WO1998006612A1

WO1998006612A1 - Dual action ball screw pump

Info

Publication number: WO1998006612A1
Application number: PCT/US1997/014387
Authority: WO
Inventors: Blaise J. Ganzel
Original assignee: Kelsey Hayes Company
Priority date: 1996-08-13
Filing date: 1997-08-13
Publication date: 1998-02-19
Also published as: AU4069497A

Abstract

A ball screw pump assembly (200) includes a pump body having an axial bore defining a travel chamber (226) and a pressure chamber (225). An input port (230) and an output port (236) are formed in the pressure chamber (225). A ball screw (205) is provided in the travel chamber (226). A piston (220) is connected to the ball screw (205) and slidably extends into the pressure chamber (225) as the ball screw (205) is rotated. The piston (220) divides the pressure chamber (225) into an input chamber having a maximum volume and an output chamber having a maximum volume which is less than the maximum of the input chamber. The ball screw assembly (200) can be used in a vehicular braking system.

Description

TITLE DUAL ACTION BALL SCREW PUMP

BACKGROUND OF THE INVENTION This invention relates in general to a pump and in particular to a ball screw pump for use in a pressurized fluid system, including vehicular Anti- lock Traction Control/Vehicle Stability Control braking systems.

Vehicles are commonly slowed and stopped with hydraulic braking systems. These systems vary in complexity but a base brake system typically includes a master cylinder, pressure fluid conduit, and a wheel brake cylinder. The master cylinder generates hydraulic forces by pressurizing brake fluid when the driver applies a brake pedal. The pressurized fluid travels through the pressure fluid conduit to actuate the brake cylinders at the wheels and slow the vehicle, Vehicle braking systems have evolved beyond the base braking system to provide improved brake pressure regulation resulting in increased versatility. Anti-lock Braking Systems (ABS) provide decreased stopping distances and controlled braking under adverse conditions. An ABS system monitors wheel rotational behavior and regulates the brake pressure in the corresponding wheel brakes in order to maintain the wheel speed within a selected slip range while achieving maximum braking forces. A Traction Control (TC) system controls excessive wheel slip during acceleration to improve vehicle traction. A Vehicle Stability Control (VSC) system automatically actuates selective wheel brakes to counteract dynamic forces generated during cornering which improves vehicle stability.

Typical ABS/TC VSC systems use a motor driven pump to provide pressurized fluid used to actuate the wheel brake cylinders. The pump must provide a sufficient capacity of fluid at high pressure for these braking systems to operate properly, Pump noise is a common problem for pumps meeting the pressure and capacity requirement of vehicle braking systems. A noisy pump can be displeasing to the driver. Additionally, many pumps produce undesirable large pressure pulses which can be felt by the driver. It would be desirable to provide a pump for use in vehicular braking systems that is quiet and produces a smooth high pressure output without pressure spikes.

SUMMARY OF THE INVENTION This invention relates to a dual action ball screw pump for pressurized fluid systems, including vehicular ABS TC/VSC braking systems. The pump can also be used in active and partially active suspension systems or any other use requiring pressurized fluid. The pump provides quiet, smooth operation by using a dual action piston attached to a nut which is reciprocated on a ball screw. The pump has an input chamber and an output chamber having approximately half the volume of the input chamber. The piston produces an input stroke when moved in one direction and outputs fluid when moved in either direction.

In a preferred embodiment, a pump assembly includes a pump body having an axial bore defining a travel chamber and a pressure chamber. An input port and an output port are formed in the pressure chamber. A ball screw is provided in the travel chamber. A piston is connected to the ball screw and slidably extends into the pressure chamber as the ball screw is rotated. The piston divides the pressure chamber into an input chamber having a maximum volume and an output chamber having a maximum volume which is less than the maximum of the input chamber.

Various objects and advantages of this invention will become apparent to those skilled in the art from the following detailed description of the preferred embodiment, when read in light of the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is an axial sectional view of a pump body according to this invention illustrating a travel chamber and a pressure chamber. Fig. 2 is an end view of the pump body of Fig. 1. Fig. 3 is an axial sectional view of a pump assembly according to this invention mounted on the pump body of Figs. 1 and 2.

Fig. 4 is an enlarged perspective view of a cage of the pump assembly of Fig. 3 removed from the pump assembly for clarity of illustration.

Fig. 5 is a sectional view of the pump assembly taken along line 5-5 of Fig. 3.

Fig. 6 is a graph illustrating fluid flow into and out of the pump assembly versus time.

Fig. 7 is an axial sectional view of a first alternate embodiment of a pump assembly according to this invention. Fig. S is an axial sectional view of a second alternate embodiment of a pump assembly according to this invention.

Fig. 9 is a schematic representation of a vehicular braking system in which a pump assembly according to this invention can be incorporated.

Fig. 10 is a schematic representation of a vehicular braking system having a separate boost valve hydraulically connected to a pump assembly according to this invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A preferred embodiment of a ball screw pump according to the present invention is illustrated in Figs. 1- 5. Referring now to Fig. 1, the pump body 1 is shown having an axial bore 2 formed therein. The bore 2 has a first portion having a larger inner diameter which forms a travel chamber 2a, a second portion having a smaller inner diameter which forms a pressure chamber 2b, and an intermediate portion having the smallest diameter forming shoulder 2c. An annular groove 22 is formed in the shoulder 2c.

A plug 50 is inserted into the end of d e pressure chamber 2b. An input port 51 and output port 52 are formed through the body 1 into the pressure chamber 2b. The input port 51 has a one-way check valve 53 which allows fluid to flow only into the pressure chamber 2b. The output port 52 has a one-way check valve 54 which allows fluid to flow only out of the pressure chamber 2b. A conduit 55 connects the left and right ends of the pressure chamber 2b. A one_¬ way check valve 56 allows fluid to flow only from the left end to the right end of the pressure chamber 2b. A plug 57 is pressed into the end of conduit 55. The body has a flange 58 with through holes 59. An axial groove 60 is formed in the wall of the travel chamber 2b.

Fig. 2 illustrates an end view of the pump body 1. The bore 2 forming the travel chamber 2a is preferably formed concentrically with the flange 58. The axial groove 60 is shown in the upper portion of the bore 2.

Referring now to Fig. 3, a pump assembly 100 is shown. A motor 3 is attached to the body 1 by bolts (not shown) through holes 59. A cylindrical ball screw 5 is provided within the travel chamber 2a. A spiral groove 6 extends over most of the outer circumference of the ball screw 5. A bearing 7 supports the ball screw 5 where it attaches to the motor shaft (not shown). A nut 8 having a central through bore 9 is located on the ball screw 5 in the travel chamber 2a. Complementary grooves 10 are formed on the inner surface of the nut bore 9 which correspond to the ball screw grooves 6. Friction reducing balls 13 are located between the nut grooves 10 and screw grooves 6. The balls 13 engage both the screw 5 and the nut 8 and transfer torque therebetween. A cap 11 is formed on a portion of the outer periphery of the nut 8. The cap 11 has a spiral conduit 12 connecting the grooves 10 on the left and right sides of the nut 8 thereby forming a return path for the balls 13. A hollow cylindrical piston 20 has a first portion 20a extending into both the travel chamber 2a and the pressure chamber 2b and a second portion 20b housed in the pressure chamber 2b. The outer diameter of the first portion 20a is slightly smaller than the diameter of the shoulder 2c. An O-ring seal 21 is located in the annular groove 22 in the shoulder 2c to prevent fluid in the pressure chamber 2b from entering the travel chamber 2a. The second piston portion 20b has an outer diameter slightly smaller than the inner diameter of the pressure chamber 2b. A second O-ring seal 23 is located in a groove 24 in the second piston portion 20b. The seal 23 divides the pressure chamber 2b into an input chamber 25 and an output chamber 26 and prevents fluid from flowing around the second piston portion 20b and moving between chambers 25 and 26.

A cylindrical guide pin 30 is located in the pressure chamber 2b and includes a shoulder 31. A third O-ring 32 is located in a circumferential channel 33 in die guide pin shoulder 31 and forms a fluid tight seal at the end of the pressure chamber 2b. Belleville springs 34 are located between the shoulder 31 and the plug 50 for cushioning movement of the guide pin 30 towards the plug 50. A shoulder 37 is formed in the wall of the pressure chamber 2b. The guide pin shoulder 31 abuts the pressure chamber shoulder 37 to prevent movement of the guide pin 30 to the right. The end of the guide pin 30 opposite the shoulder 31 extends within the piston 20 and has a circumferential channel 35. A fourth O-rin 36 is seated in d e channel 35 and forms a fluid-tight seal between the guide pin 30 and the piston 20.

The piston 20 is connected to the nut 8 by a hollow cylindrical cage 14. The cage 14 is shown in Fig. 4 removed from assembly 100. The cage 14 is a cylindrical member having a shoulder 61 at one end and internal threads 62 at the other end. An axial cut-out 16 extends along a substantial portion the length of die cage 1 . The cage 14 surrounds die nut 8 and die shoulder 61 holds bellevillc springs 15 near the nut 8. The cap 11 extends through d e cut-out 16. The first piston portion 20a has an end 20c with external threads 20d. A connecting nut 71 having both internal and external tiireads (not shown) is screwed onto the piston end 20c. This nut 71 is then screwed into internal threads 62 of the cage 14, thereby connecting the piston 20 to the cage 14. The cage shoulder 61 confines the nut 8 within the cage 14, thereby connecting the piston 20 to the nut 8 for reciprocal movement.

Referring now to Fig. 5, the nut 8 is shown on the ball screw 5. The cage 14 coaxially surrounds the nut. The cap 11 protrudes Λrough the cut-out 16 in the cage 14. The cap 11 also protrudes into the groove 60 formed in the pump body 1.

The operation of the pump shall now be described. The motor 3 turns the ball screw 5. The nut cap 11 abuts defining walls of groove 60 and the nut 8 is prevented from rotating with the ball screw 5. The rotating ball screw 5 causes the nut 8 to be displaced axially along the length of the ball screw 5. As die ball screw 5 turns and the nut 8 moves, me balls 13 move in a path between grooves 6 and 10. The continuous path extends from the first end of die conduit 12, around die screw 5 and into die second end of die conduit 12.

The direction in which the nut 8 moves depends on die direction of rotation of die ball screw 6. The cage 14 connects die piston 20 to the nut 8 so the piston 20 is moved left or right with the nut 8 as the motor turns. The piston 20 is reciprocated back and forth by reversing die direction of die motor 3.

When the piston 20 moves from the left end of die pressure chamber 2b to right end, fluid is drawn through die check valve 53 and into the input chamber 25. The second piston portion 20b is moved to the right most end of the pressure chamber 2b thereby drawing the maximum amount of fluid tiirough input port 51. The beileville springs 15 prevent die nut 8 from jamming as the nut 8 travels to die right side of the travel chamber 2a. The input chamber 25 has now reached maximum volume approximately equaling die volume of die pressure chamber bore 2b minus die volume occupied by die guide pin 25. When the piston 20 moves right, the fluid in the output chamber 26 is prevented from entering the input chamber 25 by check valve 56. Instead, die fluid is forced through check valve 54 and out the output port 52. The output chamber 26 is largest when the piston 20 is at the left most end of the pressure chamber 2b. At this position, the output chamber 26 is approximately equal to the volume of e pressure chamber bore 2b minus the volume occupied by the piston 20. The maximum volume of the output chamber 26 is approximately half the maximum volume of die input chamber 25. When the piston 20 moves from right to left, fluid in die input chamber 25 is forced into d e output chamber 26 through conduit 55 and check valve 56. Half of the fluid from die input chamber 25 is forced out the output port 52 because the maximum volume of the output chamber 26 is only half as large as the maximum volume of d e input chamber 25. Fig. 6 illustrates a graphical representation of the fluid flow bod into and out of d e pump assembly 100. Line 80 is the fluid flow into d e pump 100 through die input port 51 when the piston 20 moves from left to right. Line 81 is die flow out of die pump 100 through the output port 52 during this time. Line 82 is the flow out of the outiet port 52 when the piston 20 moves from right to left.

This dual action ball screw pump 100 provides high pressures with quiet operation . The ball screw 5 is directly driven by die pump motor 3 eliminating a prior art gear which further reduces noise. The output flow is smootii and free of pressure spikes as illustrated in Fig. 6. It will be appreciated that a single action ball screw pump is contemplated within this invention. For example, by removing check valve 54 at the output port 52, the ball screw pump 100 will function as a single action ball screw pump. Fig. 7 shows an alternate embodiment of a bail screw pump 200 according to the invention. A piston 220 is slidably disposed in a pressure chamber 219. The piston is connected to the nut 210 via a cage 214. A ball screw 205 is threaded through the nut 210 and is prevented from rotating. The ball screw is connected to a motor 203 which turns the ball screw in both directions. As the ball screw 205 turns, it moves e nut 210 and d erefore the piston 220. The piston 220 sealingly divides die pressure chamber 219 into a first chamber 225 and a second chamber 226. An input port 230 is connected to die first and second chambers 225, 226 via conduit 232. One-way check valves 234 are located in conduit 232 which allow fluid to flow through the input port 230 and into the first and second chambers 225, 226 but not in the opposite direction. An output port 236 is connected to the first and second chambers 225, 226 via conduit 238. One-way check valves 240 are located in conduit 238 which allow fluid to flow out of the first and second chambers 225, 226 but not in the opposite direction. As the piston 220 moves to the left, the fluid in the first chamber 225 is expelled through the one-way check valve 240 and out the output port 236, while fluid is drawn into die second chamber 226 through the input port 230 and one-way check valve 234. The piston 220 then moves to die right as shown in Fig. 7 and the fluid in the second chamber 226 is expelled through die one-way check valve 240 and out die output port 236, while fluid is drawn into the first chamber 226 through the input port 230 and one-way check valve 234.

Fig. 8 shows an second alternate embodiment of a ball screw pump 300 according to the invention. This embodiment is similar to the pump 100 shown in Fig. 3 and only i e differences will be described. The nut 308 is disposed coaxially about die ball screw 305 similar to pump 100. The piston 320 is coaxially disposed about die ball screw 305 and is attached to d e nut 308 by a threaded connection 321. The piston 320 reciprocates in a similar manner as die piston 20 in die pump 100 shown in Fig. 3. An O-ring 323 is disposed in a groove 324 in the outer surface of the end of the piston 320. The piston 320 is disposed in die pressure chamber 302b. A polytetrafluoroethylene (e.g., Teflon) ring 325 is disposed over the O-ring 323. The O-ring 323 and polytetrafluoroethylene (e.g.. Teflon) ring 325 act together to seal the end of the piston 320 thereby sealingly separating die pressure chamber 302b into an input chamber 325 and die output chamber 326. The O-ring 323 and polytetrafluoroethylene (e.g., Teflon) ring 325 also reduce the friction between die reciprocating piston 320 and the wall of the pressure chamber 302b. The piston 320 is coaxially disposed about a cylindrical guide pin 330 in a manner similar to the pump 100 shown in Fig. 3. A polytetrafluoroethylene (e.g., Teflon) ring 334 and an O-ring 335 are disposed in a groove 336 in die guide pin 330 to provide a seal between the guide pin and d e piston 320 while reducing die friction tiierebetween. A sleeve 340 is coaxially disposed about die piston 320. An O-ring 342 and polytetrafluoroediylene (e.g.. Teflon) ring 344 are disposed in a groove 346 on an inner surface of the sleeve 340. An O-ring 348 is disposed in a groove 350 in ie outer surface of the sleeve 340. The O- ring 342 and polytetrafluoroethylene (e.g., Teflon) ring 344 provide a seal between die piston 320 and die sleeve 340 which, together with the outer O-ring 348, sealingly separate the output chamber 326 from die travel chamber 302a. The sleeve 340 is attached to die motor housing 352 by a threaded connection 354 and does not move during operation of the pump 300. A slot 360 extends axially along the sleeve 340. The nut cap 311 extends into the slot 360 which prevents the nut from rotating as the ball screw rotates. Since die nut 308 is prevented from rotating when die ball screw 308 is turned by the motor (not shown), the nut moves axially along die ball screw and reciprocates the attached pis_ton 320. The belleville springs 315 are attached to die pump body 1 and do not travel with the nut 308, unlike d e belleville springs 15 in the pump 100 shown in Fig. 3. The pump 300 operates in a similar manner as pump 100 shown in Fig. 3.

The pump 300 is easier to assemble than die pump 100 shown in Fig. 3. The piston 320 can be screwed into the nut 308 and the motor 352, sleeve 340, ball screw 305, nut 308 and piston 320 can be inserted into die pump body 301 from one direction, as a single unit. The assembly of pump 100 shown in Fig. 3 is more difficult because the piston 20 must be inserted into the pump body from the opposite end as die ball screw 5 and nut 11. The piston 20 must men be joined to die nut 11 and cage 14 while these components are inside the pump body 1 which makes assembly more difficult.

A schematic diagram for one wheel of a vehicular anti-lock braking system 400 is illustrated in Fig. 9. The braking system 400 includes a hydraulic control unit 402 formed as a housing containing valves and oti er components as described below. For purposes of clarity of illustration, only one set of components is shown in Fig. 9. Typically, however, the hydraulic control unit 402 also embodies corresponding components for odier wheels of the vehicle in a well known manner.

The braking system 400 includes a brake pedal 404 connected to master brake cylinder 406. When the brake pedal 404 is depressed, die master cylinder 406 provides pressurized brake fluid to a brake cylinder 408 of a wheel brake assembly 410.

The hydraulic control unit 402 includes a normally open isolation valve 412 disposed between die master cylinder 406 and die brake cylinder 408, a low pressure accumulator 414, a normally closed dump/hold valve 416 disposed between the brake cylinder 408 and the low pressure accumulator 414, and a hydraulic pump assembly 420 connected between the low pressure accumulator 414 and the isolation valve 412. When d e braking system 400 is functioning in an anti-lock mode, die isolation valve 412 is closed, and die hold/dump valve 416 is opened to permit fluid to flow from the brake cylinder 408 into die low pressure accumulator 414. The pump assembly 420 is operated to pump fluid from ύvs low pressure accumulator 414 back to the inlet side of die isolation valve 412 in a well known manner. According to this invention, any of die pump assemblies 100, 200, 300 can be used for pump assembly 420 in die braking system 400. Furthermore, pump assemblies 100, 200, and 300 can be used in vehicular braking systems having traction control and or vehicle stability control. A schematic representation of a vehicular integrated ABS/TC/VSC braking system 500 having a separate boost is illustrated in Fig. 10. A ball screw pump assembly 580 is used to charge an accumulator 570. In the illustrated embodiment, a spring accumulator 570 includes a pressure responsive bypass valve 575. The ball screw pump assembly 580 is used as die single auxiliary pressure source. Any of die pump assemblies 100, 200, 300 can be used for pump assembly 580.

The braking system 500 includes a master cylinder assembly 502 having a master cylinder 504 and a booster 506. The booster 506 is hydraulically connected to a separate boost valve 508. A reservoir 510 is hydraulically connected to die master cylinder 504. Conduits carry hydraulic brake fluid to isolation and dump valves for each of the vehicle wheels. Braking system 500 is disclosed in United States provisional patent application 60/023,939, filed August 14, 1996, assigned to die present assignee, and hereby incorporated by reference. In accordance with the provisions of the patent statutes, die principle and mode of operation of this invention have been described and illustrated in its preferred embodiment. However, it must be understood tiiat this invention may be practiced otherwise than as specifically explained and illustrated without departing from its spirit or scope. The pump may be used in braking systems, active and partially active suspension systems or any odier use requiring pressurized fluid.

Claims

CLAIMSWhat is claimed is:

1. A vehicular braking system for hydraulically actuated wheel brakes comprising: a hydraulic control unit for controlling application of pressurized fluid to the wheel brakes; at least one fluid control valve mounted on die hydraulic control unit hydraulically connected to the wheel brakes; and a ball screw pump assembly for providing a source of pressurized fluid for the braking system.

2. The vehicular braking system defined in Claim 1 wherein d e ball screw pump assembly provides pressurized fluid to die fluid control valve.

3. The vehicular braking system defined in Claim 1 wherein the ball screw pump assembly provides pressurized fluid to an accumulator.

4. The vehicular braking system defined in Claim 1 wherein the ball screw pump assembly is a dual acting ball screw pump.

5. The vehicular braking system defined in Claim 1 wherein the ball screw pump assembly is a single acting ball screw pump.

6. The vehicular braking system defined in Claim 1 wherein the ball screw pump assembly includes: a pump body having an axial bore defining a travel chamber and a pressure chamber; an input port and an output port formed in the pressure chamber; a ball screw provided in the travel chamber; and a piston connected to d e ball screw and extending into the pressure chamber so that the piston slidably travels in the pressure chamber as the ball screw is rotated.

7. The vehicular braking system defined in Claim 6 wherein die piston divides the pressure chamber into an input chamber having a maximum volume and an output chamber having a maximum volume which is less than the maximum volume of me input chamber.

8. The vehicular braking system defined in Claim 7 wherein the maximum volume of the output chamber is approximately half the maximum volume of d e input chamber.

9. The vehicular braking system defined in Claim 3 including a boost valve hydraulically connected to die ball screw pump assembly.

10. The vehicular braking system defined in Claim 9 including a master cylinder assembly hydraulically connected to the boost valve and hydraulically connected to die hydraulic control unit.

11. The vehicular braking system defined in Claim 6 a sleeve is disposed about the piston and connected to a motor attached to die pump body.

12. The vehicular braking system defined in Claim 7 wherein die a pair of input ports are provided for the input chamber and a pair of output ports are provided for the output chamber.

13. A ball screw pump assembly for a pressurized fluid system comprising: a pump body having an axial bore defining a travel chamber and a pressure chamber; an input port and an output port formed in the pressure chamber; a ball screw provided in d e travel chamber; a piston connected to the ball screw and extending into the pressure chamber, the piston slidably traveling in the pressure chamber as the ball screw is rotated.

14. The ball screw pump assembly defined in Claim 13 wherein the ball screw pump assembly is a dual acting screw pump.

15. The ball screw pump assembly defined in Claim 13 wherein d e piston divides the pressure chamber into an input chamber having a maximum volume and an output chamber having a maximum volume which is less than d e τnnviτnιιτn volume of die input chamber.

16. The ball screw pump assembly defined in Claim 13 wherein d e maximum volume of the output chamber is approximately half the maximum volume of die input chamber.

17. The ball screw pump assembly defined in Claim 13 wherein a sleeve is disposed about die piston and connected to a motor attached to the pump body.

18. The ball screw pump assembly defined in Claim 15 wherein the a pair of input ports are provided for the input chamber and a pair of output ports are provided for die output chamber.

S 19. The ball screw pump assembly defined in Claim 13 wherein the pressure chamber is hydraulically connected to an accumulator of a vehicular braking system.

20. The ball screw pump assembly defined in Claim 13 wherein die 0 pressure chamber is hydraulically connected to a fluid control valve of a vehicular braking system.