JP5068306B2 - Low noise gear pump - Google Patents

Description

  The present invention relates generally to vehicular powertrain systems, and more particularly to low noise gear pumps used in any system to reduce gear wear.

[Description of related applications]
This application is a US patent application Ser. No. 11 / 359,728 filed Feb. 22, 2006, which is a priority application of US Provisional Patent Application No. 60 / 655,221 filed Feb. 22, 2005. Is a continuation-in-part application. US patent application Ser. No. 11 / 359,728 is a US application filed April 8, 2005, which is a priority application of US Provisional Application No. 60 / 560,897 filed April 9, 2004. This is a continuation-in-part of Patent Application No. 11 / 101,837 (currently US Pat. No. 7,179,070).

  This application is an alleged claim application of US Provisional Application No. 60 / 781,775 filed on Mar. 13, 2006.

  Gear pumps and gear motors are one of the most durable pumps available. However, the noise generated by these pumps is a problem for many applications. It is desirable to control this noise source. Noise level and frequency are affected by gear tooth type, gear tooth geometry, gear tooth surface and lubrication. Most of the noise is caused by the oil becoming trapped between the gear teeth when the gear teeth are engaged.

  Often, changing the type of gear teeth used or smoothing the tooth surface can alter the gear's ability to transfer loads if the gear tooth geometry is changed. In case it is not possible. Furthermore, using high viscosity oils and greases can reduce noise, but this is not suitable for every gear unit.

  Accordingly, it would be desirable to provide a low noise gear pump that further reduces gear wear.

  In order to cope with a quiet sealing method, it was necessary to reconsider the way the current gear meshes. Rather than gear seals using toothed sides, the seal is obtained using the gear tip and root as one location, and the oil meshes first when the next gear teeth engage each other. It is possible to escape hydrostatically from between the gear teeth.

  The present invention is used in any device, and is herein a low noise gear set for use in a power plant, the power plant being connected to a low pressure fluid source to produce a high pressure fluid at the output. A pump driven engine 12 and at least one variable displacement pump / motor that produces rotational motion at the output in response to the high pressure fluid, the variable displacement pump / motor comprising a drive gear and a drive gear. Idle gears, which initially mesh with the drive gear at a first location along the tooth profile of the corresponding gear, at least one of the two locations is the tip of the opposing gear teeth A root portion of one of the gear teeth meshing with the portion, the first contact point for obtaining a fluid seal from the low pressure fluid source between the root portion and the tip portion is generated, and the teeth When combined, the following second location exists along the tooth profile, and when leaving at the high pressure fluid output, the fluid can hydrostatically escape from between the locations, and the low noise gear Provide set.

  Preferably, a method of providing a low noise gear pump with reduced gear wear includes providing a first gear, wherein the first gear is second at a first meshing location. Engaging the gear, wherein the first meshing location is the root of one gear tooth and the tip of the opposing gear tooth, and the first gear is second at the second meshing location. A second meshing position is a position along the tooth profile side of one gear meshing with a position along the tooth profile side of the opposite gear, and the gear meshes with the second meshing position. A step of forming a region for sealing the gear teeth when engaged at a point and disengaged from the first meshing point, and when the gear tooth is separated at the first meshing point, the fluid is fluidized. A way to escape statically Comprising the step of subjecting.

  The foregoing and other advantages of the present invention will be readily apparent to those skilled in the art from the following detailed description of the preferred embodiment, when considered in light of the accompanying drawings.

  The following patent applications: US Provisional Application No. 60 / 560,897, US Patent Application No. 11 / 101,837 (currently US Pat. No. 7,179,070), US Provisional Application No. 60 / No. 655,221, U.S. Patent Application No. 11 / 359,728, and U.S. Provisional Application No. 60 / 781,775, which are incorporated herein by reference.

  Low noise gear set 300 is described as used in pump / motor 16 and motors 76a-76d are preferably commonly assigned copending US patents, for example, filed April 8, 2005. This is a variable displacement pump / motor shown in application Ser. No. 11 / 101,837, the disclosure of which is incorporated herein by reference and shown in FIGS. 4 and 5 is a part of this specification. And As a variant, the pump / motor 16 and the motors 76a-76d are vane-type or piston-type variable displacement pump / motor or constant displacement pump / motor. In addition, a pump / motor 16 with a low noise gear set 300 is shown, for example, in commonly assigned copending US patent application Ser. No. 11 / 759,728 filed on Feb. 22, 2005. Which can be used in connection with the hydraulic hybrid powertrain system 10, which is incorporated herein by reference, the disclosure of which is shown in FIGS.

  Referring now to FIG. 6, the low noise gear set or gear train of the present invention is indicated generally by the numeral 300. The low noise gear set 300 can be used in a variety of applications where it is desirable for an inscribed or circumscribed gear pump / motor to be used with fluids of any viscosity, thereby advantageously being used in any device. A low noise and reduced wear gear set is provided.

  The low noise gear set 300 comprises at least two or more gears, preferably a drive gear 310 and an idler gear 312. The idle gear 312 is engaged with the drive gear 310 at two locations 314 and 316 along the corresponding tooth profiles 318 and 320, while the idle gear 312 is driven. When the drive gear 310 is rotated, the gears 310 and 312 engage each other at the first meshing location 314. This first meshing location 314 is preferably such that the root portion 326 of one gear tooth, in this case the root portion 326 of the gear tooth of the drive gear 310 is the tip portion 328 of the opposite gear tooth, in this case the idle gear. It is formed by engaging the tip 328 of the gear tooth 312.

  As the drive gear 310 continues to rotate, a second meshing point 316 is preferably formed along the side of one gear tooth 318 of the drive gear 310 and the opposite gear tooth 320 of the idler gear 312. . The seal 322 is caused by the mechanical pressure generated by the pressurized fluid or gas applied to one side of the pump 16 when the first meshing location 314 is disengaged during rotation of the gear and then the second meshing location 316 is engaged. Is made. A small amount of fluid 324, such as oil, is entrained between the drive gear 310 and the idler gear 312 in the seal 322 formed by locations 314 and 320. As a result of the seal 322, the pressure of the entrained fluid 324 acts perpendicular to the center of the gears 310, 312 and the gears 310, 312 do not attempt to compress the fluid 324 therebetween, rather than the fluid 324 324 is expelled from between the gears 310 and 312.

For example, when utilized in a power plant having a hydraulic hybrid powertrain system 10 that includes a pump / motor 16, a preferred method of providing a low noise gear set 300 for use in a pump with reduced gear 300 wear is:
Providing a first gear 310;
Engaging the second gear 312 at a first meshing location 314, the first meshing location 314 comprising a root 326 of one gear tooth and an opposing gear tooth A tip 328;
Engaging the second gear 312 at a second meshing location 316, the second meshing location 316 meshing with a location along the side of the tooth profile 320 of the opposing gear. It is a location along the side of the tooth profile 318 of one gear,
Forming a region 322 that seals the gear teeth when the gears 310, 312 are engaged at the second meshing location 316 and disengaged from the first meshing location 314;
Providing a means for the fluid 324 to escape hydrostatically when the gear teeth are disengaged at the first meshing location 314.

  When the drive gear 310 rotates the idler gear 312, the first meshing location 314 and the second meshing location 316 are continuously created as a result of the mutual meshing of the gear teeth. Thus, while the second meshing location 316 is disengaged, the next first meshing location of the next gear tooth is created at the root and tip of the corresponding tooth. The rotation of the gear causes a meshing point system along the gear tooth profile (tooth profile). The sealing region 322 is formed by the start of disengagement of the first engagement portion 314 at the start of engagement of the second engagement portion 316. Once the first mating location 314 is disengaged, the fluid 324 escapes hydrostatically from the sealed region 322.

  Referring now to FIG. 1a, a hydraulic hybrid powertrain system is indicated generally at 10. As will be appreciated by those skilled in the art, the powertrain system 10 can be used in a variety of applications, such as, but not limited to, automobiles, ships, submarines, helicopters, etc. In the following description, the power train system will be described as being installed in an automobile. The power train system 10 includes a power plant section 11, a mode selector module 43, a control section 59 and a power delivery section 76.

  The power plant section 11 of the power train system 10 has an engine 12 in communication with a fuel source 14. The engine 12 may be a conventional internal combustion engine, a turbine engine, an electric motor powered by a battery, a fuel cell, or the like. The engine 12 preferably selectively provides torque to a variable displacement hydraulic pump / motor 16 that includes a low pressure source 18 of hydraulic fluid at its inlet side and a high pressure conduit at its outlet side. 20 is provided. The hydraulic oil may be, but is not limited to, a liquid such as water, hydraulic oil, transmission fluid, etc. or any compressible gas that falls within the scope of the present invention. The pump / motor 16 is described as such because, depending on the mode of the system 10, the device functions alternately as a pump or as a motor, as described in detail below.

  The power plant section 11 of the system 10 includes a plurality of auxiliary drive devices, which include, but are not limited to, a motor generator 22, an air conditioning compressor 24, and a heat pump. The motor generator 22 is connected to a power maintenance module 28, and this power maintenance module is connected to the battery pack 30. The heat pump 26 is in communication with the heater core 32, and both the heat pump 26 and the heater core 32 are in fluid communication with a cooling water source 34 for the engine 12. The air conditioning compressor 24 is in communication with the heat exchanger 36. The auxiliary drives 22, 24, 26 are preferably operated by respective electric or hydraulic motors. As a variant, the auxiliary drives 22, 24, 26 are selectively mechanically coupled to the engine 12. An accumulator 38 is in fluid communication with the high pressure conduit 20 provided at the outlet of the pump / motor 16. The accumulator 38 serves as a reservoir for high pressure hydraulic fluid and maintains high pressure in the system 10 by being charged with, for example, high pressure gas or the like (not shown), as will be appreciated by those skilled in the art.

  The throttle control module 40 receives an input signal from the air conditioning compressor 24 via a signal on the line 24a, receives an input signal from the power maintenance module 28 via a signal on the line 28a, and a signal on the line 38a. The input signal from the accumulator 38 is received via Based on the input signals on lines 24a, 28a, 38a, throttle control module 40 outputs an output signal on line 42 to determine which of engine 12 and pump / motor 16 is described, as will be described in detail below. Control one or both. The signals on lines 24a, 28a, 38a, 42 may be electronic signals or mechanical feedback between various components and throttle control module 40. The throttle control module 40 may be any suitable mechanical or electrical device that can control the operation of the engine 12 and the pump / motor 16 based on one or more inputs.

  The mode selector module 43 has a mode selection valve 44 that is in fluid communication with the high pressure conduit 20 by the high pressure inlet conduit 46. The mode selection valve 44 preferably places the valve 44 in the “D” position, ie, the drive position (best shown in FIG. 1a), and the “N” position, ie, the neutral position (best shown in FIG. 1b). ), One of the “R” position, ie reverse or back position (best shown in FIG. 1 c) and the “P” position, ie parking position (best shown in FIG. 1 d) It is connected to a transmission-type shift lever (not shown) or the like that moves automatically. A low pressure inlet conduit 48 is connected to the mode selection valve 44 adjacent to the high pressure inlet conduit 46. Further, a high pressure outlet conduit 50 and a low pressure outlet conduit 52 are connected to the mode selection valve 44 on the opposite side of the mode selection valve 44. Each position P, R, N, D of the mode selection valve 44 selectively aligns the inner portion of the position with the conduits 46, 48, 50, 52 as described in detail below. Control the flow direction of hydraulic oil. Although described as “inlet” and “outlet” as described above, during operation, each of the conduits 46, 48, 50, 52 depends on the operating conditions of the system 10, as described in detail below. , Can act as an inlet or outlet.

  The conduits 50 and 52 are connected to the brake override device 54. A high pressure outlet conduit 56 and a low pressure outlet conduit 58 are also connected to the brake override device 54 on the opposite side of the brake override device 54. The brake override device 54 has a first or normal position 54a and a second or override position 54b, as will be described in detail below.

  The control section 59 has a displacement control valve 60 that is in fluid communication with the high pressure conduit 20 by the high pressure inlet conduit 62. A low pressure inlet conduit 64 is connected to the displacement control valve 60 adjacent to the high pressure inlet conduit 62. Further, a high pressure outlet conduit 66 and a low pressure outlet conduit 68 are connected to the displacement control valve 60 on the opposite side of the displacement control valve 60. The displacement control valve 60 is a floating position control valve, and an accelerator and a brake 72 for directing a flow from the displacement control valve 60 to the plurality of cylinders 74a, 74b, 74c, and 74d are connected to the displacement control valve. The accelerator 70 and the brake 72 are preferably mechanically coupled to respective accelerator pedals and brake pedals (not shown). The brake 72 is connected to the brake override device 54 via the connector 73. The displacement control valve 60 has a first or acceleration position 60a, a second or holding position 60b, and a third or deceleration position 60c. Each position 60a, 60b, 60c of the displacement control valve 60 selectively positions the inner portion of each position 60a, 60b, 60c in a conduit 62, 64, 66, 68, as best shown in FIG. In combination, the flow direction of the hydraulic oil to the cylinders 74a, 74b, 74c, and 74d is controlled.

  Each of the cylinders 74a, 74b, 74c, 74d has a respective drive or traction motor 76a, 76b, 76c, 76d (power delivery section 76) attached to the vehicle wheels via connectors 75a, 75b, 75c, 75d. Inside). The motors 76a and 76d are preferably variable displacement motors. As understood by those skilled in the art, the positions of the connectors 75a to 76d determine the push-out amounts of the motors 76a to 76d by connecting to the swash plate, for example. The high pressure outlet conduit 66 is in fluid communication with one side of a piston (not shown) in each of the cylinders 74a-74d, and the low pressure outlet conduit 68 is in fluid communication with the opposite side of the piston in the cylinders 74a-74d. In communication. Although the system 10 is shown with a plurality of traction motors 76a, 76b, 76c, 76d, those skilled in the art may utilize as few as one motor, which is the invention of the present invention. Included in the range. For example, in a single motor system used in an automobile, the output of a single motor is connected to a differential gear, and this differential gear is mechanically connected to a pair of drive wheels. Each of the traction motors 76a, 76b, 76c, 76d has an upper port 77a, 77b, 77c, 77d and a lower port 78a, 78b, 78c, 78d. The flow direction of the hydraulic oil passing through the upper ports 77a to 77d and the lower ports 78a to 78d determines the directions of the motors 76a to 76d. A feedback connector 80 extends between the displacement control valve 60 and the pistons of the cylinders 74a to 74d.

  The check valve bridge circuit 82 has a plurality of check valves 84, 86, 88, 90 that are similar to a full wave bridge rectifier, as best shown in FIG. Are arranged in various ways. A conduit 92 is in fluid communication with the inlet of check valve 84 and the outlet of check valve 86. The conduit 92 is also in fluid communication with the high pressure outlet conduit 56. A conduit 94 is in fluid communication with the inlet of check valve 86 and the inlet of check valve 88. The conduit 94 is also in fluid communication with the low pressure source 18 of hydraulic oil. The conduit 96 is in fluid communication with the outlet of the check valve 88 and the inlet of the check valve 90. The conduit 96 is also in fluid communication with the low pressure outlet conduit 56. A conduit 98 is in fluid communication with the outlet of check valve 84 and the outlet of check valve 90. The conduit 98 is also in fluid communication with the high pressure conduit 20.

  Referring now to FIG. 4, the inscribed gear device of the present invention is generally designated 100. The device 100 can be configured to operate as either a motor or a pump as will be understood by those skilled in the art, but will be referred to as a motor in the following description of the invention. The internal gear motor 100 has a hollow housing 102 with a base portion 104 and an end cap 106. The base portion 104 is provided with a recess or cavity 108 sized to receive the first mandrel 110 and the first piston member 112. End cap 106 has at least two ports 107 (only one shown), each extending between its inner and outer surfaces, preferably on opposite sides of end cap 106. One of the ports 107 is connected to the high pressure side segment of the fluid system, eg, the high pressure conduit 200 of FIGS. 1a-1e, and the other of the ports 107 is a return line or fluid source, eg, FIGS. 1a-1e. Connected to a fluid source 18.

  The first mandrel 110 has a hole 114 provided through its base portion 111, the first mandrel having a first outer flange 116 extending upward from the upper surface 113 of the base portion 111 and a plurality of mandrels. There is a second outer flange 118 spaced from one another. An inner flange 120 extends upward from the base portion 111 of the first mandrel 110 and is disposed adjacent to the hole 114. The first outer flange 116 is disposed adjacent to the hole 114. Second outer flange 118 is spaced from both hole 114 and inner flange 120. A first seal bushing 122 is dimensioned to fit rotatably in the bore 114, and this first seal bushing preferably has a height substantially equal to the base portion 111 of the first mandrel 110. Accordingly, when the bushing 122 is disposed in the hole 114, the upper surface of the bushing 122 is substantially flush with the upper surface 113 of the base portion 111.

  A circumscribed gear 124 having a substantially circular cross-section is disposed over the upper surface 113 of the base portion 111 so that the curved outer surface of the gear 124 is on the curved inner surfaces of the outer flanges 116 and 118, respectively. Located adjacent to each other. A plurality of teeth 126 are formed on the inner surface of the external gear 124. The gear 124 is axially fixed between the outer flange 118 and the inner flange 120 when disposed on the upper surface 113.

  An internal gear 128 having a substantially circular cross section has a plurality of teeth 130 formed on the outer surface thereof, and a hole 132 is formed through the internal gear. The teeth 130 can mesh with teeth 126 formed on the inner surface of the external gear 124. The lower surface of the gear 128 extends into and rotates with the bushing 122, and the teeth 130 cooperate with the corresponding teeth of the bushing 122 when the motor 100 is assembled and operated. Will be described in detail below. The outer surface of each of the teeth 130 of the internal gear 128 is located adjacent to the inner surface of the inner flange 120. The bore 132 is adapted to receive the free end of the drive shaft or output shaft 134 when the motor 100 is assembled. The internal gear 128 can move axially along the shaft 134. The drive shaft 134 is rotatably supported in the end cap 106 by a bearing 135 such as a ball bearing or a roller bearing. The free end of the drive shaft 134 extends a predetermined distance beyond the top surface of the end cap 106, and this drive shaft serves as the output shaft of the motor 100.

  The second piston member 136 has a hole 138 provided in an inner portion thereof, and the second piston member is attached to the upper surface of each of the outer flanges 116 and 118 of the first mandrel 110. It has become. Therefore, the second piston 136 and the first piston 112 are attached to the upper surface and the lower surface of the lower mandrel 110, respectively.

  A second mandrel 140 is arranged in the hole 138 of the second piston member 136, and a hole 142 for receiving the drive shaft 134 is formed in the inner portion of the second mandrel. . The second mandrel 140 has a downwardly extending flange 144 that cooperates with the inner flange 120 that extends to both of the first mandrels 110 when the motor 100 is assembled. A pair of bores 146 are formed through the upper mandrel 140 and are in fluid communication with the gears 122, 124 during operation of the motor 100.

  The second seal bush 148 has a plurality of teeth 150 formed on the outer surface thereof, and a hole 152 is formed through the second seal bush. The second seal bushing 148 is adapted to receive the upper mandrel 140 in the bore 152 and is received in the external gear 124 for rotation therewith. When assembled and activated, it cooperates with the teeth 150 of the bushing 148, which will be described in detail below.

  When assembling the motor 100, the first mandrel 110 and the first piston 112 are disposed in the base portion 104 of the housing 102, the first seal bushing 122 is disposed in the mandrel 110, and the external gear 124 is disposed on the mandrel 110. To place. The internal gear 132 and the second mandrel 138 are attached to the drive shaft 134 so that the teeth 126 and 130 of the gears 132 and 124 are rotatably engaged with each other and the internal gear 132 is engaged with the first seal bush 122. Assemble to do. The second piston 136 is attached to the upper surface of the mandrel 110, and the second seal bush 148 is disposed on the second mandrel 138 and engaged with the external gear 124. A downwardly extending flange 144 cooperates with the upwardly extending inner flange 120 to divide the interior of the circumscribed gear into an inlet chamber and a discharge chamber of the motor 100 and attach an upper end cap 106 to the base portion 104 to seal the housing 102. To do. The flanges 120, 144 extend radially between the teeth 126 and 130 to form an inlet chamber on one side of the flange and a discharge chamber on the other side of the flange.

  In operation, the shaft 134 is coupled to a load (not shown), such as a vehicle wheel. Pressurized fluid is introduced through one of the ports 107 from a fluid system, such as the high pressure conduit 20 of FIGS. 1 a-1 e, and routed through the bore 146 to the inlet chamber side of the gears 124, 128. Acts on the intermeshing teeth 126, 130 to rotate the gear and shaft, flow between the teeth to the discharge chamber and through the other of the bores 146 to the other of the ports 107. It is. The first seal bush 122 serves as a rotational seal between the internal gear 128 and the first mandrel 110, and the second seal bush 148 serves as a rotational seal between the external gear 124 and the second mandrel 140. , Thereby ensuring the integrity of the inlet chamber and the discharge chamber. The motor 100 of the present invention requires only seal bushings 122 and 148 to maintain a fluid seal and allow efficient operation of the motor 100.

  The normal or predetermined spatial relationship between the teeth 126, 130 of the gears 124, 128 is such that the teeth 126, 130 engage each other over substantially all of the axial region of the teeth. In such a relationship, the motor 100 produces its maximum volume flow or maximum output. The motor 100 of the present invention can advantageously vary from its maximum displacement because the internal gear 128 can move axially along the shaft 134. As the internal gear 128 moves toward the first mandrel 110, the inter-axial meshing area of the teeth 126, 130 decreases, thereby reducing the volumetric flow or displacement of the motor 100.

  When unit 100 is configured as a motor, an external pressure source, such as hydraulic fluid from an external hydraulic pump, compressed air from an air compressor, etc., causes gears 124, 128 to spin and produce output torque on shaft 134. Volume flow is provided to port 107. When the pressure is changed, the internal gear 128 moves along the axis of the shaft 134 to change the output horsepower of the motor 100. The motor 100 can advantageously be used to control the output rpm under greatly varying output loads, such as automobiles, turrets, large machines, earth movers, large drilling machines, ships, farm equipment. However, it is not limited to these.

  When the unit 100 is configured as a pump and the prime mover, such as the engine 12 of FIGS. 1a-1e, rotates the shaft 134 at a low speed or low torque, the pump 100 outputs its output based on the internal pressure in the pump housing 102. It responds to the decrease of input speed or input torque by changing. In this state, the output port 107 creates a high back pressure in the discharge chamber, and the internal gear 128 is in or near equilibrium along the axis of the shaft 134 for the gear 128 to continue to operate. Move to a point along the axis. Accordingly, the pump 100 can be configured such that the maximum displacement or displacement of the internal gear 128 substantially adjacent to the lower mandrel 110 from the maximum output or displacement of the internal gear 128 substantially adjacent to the upper mandrel 140. Can vary up to.

  Referring now to FIG. 5, the circumscribed gear device of the present invention is indicated generally by the reference numeral 200. The device 200 can be configured to operate as either a pump or a motor, as will be appreciated by those skilled in the art, but will be a pump in the following description of the invention. The circumscribed gear pump 200 has a hollow housing 202 with a first end cap 204 and a second end cap 206 connected to each other by a body portion 208. Preferably, the first end cap 204 and the second end cap 206 are attached to the body portion 208 by a plurality of fasteners 210, such as high strength bolts or the like. The body portion 208 is provided with a recess 212.

  A first gear 214 having a plurality of teeth 216 formed on the outer surface and a second gear 218 having a plurality of teeth 220 formed on the outer surface are accommodated in the recess 212 of the housing 202. The respective teeth 216, 220 of the gears 214, 218 can mesh with each other rotatably in the recess or pump cavity 212 during operation of the pump 200. A shaft 222 extends from the first gear 214, and a stepped shaft 224 extends from the second gear 216. The first gear 214 is fixed to the shaft 222, and the second gear 218 can move axially along the shaft 224. The shafts 222 and 224 extend in opposite directions in the axial direction, and the shaft 224 is longer than the shaft 222. A first seal sleeve 226 with internal teeth receives the first gear 214, and a second seal sleeve 228 with internal teeth receives the end of the second gear 218.

  A flange 232 extends from the plate-like joint 230, and this plate-like joint is attached to a first thrust plate 234 provided on the flat upper surface thereof. Preferably, the thrust plate 234 is attached to the joint 230 by a plurality of fasteners 236, such as high strength bolts. The free end of the shaft 222 passes through an opening provided in the joint 230 and the thrust plate 234. The free end portion of the shaft 222 is rotatably fixed in the joint 230 and the thrust plate 234 by a pair of nuts 238 and is rotatably supported by a bearing 240 such as a ball bearing or a roller bearing. The second seal sleeve 228 is receivable in a recess provided in the joint 230 adjacent to the flange 232. When the shaft 222 is disposed in the joint 230 and the thrust plate 234, the gear 214 is fixed in the axial direction with respect to the housing 202.

  A second thrust plate 242 is attached to the upper surface 205 of the first end cap 204 by a plurality of fasteners 244, such as high strength bolts. Plate 242 has a hole for receiving the free end of shaft 224 and a large hole for receiving first seal sleeve 226 and positioning it adjacent to the top surface of first end cap 204. The free end portion of the shaft 224 passes through the hole of the plate 242, is screwed to the pair of nuts 246 at the step portion, and is rotatably supported by a bearing 248 such as a ball bearing or a roller bearing. The bearing 248 is preferably disposed within a cavity 250 formed in the upper surface 205 of the first end cap 204 and a nut 246 attaches the shaft 224 to the lower surface opposite the upper surface 205 of the end cap. The free end of the shaft 224 extends a predetermined distance beyond the lower surface of the end cap 204 and serves as a drive or output shaft for the pump 200.

  The body portion 208 has a first port 252 and a second port 254, each extending between an inner surface and an outer surface of the body portion. One of the ports 252, 254 is connected to a low pressure side segment of the fluid system, such as the hydraulic fluid source 18 of FIGS. 1a-1e, and the other of the ports 252, 254 is connected to the high pressure or pressure of the fluid system. It is connected to the pressure side segment, for example the high pressure conduit 20 of FIGS. 1a to 1e.

  In operation, the shaft 224 is coupled to a prime mover, such as the engine 12 of FIGS. As the prime mover rotates the shaft 224, the gear 218 rotates, thereby causing the gear 214 to rotate. Fluid is introduced from the fluid system through one of the ports 252 or 254, taken in between the meshing teeth 216 and 220, as is well known in the art, and of the ports 252 or 254 Exhaled through the other. Appropriate passages are formed in the housing 202 to ensure that fluid is accurately routed during operation of the pump 200. The first seal sleeve 226 provides a rotational seal between the first gear 214 and the top surface 205, and the second seal sleeve 228 provides a rotational seal between the second gear 218 and the coupling 230, thereby. The integrity of the pump cavity 212 is guaranteed. The pump 200 of the present invention requires only seal sleeves 226 and 228 to maintain a seal and allow efficient operation of the pump 200.

  The normal or predetermined spatial relationship between the teeth 216, 220 of the gears 214, 218 is such that the teeth 216, 220 engage with each other over substantially all of the axial region of the teeth. In such a relationship, the pump 200 produces its maximum volumetric flow or maximum output. The pump 200 of the present invention can advantageously vary from its maximum displacement because the second gear 218 can move axially along the shaft 224. As the second gear 218 moves toward the thrust plate 242, the intermeshed area of the teeth 216, 220 is reduced, thereby reducing the volumetric flow or displacement of the pump 200. Typically, this occurs when the prime mover rotates the shaft 224 at low speed or low torque, and the pump 200 changes its output based on the internal pressure in the pump housing 202, thereby changing the input speed or input. Responds to torque reduction. In this state, the output port 252 or the output port 254 creates a high back pressure in the recess 212 and the second gear 218 is in equilibrium along the axis of the shaft 224 for the gear 218 to continue operation. And move to a location along the axis that is at or near it. Accordingly, the pump 200 is configured such that the second gear 218 is positioned substantially adjacent to the lower thrust plate 242 from the maximum output or maximum displacement where the gear 218 is positioned substantially adjacent to the joint 230. Can vary up to.

  When apparatus 200 is configured as a motor, an external pressure source, such as hydraulic fluid from an external hydraulic pump, compressed air from an air compressor, etc., causes gears 214, 218 to spin and produce output torque on shaft 224. Volume flow is provided to ports 252 and 254. When the pressure is changed, the second gear 218 moves along the axis of the shaft 224 to change the output horsepower of the motor 200. The motor 200 can advantageously be used to control the output rpm under greatly varying output loads, such as automobiles, turrets, large machines, earth movers, large drilling machines, ships, farm equipment. However, it is not limited to these.

  In operation of the system 10, the engine 12 is started and the engine supplies torque to the pump / motor 16, which supplies pressurized hydraulic fluid to the high pressure conduit 20. The accumulator 38 allows the oil pressure in the conduit 20 to remain relatively stable and store energy in a manner well known to those skilled in the art. The pressure in the conduit 20 is transmitted to the conduits 46, 62, 98.

  Referring to FIG. 1a, when the mode select valve 44 is in the D or drive position and the brake override device 54 is in the 54a position, hydraulic fluid passes through the conduit 46, through the mode select valve 44, and D Exits the conduit 50 in the direction indicated by the arrow in the position, passes through the brake override device 54, and exits the conduit 56 in the direction indicated by the arrow in the 54a position, to each upper port 77a- of the motors 76a-76d. 77d, passes through motors 76a-76d, and flows to respective lower ports 78a-78d to reduce the pressure, and in a manner well known to those skilled in the art, output torque is applied to each of motors 56a-56d in the forward direction. give. The low pressure hydraulic fluid in lower ports 78a-78d passes through conduit 58, through the brake override device, and exits conduit 52 in the direction indicated by the arrow at position 54a, through mode select valve 44, and D position. And exit the conduit 48 in the direction indicated by the arrow to the hydraulic oil source 18.

  Referring to FIG. 1b, when the mode selection valve 44 is in the N or neutral position and the brake override device 54 is in the 54a position, hydraulic fluid flows through the conduit 46 but through the mode selection valve 44. Flow is prevented by a cap located adjacent to the conduit 46 in the N position. The outlet conduits 50, 52 are in fluid communication with the low pressure hydraulic fluid in the conduit 48 so that no fluid flow occurs through the brake override device 54 or to the motors 76a-76d. This is because the pressure in conduits 50 and 56 balances the pressure in conduits 52 and 58. When in the N position, oil from reservoir 18 is available to flow to motors 76a-76d if any of motors 76a-76d requires oil flow.

  Referring to FIG. 1c, when the mode selection valve 44 is in the R or reverse position and the brake override device 54 is in the 54a position, hydraulic fluid passes through the conduit 46, through the mode selection valve 44, and in the R position. Exit the conduit 52 in the direction indicated by the arrow, pass through the brake override device 54 and exit the conduit 58 in the direction indicated by the arrow at the 54a position to the respective lower ports 78a-78d of the motors 76a-76d. As the pressure drops, the output torque is applied in a reverse direction to each of the motors 56a-56d in a manner well known to those skilled in the art. The low pressure hydraulic fluid in upper ports 77a-77d passes through conduit 56, through the brake override device, and exits conduit 50 in the direction indicated by the arrow in position 54a, through mode select valve 44, and in the D position. Exit conduit 48 in the direction indicated by the arrow to hydraulic oil source 18.

  Referring to FIG. 1d, hydraulic fluid flows through any of the conduits 46, 48, 50, 52 when the mode select valve 44 is in the P or parking position and the brake override device 54 is in the 54a position. There is no. This is because the cap located adjacent to each of the conduits 46, 48, 50, 52 in the P position prevents flow to the motors 76a-76d. As briefly described above, in the first position 54a, the brake override device 54 causes hydraulic fluid to flow between the conduits 50, 56 and between the conduits 52, 58 (depending on the position of the mode selection valve 44). ) Can flow. However, in the second position 54b, hydraulic fluid does not flow through any of the conduits 50, 52, 56, 58, as best seen in FIG. 1e. This is because the cap located adjacent to each of the conduits 50, 52, 56, 58 in the second position 54 b prevents flow through the brake override device 54. The brake override device 54 is moved from its normal first position 54a to the second position 54b by the operation of the brake 72 and the transmission of a signal along the connector 73, and the operation from the displacement control valve 44 to the motors 76a to 76d. Block oil flow.

  In operation, the only operation for the motors 76a-76d if the mode select valve 44 is in the D or drive position and the brake 72 is activated when the override device 54 is moved to the second position 54b. The oil source passes through the check valve bridge circuit 82, so all fluid flow is routed through the check valve bridge circuit 82. During braking, the motors 76a-76d begin to function as pumps and advantageously recapture energy from the rotation of the vehicle wheels during braking. During braking in the D position, hydraulic fluid flows from hydraulic fluid source 18 through conduit 94, through check valve 86, through conduit 92 and into upper ports 77a-77d to motors 76a-76d, where Increase hydraulic oil pressure. High pressure hydraulic fluid then flows from motors 76a-76d through lower ports 78a-78d through conduit 96, and when the pressure in conduit 96 is higher than conduit 98, through check valve 90 to conduit. 98, where the high pressure hydraulic fluid flows into conduit 20 and re-enters accumulator 38.

  During braking, when mode select valve 44 is in the R position, hydraulic fluid flows from hydraulic fluid source 18 through conduit 94, through check valve 88, through conduit 96, and into lower ports 78a-78d. Thus, the motors 76a to 76d are reached, and the hydraulic oil pressure is increased here. High pressure hydraulic fluid then flows from motors 76a-76d through upper ports 77a-77d through conduit 92 and, if the pressure in conduit 92 is higher than conduit 98, through check valve 84 to conduit 98. Where the high pressure hydraulic fluid flows through conduit 20 and back into accumulator 38.

  The check valve bridge circuit 82 functions to prevent the flow of hydraulic oil to the motors 76a-76d in the reverse direction once the vehicle has completely stopped. During braking, when the mode switching valve 44 is in the D position, the brake override device 54 moves to the position 54b and blocks the flow from the mode selection valve 44 to the motors 76a to 76d. The flow from the high-pressure conduit 20 attempts to reach the motors 76a to 76d via the conduit 98, but is prevented from flowing to the motor by the check valves 84 and 90. The check valve bridge circuit 82 only allows flow from conduit 92 through check valve 84 or from conduit 96 through check valve 90 to conduit 98, which is within conduits 56, 92 or conduits 58, 96. Occurs only when the pressure in the pipe is higher than the pressure in the conduit. If the pressure in conduit 92 is lower than the pressure in conduit 98 and conduit 94, check valve 86 opens, but flow from reservoir 18 to conduit 92 cannot occur because conduit 94 is in a low pressure condition. Similarly, if the pressure in conduit 96 is lower than the pressure in conduits 98 and 94, check valve 88 opens, but since conduit 94 is in a low pressure state, flow from reservoir 18 to conduit 96 is It can not occur, and advantageously, the high pressure hydraulic oil prevents the motors 76a-76d from operating in the reverse direction after the vehicle is completely stopped. In operation, the flow of hydraulic fluid through the system 10 is controlled by an operator via an accelerator 70 and a brake 72 connected to a displacement control valve 60. The connector 80 and the connecting portions 75a to 75d are connected to each other by an appropriate link device or the like, so that the motors 76a to 76d are the same as the connector 80 exerts on the control motors 76a to 76d via the connecting portions 75a to 75d. In this manner, feedback can be given to the displacement control valve 60 via the connecting portions 75a to 75d.

  For example, when a vehicle user (not shown) steps on the accelerator 70, the feedback connector 80 moves in the acceleration direction and the displacement control valve 60 moves toward the position 60a. High pressure fluid from conduit 62 flows through the port of displacement control valve 60, increasing the pressure in conduit 66 and flowing to cylinders 74a-74d. Because the pressure in conduit 66 is higher than the pressure in conduit 68, connectors 75a-75d are moved in the acceleration direction to increase displacement and thus increase the output torque of motors 76a-76d.

  Once the desired output torque of motors 76a-76d is reached, motors 76a-76d throttle the flow to move connectors 75a-75d in a decelerating direction, reducing the pressure in conduit 66 and increasing the pressure in conduit 68. Let This movement is transmitted by the feedback connector 80 and returned to the displacement control valve 60, thereby moving the displacement control valve toward the position 60b. At position 60b, there is no flow through the displacement control valve 60, thus the connectors 75a-75d remain stationary and the displacement of motors 76a-76d, and therefore the output torque, remains constant.

  When the user lifts his / her foot from the accelerator 70, the feedback connector 80 thereby moves in the decelerating direction, so that the displacement control valve moves toward the position 60c. High pressure fluid from the conduit 62 flows through the port of the displacement control valve 60, increasing the pressure in the conduit 68 and flowing to the cylinders 74a-74d. Since the pressure in the conduit 68 is higher than the pressure in the conduit 66, the connectors 75a-75d are moved in the deceleration direction to reduce the displacement and thus reduce the output torque of the motors 76a-76d.

  Advantageously, there is no direct connection between the accelerator 70 and the engine 12. Unlike this, the engine 12 is driven by engine speed (based on the signal on the line 42), torque (based on the position of the displacement control valve 60, which is affected by the position of the accelerator 70), system pressure, Actuated and controlled based on a combination (based on signal on line 38a). This combination of inputs allows the throttle control module 40 of the system 10 to operate the engine 12 at its peak efficiency based on known engine efficiency parameters and thus provide proportional control of the engine 12 and the system 10. When the system 10 is fully charged, the engine 12 may advantageously be turned off, thereby reducing instantaneous fuel consumption to zero. When the system pressure decreases, the engine 12 is restarted and pressure is again applied to the conduit 20.

  Based on the conditions or operating conditions of the air conditioning compressor 24, power maintenance module 28 and accumulator 38 (determined by their respective signals on lines 24a, 28a, 38a), the throttle control module 40 signals on line 42. To start or stop the engine 12 and / or change the displacement of the pump / motor 16.

  As system pressure in conduit 20 increases, accumulator 38 fills and the flow from pump / motor 16 decreases. The flow rate of the pump / motor 16 continues to decrease until the system pressure decreases due to the output to the motors 76a-76d. If at any point the flow from the pump / motor 16 reaches zero, the engine 12 may be turned off until flow is required again. The flow rate from the pump / motor 16 also assumes that the auxiliary equipment needs power to prevent the engine 12 from slowing (assuming the auxiliary equipment is coupled to the engine 12 via a clutch). May also decrease. The powertrain system 10 obtains its efficiency by averaging power consumption. The energy required for the intermittent burst is provided by the stored energy in the accumulator 38. The pump / motor 16 provides a flow rate that is higher than the average flow rate required to propel the vehicle. In this case, the excess flow rate obtained by the pump 16 is stored in the accumulator 38.

  The hydraulic hybrid powertrain system 10 of the present invention advantageously is complex for the system 10 because the output torque response from these motors 76a-76d is very rapid once the displacement is increased. Rather, it provides a simple control methodology and a very responsive control means.

  As will be appreciated by those skilled in the art, the system 10 of the present invention can be used to provide hydraulic power to an unspecified number of systems including, among other things, ships that can float or dive, such as , Propulsion systems for ships, boats or submarines, and propulsion systems for helicopters. In short, when the output of the pump / motor 16 is utilized in the power train system 10, an unspecified number of hydraulic motors, such as motors 76a-76d, can be operated for many purposes that are within the scope of the present invention. .

  The signals on connectors 73, 75a-75d, 80 and lines 24a, 28a, 38a, 42 are electrical signals in communication with any type of mechanical connector, such as a hydraulic line, cable, metal rod or solenoid valve. These may be included and fall within the scope of the present invention.

1 is a schematic diagram of a hydraulic hybrid powertrain system of the present invention showing a mode selection valve in a “drive” position. FIG. 1b is a diagram of the hydraulic hybrid powertrain system of FIG. 1a, with the mode selection valve in a “neutral” position. 1b is a diagram of the hydraulic hybrid powertrain system of FIG. 1a showing the mode selection valve in a “reverse (back)” position. FIG. 1b is a diagram of the hydraulic hybrid powertrain system of FIG. 1a showing the mode selection valve in a “parking” position. FIG. FIG. 1b is a diagram of the hydraulic hybrid powertrain system of FIG. 1a showing the brake override device in the override position. FIG. 2 is a schematic enlarged view of the drive motor and the displacement control device shown in FIGS. FIG. 2 is a schematic enlarged view of the brake override device and the check valve bridge circuit shown in FIGS. 1 is an exploded perspective view of an internal gear pump / motor of the present invention. FIG. 1 is a partially exploded perspective view of a circumscribed gear pump / motor of the present invention. FIG. It is an enlarged view of the gear meshing device and method of the present invention.

Claims (10)

A pump gear set 300,
A drive gear 310;
An idler gear 312 meshed with the drive gear 310, the gears 310, 312 initially meshing at a first location 314 of the two locations 314, 316 along the corresponding tooth profiles 318, 320; Next, cod also sealed region 322 between the gears 310 and 312 each other in a fluid device meshes at the second location 316 of the two locations,
The pump gear set 300 , wherein the first of the two meshing locations 314, 316 includes a root portion 326 of one gear tooth and a tip portion 328 of opposing gear teeth . Of the two meshing locations 314 and 316, the second location is such that when the gears 310 and 312 are rotatably engaged, the root portion 326 and the tip 328 of the location 314 are the gear teeth. A portion 316 located along the side of one gear tooth profile 318 that meshes with a location 316 along the opposite gear tooth profile 320 side when disengaged to form a region 322 for sealing. Item 3. A pump gear set 300 according to item 1 . The pump gear according to claim 2 , wherein the sealing region is a means for allowing the fluid 324 to escape hydrostatically when the first meshing portion 314 of the gear teeth is disengaged. Set 300. A low noise gear set 300 for a power plant 11, said power plant driving an pump 12 connected to a low pressure fluid source 18 to produce a high pressure fluid at outputs 107, 252 and 254; And at least one variable displacement pump / motor 16 that produces rotational motion at outputs 107, 252, and 254 in response to the high pressure fluid;
The variable displacement pump / motor 16 includes a drive gear 310 and an idler gear 312 meshing with the drive gear 310, and the idler gear 312 is initially aligned with the corresponding tooth profile 318, 320 of the gear. Meshing with the drive gear 310 at one location 314;
The first location 314 is a root portion 326 of one gear tooth meshing with the tip portion 328 of the opposite gear tooth, and the low pressure fluid source 18 is connected between the root portion 326 and the tip portion 328. Creating a first contact point 314 to obtain a fluid seal 322;
When the teeth engage with each other, there is a second second location 316 along the tooth profile 318, 320, and when disengaged at the high pressure fluid output 107, 252, 254, the fluid 324 is at the location 314, A low-noise gear set 300 that can hydrostatically escape between 316. Of the two meshing locations 314 and 316, the second location 316 is the gear teeth while the locations of the root portion 326 and the tip portion 328 are disengaged when the gears 310 and 312 are engaged. when forming the region 322 for sealing the consist portion 316 located along the sides of one of the gear teeth 318 meshing with the portion 316 along the side of the opposing gear tooth 320, claim 4, wherein Low noise type gear set 300. 6. The low noise of claim 5 , wherein the sealing region 322 provides a means for allowing fluid 324 to escape hydrostatically when the first meshing location 314 of the gear teeth is disengaged. Mold gear set 300. A gear set that reduces wear by creating hydrostatic bearings between the contact surfaces of the gear 300;
Having at least two gears 310, 312, wherein the gears 310, 312 are at least two locations 314, 316 of the tooth profiles 318, 320, which correspond to provide a seal 322 between the gears 310, 312 in a fluidic device have if chewed one after another to each other along the,
The first set 314 of the two meshing locations 314, 316 includes a gear tooth root 326 and an opposing gear tooth tip 328, the gear set 300. Of the two meshing locations 314 and 316, the second location 316 seals the gear teeth when the gears 310 and 312 are engaged with each other at the root portion 326 and the tip portion 328. when you are disengaged from each other so as to form a region 322 for, consists of portions 316 positioned along the sides of one gear tooth 318 which meshes with portion 316 along the side of the opposing gear tooth 320, claim 7 The gear set 300 described. 9. The gear set 300 of claim 8 , wherein the sealing region 322 provides a means for allowing fluid 324 to escape hydrostatically when the gear teeth are disengaged. A method for providing a low-noise gear pump with reduced wear of the gear 300,
a. Providing a first gear 310;
b. Engaging the first gear 310 with a second gear 312 at a first meshing location 314, wherein the first meshing location 314 includes a root 326 of one gear tooth and an opposing gear; A tooth tip 328;
c. Engaging the first gear 310 with the second gear 312 at a second meshing location 316, the second meshing location 316 being on the side of the tooth profile 320 of the opposing gear. It is a location along the side of the tooth profile 318 of one gear meshing with the location along
d. Forming a region 322 that seals the gear teeth when the gears 310, 312 are engaged at the second meshing location 316 and disengaged from the first meshing location 314;
e. Providing the means for fluid 324 to escape hydrostatically when the gear teeth are disengaged at the first engagement point 314.

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