446, the first retaining ring 446 prevents displacement or other movement of the first plug 444 without an intentional force exceeding a threshold value. An intentional force exceeding the threshold value can remove the first plug 444 and the first retaining ring 446 from the second hole 424. The first plug 444 can form a fluid-tight seal with the side walls and surfaces of the pump body 318 surrounding the second hole 424, thus ensuring a fluid seal that is at least fluid-tight and prevents fluid from escaping the second hole 424. Similarly, the seal created by the first plug 444 between the side walls and surfaces of the pump body 318 surrounding the second hole 424 can be airtight, thus preventing air or other gases from escaping the second hole 424.

[0108] The exhaust check valve 354 can comprise a second ball 452, a second plug 454, a third plug 456, and a second retaining ring 458. The second ball 452, the second plug 454, the third plug 456, and the second retaining ring 458 can be radially centered about the third axis 408. The second ball 452 is an inner ball of the exhaust check valve 354, and the second ball 452 can be an approximately spherical rolling bearing. The second ball 452 can, for example, be a 17 / 32" rolling element of a ball bearing. The second plug 454 can be partially frustoconical. The third plug 456 can have a partially cylindrical shape. A second plug 454 can have surface contact with the second ball 452. The third plug 456 can be located above the second plug 454 and be in surface contact with it.The second retaining ring 458 can be a retaining ring configuration with inwardly or inwardly directed ears, such as an internal retaining ring around which a groove may be arranged radially. The second retaining ring 458 can be a snap ring. The third plug 456 can have a second groove 460. The second groove 460 can extend radially inward toward the center of the third plug 456, for example, radially inward toward the third axis 408. The second retaining ring 458 can be fitted into the second groove 460 such that a physical connection is formed. The second retaining ring 458 can physically couple the third plug 456 to the third hole 426, for example, via a tongue-and-groove arrangement in which the second retaining ring 458 is a tongue that physically couples with and is fitted into another groove of the pump body 318.The other groove can extend radially outwards into the inner surfaces and side walls of the pump body 318, which bulge around the third hole 426.

[0109] When physically coupled via the second retaining ring 458, the second retaining ring 458 can prevent displacement or other movement of the third plug 456 without an intentional force exceeding a threshold value. Intentional forces exceeding the threshold value can remove the second retaining ring 458 and the third plug 456 from the third hole 426. The second plug 454 and the third plug 456 can form a fluid-tight seal against the side walls and surfaces of the pump body 318 surrounding the third hole 426, thus providing multiple fluid seals that are at least fluid-tight and prevent fluid from escaping the third hole 426. Likewise, the seals formed by the second plug 454 and the third plug 456 against the side walls and surfaces of the pump body 318 surrounding the third hole 426 can be airtight, thus preventing the escape of air or other gases from the third hole 426.

[0110] A first gap, represented by a plurality of arrows 472, can exist between the first sphere 442 and the first plug 444. The first sphere 442 can be moved upwards by a negative differential pressure, which increases the pressure in a first space between the first sphere 442 and the first hole 422. More precisely, the first sphere 442 can be moved upwards by a negative differential pressure below a first threshold, creating a suction force greater than gravity. This suction force, greater than gravity, can move the first sphere 442 upwards, allowing fluid to flow from the second hole 424 to the first hole 422. The first gap can decrease in size until the first sphere 442 contacts the first plug 444.

[0111] A second gap, represented by a plurality of arrows 474, can exist between the second plug 454 and the third plug 456. The second sphere 452 can be moved upwards by a positive differential pressure, which increases the pressure in a second space between the second sphere 452 and the first hole 422 above a second pressure threshold, thereby exerting a blowing force on the second sphere 452 that is greater than the force of gravity. The second sphere 452 and the second plug 454 can be displaced upwards, allowing fluid to flow from the first hole 422 to the third hole 426. The second gap can decrease in size until the second plug 454 touches and seals the third plug 456.

[0112] It is understandable that the in Fig. The configuration of pump 226 and outlet check valve 354 shown in Figure 4 is not limited and may also include fewer parts. For example, the outlet check valve 354 may include different or fewer parts, including a minimum number of components required to be a check valve. In these examples, the outlet check valve 354 may include a different fastening element than the second retaining ring 458. For example, the outlet check valve 354 may secure the second plug 454 to the pump body 318, for example, by means of a different retaining ring, which may have a simpler configuration. Another example is that the outlet check valve 354 does not have a closure separate from other components of the outlet check valve 354. A feature or component of the outlet check valve 354, such asOther configurations of the third plug 456 may be physically coupled or have a fastening feature. The fastening feature may secure the feature or component of the outlet check valve 354 to the pump body 318 via the third hole 426. In this or another example, the pump body 318 may have or be coupled to one or more other fastening features that may extend radially inward or in another direction inward toward the third hole 426. The other fastening features may be attached to and seal against an element of the outlet check valve 354. One or more of the other fastening features may be attached to a groove of a feature or component of the outlet check valve 354, for example, a groove of the second plug 454 or the third plug 456.In this or another example, the outlet check valve 354 may also contain only a single plug instead of two plugs, e.g. only the third plug 456.

[0113] The minimum differential pressure required to move either the first ball 442 or the second ball 452, whether a negative differential pressure for suction or a positive differential pressure for blowing, can be determined by an equation. More precisely, the force can be determined by dividing the weight of the ball by the cross-sectional area of ​​a hose or other fluid passage, together with the hydrostatic pressure of the pump. The hose or hoses can be located inside the pump body 318. The minimum differential pressure can be represented by Equation 3. ΔP=Wb / (Ah)+HH=(m*g) / (Ah)+HH

[0114] ΔP is the minimum differential pressure required to move the ball and open a check valve. W b ΔP is the weight of an inner ball of a check valve, e.g., the first ball 442 or the second ball 452. HH is the hydrostatic head. When determining ΔP for the ball of the inlet check valve 344, HH can be the total dynamic suction head (TDSH) on the suction side of the pump 226, e.g., at the inlet port 342. When determining ΔP for the ball of the outlet check valve 354 and the hydrostatic head, it can be the static head (SDH) on the outlet side of the pump 226, e.g., at the outlet port 352. h is the cross-sectional area of ​​a hose. For the ball of the inlet check valve 344, A can be hThe cross-sectional area of ​​a hose or other fluid passage that fluidically connects the inlet check valve 344 to the pump inlet opening 332. For the ball of the outlet check valve 354, A h The cross-sectional area of ​​a hose or other fluid passage connected to the pump outlet opening 334 and the outlet check valve 354. m can be the mass of the sphere. g can be the acceleration due to gravity.

[0115] This is what the pump looks like Fig. Figures 1-4 and 8-9 describe a pump comprising: a spring; a piston configured to receive the spring; a pump body with a cylindrical cavity configured to receive the spring; and a first and second check valve, which are springless and closed by gravity. The first inlet check valve is configured to be connected to an inlet port, opens due to suction and pressure drop during an expansion stroke of the piston, and draws fluid into the cylindrical cavity. The second inlet check valve is an outlet check valve configured to be connected to an inlet port, opens due to a blowing force and pressure rise during a compression stroke of the piston, and expels fluid from the cylindrical cavity.

[0116] The disclosure also provides a mounting for a lubricant pump, comprising: a nose mounted on and driven by a shaft, a piston in contact with the nose, a spring acting on the piston, an inlet check valve positioned in an inlet port, and an outlet check valve positioned in an outlet port, wherein the inlet check valve and the outlet check valve do not include preload springs and are positioned vertically in a normally closed position due to gravity acting on the inner balls of the inlet check valve and the outlet check valve. In a first example of the system, which further comprises a pump body, a cylindrical hole in the pump body is configured to receive the piston.In a second example of the system, which optionally includes the first example and also comprises a pump body, the inlet check valve is positioned in a first hole of the pump body and seals it fluidically, the outlet check valve is positioned in a second hole of the pump body and seals it fluidly, and the first hole and the second hole are arranged vertically with openings that are open to a surface perpendicular to a vertical axis of the pump.In a third example of the system, optionally comprising one or both of the first and second examples, the inlet port connects a first port and the outlet port a second port in fluid communication with a pressure chamber containing the spring and upon which the piston acts. The first port and the second port are located outside a piston stroke, thus preventing the piston from blocking either the first or the second port. In a fourth example of the system, optionally comprising one or more, or each of the first through third examples, the inlet port comprises the first port and the outlet port comprises the second port. In a fifth example of the system, optionally comprising one or more, or each of the first through fourth examples, the inlet port is located in a side wall of a pump body, and the first port extends through the side wall of the pump body.In a sixth example of the system, optionally comprising one or more or each of the first five examples, the outlet opening is located in a side wall of a pump body, and the second opening extends through the side wall of the pump body. In a seventh example of the system, optionally comprising one or more or each of the first six examples, the pump is a flushing pump with a suction side in fluid communication with a dry sump. In an eighth example of the system, optionally comprising one or more or each of the first seven examples, the piston includes a piston jacket. In a ninth example of the system, optionally comprising one or more or each of the first eight examples, the piston jacket has a length less than the diameter of the piston, the length being at least 81% and at most 84% of the diameter.In a tenth example of the system, which optionally includes one or more or each of the first through ninth examples, the nose is a cam nose. In an eleventh example of the system, which optionally includes one or more or each of the first through tenth examples, the nose is an eccentric nose. In a twelfth example of the system, which optionally includes one or more or each of the first through eleventh examples, the shaft is driven by a mechanical system lubricated by the pump.

[0117] The disclosure also provides support for a vehicle transmission, comprising: a self-priming pump, comprising: an eccentric nose, a spring, a piston configured to receive the spring and interact with the eccentric nose, a pump body having a cylindrical hole configured to receive the spring, an inlet check valve positioned in an inlet port, and an outlet check valve positioned in an outlet port, wherein the inlet check valve and the outlet check valve have no preload springs and are positioned vertically in a normally closed position due to gravity acting on internal balls of the inlet check valve and the outlet check valve.In a first example of the system, the eccentric nose is rigidly coupled to a rotating element of a mechanical system, the mechanical system drives the eccentric nose via the rotating element, and the mechanical system receives targeted lubrication through a lubrication system that includes the self-priming pump.

[0118] In Fig. Figure 5 shows a method 500 for operating a mechanically driven pump. The method of Fig. 5 can be equipped with a mechanically driven pump, such as the one in Fig. 2-4 and Fig. The mechanically driven pump 226 shown in Figures 8-9 can be used. Furthermore, the pump driven by the method 500 can be a flushing pump that draws gaseous and liquid media from a dry sump on the suction side. A nose of the mechanically driven pump can be an eccentric nose (e.g., an eccentric nose), such as the nose 322 in Figure 8-9. Fig. 3A-4 and Fig. 8. However, the nose can also be a cam nose (e.g., a cam nose). In method 500, the mechanically driven pump is moved back and forth between an expansion and a compression stroke.

[0119] In 502, method 500 rotates a shaft and a nose to supply a pump with driving force, as in the Fig. 2A-4 and 8-9 are shown. The shaft can be rotated via an output from a rotating shaft in a gearbox, transmission, or other device. More precisely, the shaft can be driven by a mechanical drive from one or more mechanical systems, such as a gear set, the gearbox, or other device. The shaft can be coupled to be driven by a trigger, the trigger being configured to be driven by a mechanical system, such as a mechanical system 216 of the Fig. 2A-2B. Procedure 500 continues with 504. The mechanical system that drives the mechanically driven pump may have one or more components that are lubricated by a lubrication system to which the pump belongs.

[0120] In procedure 500, an expansion stroke is performed for the mechanically driven pump in instrument 504. During the suction stroke, the stroke (e.g., the distance between a contact surface and the axis of rotation) of the nose decreases, and a spring exerts a force to move a piston away from a body (e.g., a pump body) of the mechanically driven pump. The nose can be eccentric, such as nose 322 in instrument 504. Fig. 3A-4 and Fig. 8. The piston in question could be piston 320 from Fig. 3A-4 and Fig. It could be 8-9. The spring could be spring 324 from Fig. 3A-4 and Fig. 8. When the piston is moved away from the housing of the mechanically driven pump, the area between the piston and the housing of the mechanically driven pump can increase, thereby reducing the pressure in that area. This area can be a pressure chamber, such as the pressure chamber of 336 in Fig. 3A-3D and Fig. 8. When the piston is moved away from the housing of the mechanically driven pump, the inlets of the mechanically driven pump also open and the outlets of the mechanically driven pump close. Below a pressure threshold, one or more inlets can be closed via at least one first inlet check valve, such as the inlet check valve 344 in Fig. 3A-4 and Fig. 8, can be opened. The first check valve is in fluid communication with the inlets and the area between the piston and the housing and, when open, allows fluid communication between the inlet and the area within it. Likewise, below the pressure threshold, one or more outlets can be opened via at least one second outlet check valve, such as the outlet check valve 354 of the Fig. 3A-4 and Fig. 8, closed. The second check valve can be in fluid contact with the outlets and the area between the piston and the body and, when closed, prevents fluid contact between the outlet and the area within it. The inlets opened via the check valve can include at least one inlet port, such as inlet port 342 in Fig. 3A-3D and Fig. 8. The outlets closed via the check valve may include at least one outlet opening, such as outlet opening 352 in Fig. 3A-4 and Fig. 8. The combination of open inlet ports and low pressure under the piston drives allows fluid to flow into the mechanically driven pump. During the expansion stroke, the piston can be moved, and the area can continue to expand until the piston is moved to top dead center. Upon reaching top dead center, the expansion stroke and procedure 504 end, and procedure 500 continues with 506. The steps of 504 can be described by referring to the procedure of Fig. 6 will be described and illustrated in more detail.

[0121] In 506, method 500 performs a compression stroke for the mechanically driven pump. During the compression stroke, the stroke of the nose increases, causing the nose to move the piston toward bottom dead center and thereby compressing the spring. This moves the piston toward the housing of the mechanically driven pump. The movement of the piston toward the housing of the mechanically driven pump reduces the area between the piston and the housing, thereby increasing the pressure in this area. The movement of the piston toward the housing of the mechanically driven pump also closes the inlets and opens the outlets of the mechanically driven pump.Upon exceeding another pressure threshold, one or more inlets can be closed by closing at least the first check valve, thus preventing fluid communication between the inlet and the area between the piston and the body located therein. Likewise, above the other pressure threshold, one or more outlets can be opened via at least the second opening of the check valve, so that the outlets are in fluid communication with the area between the piston and the body. The combination of closed inlet openings and higher pressure under the piston drives the delivery flow from the mechanically driven pump. Upon reaching bottom dead center, the compression stroke ends, and procedure 506 continues with 508. The steps of 506 can be described using the procedure of . Fig. 7 will be described and illustrated in more detail.

[0122] At 508, procedure 500 can either loop or terminate, depending on whether the pump, or more precisely the piston, is still receiving rotational energy from the rotating element, for example, to be actuated. In other words, at 508, the next steps of procedure 500 are determined by whether the nose remains in contact with the piston and rotates. If the piston continues to receive rotational energy from the nose (e.g., if 508 is YES), procedure 500 can return to 504 to begin another cycle of the pumping operation sequence for the mechanically driven pump. If the transfer of rotational energy from the nose to the piston ceases (e.g., 508 is NO), procedure 500 proceeds to the exit or termination.

[0123] Fig. Figure 6 shows a method 600 for moving a piston of a pump of the present disclosure during an expansion stroke. During the expansion stroke, an outlet check valve (e.g., the second valve described in method 500 of Fig. 5 described) closed and an inlet check valve (e.g. the first valve described in procedure 500 of Fig. 5 is described) opened. In other words, Method 600 actuates the drive components of a mechanically driven pump of the present disclosure, particularly during an expansion stroke. Method 600 can be carried out with a mechanically driven pump, e.g., with the mechanically driven pump 226, as described in the Fig. 2 to 4 and Fig. 8 shown.

[0124] Method 600 begins with 602 by rotating the nose described in Method 500 from a starting position toward a top dead center (TDC) position. The starting position and the TDC position are radial positions with respect to the nose and the nose's axis of rotation. At the TDC position, a surface of the nose contacts the piston, so the piston has been moved to TDC. The nose can be driven by a rotating element, such as a shaft. The nose can rotate in a first or a second direction, the first and second directions being opposite to each other. As the nose begins to rotate toward top dead center, the distance between the surfaces of the nose that contact the piston and the nose's axis of rotation decreases. In other words, the distance between the piston's contact surface and the center axis and the center of the rotating element driving the nose decreases.The spring, or more precisely the tension on the spring, reduces the downward force from the nose onto the piston, as the spring acts in the opposite direction to the force generated by the contact between the piston and the nose. The spring force pushes the piston towards top dead center.

[0125] When the downward force falls below a threshold, procedure 600 continues with 604, where the spring begins to expand when the downward force becomes less than the spring force. The expansion of the spring moves the piston toward the nose and presses it against the nose. The expansion of the spring keeps the piston in contact with the nose. Likewise, the expansion of the spring increases the volume of a region between the piston and the pump body, such as the pressure chamber 336 in Fig. 3A-3D and Fig. 8. Increasing the volume can reduce the pressure in the area between the piston and the pump body. The area between the housing and the piston can be referred to as the pressure chamber.

[0126] Method 600 continues to 606, where the pressure in the pressure chamber drops below a first threshold. Below the first pressure threshold, the blowing force acting on the outlet check valve, and in particular on the inner ball, becomes less than the force of gravity acting on the outlet check valve. The outlet check valve can then be closed by gravity.

[0127] Procedure 600 continues to 608, where the pressure of the pressure chamber drops below a second threshold to have a negative differential pressure relative to an external environment of the body, such as the closed environment 303 of the Fig. 3A-3D. More precisely, below the first threshold, the pressure chamber can exhibit a negative differential pressure relative to the pump's inlet and outlet ports, such as inlet and outlet ports 342 and 352, which can be selectively connected to the pressure chamber via the first and second check valves. Upon reaching a vacuum, a suction effect is created between the inlet check valve and the pressure chamber. The inlet check valve is designed so that a suction force greater than gravity can open it. Additionally, the vacuum creates a suction effect between the outlet check valve and the pressure chamber. The outlet check valve is configured so that the suction force acts additively to gravity, helping to seal and close the outlet check valve during the expansion stroke.

[0128] In procedure 600, process 610 reduces the pressure in the pressure chamber to or below a third threshold. At or below the third pressure threshold, the suction force acting on the inlet check valve is increased so that it exceeds the force of gravity on the inner ball of the inlet check valve. The inner ball is lifted by the suction force and opens the inlet valve. Through the opening of the inlet valve, fluid can flow into the pump's pressure chamber. The fluid can be either gas or liquid, the gas being air and the liquid being or including a lubricant. The fluid flows as long as the differential pressure of the chamber is negative, and the differential pressure can remain negative as the volume of the pressure chamber expands and the piston moves toward top dead center.

[0129] At 612, procedure 600 rotates the nose into the TDC position, lifting the piston to TDC. At top dead center, the piston stops its upward movement and moves away from the pump body. When the piston's upward movement stops, the pressure in the pressure chamber no longer decreases. Furthermore, the differential pressure in the pressure chamber can equalize, so that the pressure inside the pressure chamber and the pressure outside the pressure chamber, e.g., the pressure at the inlet and outlet ports, are equal. When the pressure is equalized, no more fluid flows into the chamber and through the inlet check valve. Once the pressure is equalized, the suction force on the inlet check valve ceases, and the inlet check valve can close by gravity at 612.

[0130] After 612, the procedure ends in 600.

[0131] Fig. Figure 7 shows a method 700 for moving a piston of a pump of the present disclosure during a compression stroke. During the compression stroke, an outlet check valve (e.g., the second valve described in method 500 of Fig. 5 is described) opened and an inlet check valve (e.g. the first valve described in procedure 500 of Fig. 5 is described) closed. In other words, Method 700 controls the drive components of a mechanically driven pump of the present disclosure specifically during the compression stroke. Method 700 can be carried out with a mechanically driven flushing pump, e.g., with the mechanically driven pump 226, as described in the Fig. 2-4 and Fig. 8 shown.

[0132] Method 700 begins in 702 with the rotation of the nose described in Method 500 from a starting position toward a top dead center (TDC) position. The starting position and the bottom dead center (BDC) position are radial positions with respect to the nose and the nose's axis of rotation. At the TDC position, a surface of the nose contacts the piston, so the piston has been moved to TDC. The nose can be driven by a rotating element, such as a shaft. The nose can rotate in a first or a second direction, the first and second directions being opposite to each other. As the nose begins to rotate toward bottom dead center, the distance between the surfaces of the nose that contact the piston and the nose's axis of rotation increases. In other words, the distance between the piston's contact surface and the center axis and the center of the rotating element driving the nose increases.The surface contacting the piston is moved further away from the axis of rotation and presses against the piston, increasing the force exerted on it. More precisely, the nose is lowered relative to the axis of rotation and presses against the spring's load. The contact force between the nose and piston in a direction opposite to the spring's load can be greater than the spring force, thus compressing the spring. The force increase due to the nose-piston contact can be directed downwards towards the piston.

[0133] If the downward force exceeds a threshold, procedure 700 continues with 704, where the spring begins to compress when the downward force becomes greater than the spring force. Compressing the spring moves the piston toward bottom dead center. The rotation and the increase in the distance between the surface in contact with the piston and the axis of rotation of the nose keep the piston in contact with the nose. Likewise, compressing the spring increases the volume of a region between the piston and the pump body, e.g., the pressure chamber 336 in Fig. 3A-3D and Fig. 8. Reduced. A reduction in volume can increase the pressure in the area between the piston and the pump body. The area between the piston and the pump body can be referred to here as the pressure chamber. In other words, compressing the spring reduces the volume of the pressure chamber between the piston and the housing and increases the pressure.

[0134] Method 700 continues to 706, where the pressure in the area between the piston and the pump body rises above a first threshold. At or above the first pressure threshold, the suction force exerted on the inlet check valve, particularly on the inner ball, becomes less than the force of gravity exerted on the inlet check valve. The inlet check valve can then be closed by gravity.

[0135] Method 700 continues to 708, where the pressure in the area between the piston and the pump body rises above a second threshold. Above the second pressure threshold, the area between the piston and the pump body can have a positive differential pressure relative to an environment outside the area, such as the closed environment 303 in the Fig. 3A-3D. More precisely, the area above the second threshold can exhibit a positive differential pressure with respect to the pump's inlet and outlet ports, such as inlet and outlet ports 342, 352, and other volumes, which can be selectively connected to the area via the first and second check valves. Upon reaching an overpressure, a blowing force is generated between the outlet check valve and the pressure chamber. The outlet check valve is designed so that a blowing force greater than gravity can open the outlet check valve. Additionally, the overpressure generates a blowing force between the pressure chamber and the inlet check valve. The inlet check valve is configured so that the blowing force is added to gravity, which helps to seal and close the inlet check valve during the compression stroke.

[0136] In procedure 700, the pressure in the area between the piston and the pump body increases above a third pressure threshold. Upon reaching or exceeding this third pressure threshold, the blowing force applied to the outlet check valve is increased to greater than the force of gravity acting on the inner ball of the outlet check valve. The inner ball is lifted by the blowing force, thereby opening the outlet check valve. The opening of the outlet check valve allows fluid from the area between the piston and the housing to flow through the outlet check valve. The fluid may consist of either gas or liquid, with the gas being air and the liquid being or including a lubricant. The fluid can flow as long as the differential pressure of the chamber is positive, and the differential pressure can remain positive as the volume of the pressure chamber is compressed and the piston moves toward bottom dead center.

[0137] In step 712, procedure 700 rotates the nose into the bottom dead center (BDC) position, bringing the piston to bottom dead center. At bottom dead center, the piston stops moving downwards and towards the casing. As the movement stops, the differential pressure in the area between the piston and the casing equalizes, so that the pressure in the area between the piston and the casing and the pressure outside the area are equal. More precisely, when the pressure equalizes, the pressure in the area between the piston and the casing and the pressures at the inlet and outlet ports become approximately equal. In a sample pump configuration, once the pressure equalizes, the fluid no longer flows out of the area and through the outlet check valve. Likewise, the pressure in the area between the piston and the pump body no longer increases.When the pressure equalizes, the blowing force on the outlet check valve can decrease, and the outlet check valve can close by gravity at 612. When the outlet check valve is closed, fluid continues to be expelled from the outlet port from volumes connected to the outlet check valve and the outlet port. In another example of a pump configuration, the outlet check valve can remain open at bottom dead center because the pressure in the area between the piston and the body remains above the third threshold, allowing liquid and gaseous substances to continue flowing through the outlet check valve. Furthermore, in this or another example configuration of the pump, the inlet check valve can open before the outlet check valve closes.The movement of liquid and gaseous fluids from the area between the piston and the housing can generate a suction force greater than gravity, and thus sufficient to open the inlet check valve. In such a configuration, the inlet check valve and the outlet remain open for a specific period, with fluid flowing into the pressure chamber via the inlet check valve and out of the pressure chamber via the outlet check valve.

[0138] After 712, the procedure ends at 700.

[0139] Methods 500, 600, and 700 describe a pump operation comprising: rotating a cam nose to move a piston; selectively extending and compressing a spring depending on the cam nose's position relative to the piston; and pumping one or more fluids while one fluid flow is blocked by opening a first check valve or a second check valve and closing the other. The first check valve may be connected to an inlet, and the second check valve to an outlet. The first check valve may alternatively be called the inlet check valve. Likewise, the second check valve may alternatively be called the outlet check valve. Fluid may be drawn into the pump by decreasing pressure into a pressure chamber between the piston and the casing, thereby opening the first valve by suction.The second valve is designed to remain closed due to gravity and / or suction. Fluid can also be pumped out of the pump by increasing the pressure in the pressure chamber and opening the second valve with a blowing force. The second valve is designed to remain closed due to gravity and / or blowing force.

[0140] The disclosure also provides support for a method of moving a pump back and forth within a gearbox, wherein the pump is arranged inside the gearbox, comprising: rotating a nose to move a piston, selectively compressing a spring for an expansion stroke according to a position of the nose relative to the piston, moving the piston from a top dead center to a bottom dead center, increasing the pressure between an inlet check valve and a pressure chamber, causing the inlet check valve to close, increasing the pressure between an outlet check valve and the pressure chamber, causing a blowing force on the outlet check valve and its opening, and forcing fluid out of the pressure chamber through the outlet check valve.In a first example of the procedure, after a threshold value for the rotation of the nose relative to the piston is reached, the spring is selectively extended for one compression stroke according to a different nose position relative to the piston, the piston is moved from bottom dead center to top dead center, the pressure between the exhaust check valve and the pressure chamber decreases, causing suction and closing of the exhaust check valve, the pressure between the inlet check valve and the pressure chamber decreases, causing suction and opening of the inlet check valve, and fluid is drawn through the inlet check valve into the pressure chamber. In a second example of the procedure, which optionally includes the first example, the inlet and exhaust check valves contain no preload springs and are closed by gravity.In a third example of the method, optionally comprising one or both of the first and second examples, the nose is driven to rotate by a mechanical system, and during the reciprocating motion, a lubrication system comprising the pump provides targeted lubrication to a component of the mechanical system. In a fourth example of the method, optionally comprising one or more or each of the first through third examples, the pumping of fluid involves pumping fluid through an inlet port in fluid communication with the inlet check valve and an outlet port in fluid communication with the outlet check valve, both the inlet port and the outlet port extending through a side wall of a pump body.

[0141] Fig. 4 and Fig. Figure 9 shows example configurations with approximate positions. Fig. 4 and Fig. Figure 9 is shown approximately to scale; however, other relative dimensions may also be used. In this context, the term "approximately" should be understood to include plus or minus five percent of the range, unless otherwise stated.

[0142] Fig. 1-4 and Fig.Figures 8-10C show example configurations with the relative positioning of the various components. If such elements are shown in direct contact with each other or directly coupled, then in at least one example they can be described as being in direct contact with each other and directly coupled. Similarly, elements shown side by side or adjacent to each other can be described as being adjacent to each other or adjacent to each other in at least one example. For instance, components that are in planar contact with each other can be described as being in planar contact. As another example, in at least one case elements that are separated from each other, with only a gap between them and that have no other components, can be described as such.In yet another example, elements that are displayed above / below each other, on opposite sides, or to the left / right of each other can be described as such, relative to one another. Furthermore, in at least one example, as shown in the figures, a topmost element or the highest point of an element can be referred to as the "top" of the component, and a bottommost element or the lowest point of the element can be referred to as the "bottom" of the component. The terms top / bottom, upper / lower, and above / below used here can refer to a vertical axis of the figures and be used to describe the positioning of elements within the figures relative to each other. Thus, in one example, elements displayed above other elements are arranged vertically above the other elements.As a further example, the shapes of the elements depicted in the figures can be described as such (e.g., circular, straight, flat, curved, rounded, beveled, angled, etc.). Furthermore, in at least one example, elements shown intersecting each other can be described as intersecting elements or as intersecting each other. In addition, an element depicted inside or outside another element can be described as such.

[0143] Although various embodiments have been described above, it is understood that they are presented only as examples and not as limitations. It is understood that the configurations and routines disclosed here are exemplary in nature and that these specific examples should not be considered restrictive, as many variations are possible. The technology described above can, for example, be applied to powertrains that include various types of drive sources, including different types of electric machines, internal combustion engines, and / or transmissions. The technology can be used as a standalone system or in combination with other power transmission systems, e.g.,including, but not limited to, machinery and drive systems for tandem axles, electric trailer axles, P4 axles, hybrid vehicles, battery-powered vehicles, agriculture, shipping, motorcycles, recreational vehicles, and on- and off-road vehicles. The subject matter of this disclosure includes all novel and non-obvious combinations and sub-combinations of the various systems and configurations, as well as other features, functions, and / or characteristics disclosed herein. It will be apparent to those skilled in the art that the disclosed subject matter can be implemented in other specific forms without departing from the spirit of the subject matter.

[0144] The following claims highlight in particular certain combinations and subcombinations that are to be considered novel and not obvious. These claims may refer to "one" element or "a first" element, or the equivalent thereof. Such claims are to be understood as including one or more such elements, not as requiring or excluding two or more such elements. Further combinations and partial combinations of the disclosed features, functions, elements, and / or properties may be claimed by amending the present claims or by presenting new claims in this or a related application. Such claims, whether they have a broader, narrower, the same, or different scope than the original claims, are also to be considered as belonging to the subject matter of the present disclosure.

[0145] Unless otherwise stated, the term "approximately" means plus or minus five percent of the range.

Claims

[1] Pump for lubrication, comprising: a nose mounted on and driven by a shaft; a piston that is in contact with the nose; a spring acting on the piston; an inlet check valve located in an inlet port; and an exhaust check valve arranged in an exhaust port, wherein the inlet check valve and the exhaust check valve have no preload springs and are arranged vertically in a normally closed position due to gravity acting on internal balls of the inlet check valve and the exhaust check valve. [2] Pump according to claim 1, further comprising a pump body of the pump, wherein a cylindrical hole of the pump body of the pump is provided for receiving the piston. [3] Pump according to one of the preceding claims, further comprising a pump body of the pump, wherein the inlet check valve is arranged in a first hole of the pump body and fluidically seals it, the outlet check valve is arranged in a second hole of the pump body and fluidically seals it, and the first hole and the second hole are arranged vertically with openings that are open to a surface perpendicular to a vertical axis of the pump. [4] Pump according to one of the preceding claims, wherein the inlet opening connects a first opening and the outlet opening connects a second opening in fluid communication with a pressure chamber in which the spring is housed and on which the piston acts, and the first opening and the second opening are outside of a piston stroke of the piston, so that the piston is prevented from blocking the first opening or the second opening. [5] Pump according to claim 4, wherein the inlet opening comprises the first opening and the outlet opening comprises the second opening. [6] Pump according to claim 4 or 5, wherein the inlet opening is arranged in a side wall of a pump body and the first opening extends through the side wall of the pump body. [7] Pump according to one of claims 4 to 6, wherein the outlet opening is located in a side wall of a pump body and the second opening extends through the side wall of the pump body. [8] Pump according to one of the preceding claims, wherein the pump is a flushing pump whose suction side is connected to a dry sump. [9] Pump according to one of the preceding claims, wherein the piston has a piston jacket. [10] Pump according to claim 9, wherein the piston jacket has a length which is less than a diameter of the piston, wherein the length is at least 81% of the diameter and at most 84% of the diameter. [11] Pump according to any of the preceding claims, wherein the nose is a cam nose. [12] Pump according to any of the preceding claims, wherein the nose is an eccentric nose. [13] Pump according to one of the preceding claims, wherein the shaft is driven by a mechanical system which is lubricated via the pump. [14] Transmission of a vehicle, comprising: a self-priming pump, including: an eccentric nose; a feather; a piston designed to receive the spring and to interact with the eccentric nose; a pump body with a cylindrical hole designed to receive the spring; an inlet check valve located in an inlet port; and an outlet check valve arranged in an outlet port, wherein the inlet check valve and the outlet check valve have no preload springs and are installed vertically in a normally closed position due to gravity acting on internal balls of the inlet check valve and the outlet check valve. [15] Gearbox according to claim 14, wherein the eccentric nose is rigidly coupled to a rotating element of a mechanical system, the mechanical system drives the eccentric nose via the rotating element and the mechanical system receives targeted lubrication by a lubrication system comprising the self-priming pump.

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