• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The disclosure relates to a cheek plate unloading pump for supplying fluid to a system. The pump has a discharge port concentric with its axis of rotation. The pump includes a rotor, a cam encircling said rotor and means for effecting relative rotation of the cam and rotor about an axis. A plurality of vanes are carried by the rotor and engage the cam to define pumping pockets which expand and contract on rotation of the rotor. A cheek plate extends radially of the axis and is disposed adjacent one axial side of the rotor and cam. The cheek plate is movable along the rotational axis to communicate expanding and contracting pumping pockets. ¡There is a cavity on one side of the cheek plate, and a fluid passage conducts fluid pressure into the cavity which fluid pressure biases the cheek plate into a position blocking the flow of fluid from the contracting pumping pockets to the expanding pumping pockets. The pump also includes a servo valve for venting the pressure in the cavity to thereby control the flow of fluid between the contracting and expanding pumping pockets. A fluid passage in the cheek plate receives flow from the contracting pockets. The passage has a portion directing flow from the contracting pumping pockets radially inwardly of the cheek plate. A tubular member is fixedly attached to the cheek plate coaxially with the axis of relative rotation of the rotor, and the interior of the tubular member communicates with the portion of the fluid passage directing flow radially inwardly. A housing member defines a chamber in which the cam ring, rotor and cheek plate are located, and the housing has a discharge orifice coaxial with the tubular member. A seal is provided between the tubular member and the housing member enabling the tubular member to move with the cheek plate relative to the housing member while maintaining the seal. A droop in the output flow rate is achieved by a variable control orifice which is in part defined by a tapered surface on the tubular member. As the cheek plate and tubular member move away from the cam and rotor, the tapered surface moves to decrease the size of the control orifice. This, in turn, decreases the pressure acting on one end of the servo valve spool and further reduces the output flow of the pump, thereby causing the desired droop.
    公开号:SU1245266A3
    申请号:SU823444078
    申请日:1982-05-06
    公开日:1986-07-15
    发明作者:Х.Дратчас Джилберт
    申请人:Трв,Инк (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to pump construction, in particular, to vane pumps for supplying fluid to a hydraulic system with means for discharging a pump from pressure.
    The aim of the invention is to reduce the size and reduce the flow of fluid into the hydraulic system when the discharge rate exceeds a predetermined.
    FIG. 1 shows a vane pump, a longitudinal section; in fig. 2 is a section A-A in FIG. one; in fig. 3 is a section BB in FIG. one; in fig. 4 - section BB in FIG. 4, section G-D in FIG. Section D-D in FIG. Section E-E in FIG. GF in FIG. one; in fig. 9 is a view of FIG. eight; in fig. 10 is a cross-section K-K in FIG. 9; in fig. 11 is a section L-L in FIG. one; in fig. 12 is a cross section in FIG. eleven; in fig. 13 is a section HH in FIG. 12; ya fig. 14 - blade pump in the area of the servovalve; in fig. 15 - servo valve moved to the working position; in fig. 16 is a graph of pump performance.
    The blade pump contains rotor 2 located in the housing 1 and the cam 3 element encompassing it; in fig. 3, in FIG. 3; in fig; in fig.
    5 6 7
    The rotor element 2 has radial grooves 4 with blades 5 installed with the possibility of contact during rotation of the rotor element 2 by means of a drive with a cam element 3 with the formation of a plurality of working chambers 7 of variable volume, alternately communicated with the inlet 8 and the outlet 9 of the pump. The pump has means for adjusting its volumetric feed, including perpendicular to the axis of rotation and mounted for axial movement in the control chamber 10 and pressed by the spring 11 to one side of the rotor 2 and the cam 3 elements side plate 12 for separation and communication of the working chambers 7 among themselves, while the other sides of the rotor 2 and cam 3 elements are in constant contact with the cover 13 of the housing 1.
    Pump means defining adjustable throttling from
    five
    0
    Version 14, including a conical element 15 and a sleeve 16 connected to the side plate 12, fixed in the housing 1 between the pump outlet 17 and the entrance to the heating pipe (not shown), connected to the axial hole 18 in the housing 1. the cross section of the throttling hole 14 is reduced by moving the side plate 12 away from the rotor 2 and cam 3 elements, and the increase is due to moving the side plate 12 to the rotor 2 and cam 3 elements. The outlet 17 and the axial 18 holes in the housing are communicated with the channels with the end surfaces 19 and 20 of the servoclaval 21, designed to control the pressure in the control position 10 of the side plate 12.
    The housing 1 is enclosed by a shell 22, the internal cavity 23 of which serves as a reservoir for the liquid transferred by: a pump into which fluid returns from the system through the inlet 8.
    A cavity 23 is connected by a channel 24 in the spruce 1 with a collective chamber 25 of this body, which encloses the cam element 3.
    On the end surface 26 of the cam element 3 are two diametrically opposite grooves 27
    5 and 28 for communication with the annular chamber 25. The end face 29 of the cam element 3 ,. protisopoic. surface 26 also has two slots 30 and 31. The grooves 27 and 28 of the cam element 3 are turned along the input channels 32 and 33 formed in the cover 13, which also has input channels 34 and 35. With the help of channels 34 and 35 the working fluid is supplied to
     heating chambers in the rotor element 2 and to the blade 5. The channel 32 is connected to the channel 34 by means of the channel 36 in the lid 13, and the cannula 33 is connected to the channel 35 when it is shrouded.
    0 of channel 37. With the help of channel 37, the drive shaft 6 is also lubricated. The grooves 30 and 31 are facing along the inlet channels 38 and 39 in the side plate 12, which is adjacent to the lateral side 29 of the cam element 3 and the lateral surface of the rotor 2. Channels 40 and 41 located on the same diameter, smaller than the diameter
    0
    3
    the locations of the channels 38 and 39 and serve to supply the liquid blade 5
    one
    Channels 38, 39, 40 and 41 are located axially opposite to channels 33, 35, 32 and 34 in krppka 13 housing 1.
    When the pump is operating, the fluid from the cavity 23 through the channel 34 enters the annular chamber 25 and further into the inlet channels connected with the working chambers 7, the volume of which increases. The pressure in the various inlet channels 32, 33, 34, 35, 38, 39, 40 and 4 is the same and is defined as the inlet pressure. With a decrease in the volume of the working chambers 7, the working fluid is expelled from them into the outlet channels 42, 43, 44, 45 in the crew 13 of the housing 1. Channels 42 and 43 are interconnected by channel 46. Channels 43 and 45 are interconnected by channel 47 and are located on a diameter smaller than the diameter of the channels 42 and 44 and serve to receive liquid displaced from under the blades 5. Flow from The channels 42, 43, 44 and 45 are guided through the cam element 3 to the surface 29 in the side plate 12 through the channels 48 and 49 facing the channels 42 and 43, respectively.
    At the same time, the working fluid from the working chambers 7 is displaced into the outlets 50, 51, 52 and 53 of the side plate 12. All the channels 50, 51, 52 and 53 are connected to the chamber 54 located on the inner side of the side plate 12. In addition, the channels 48 and 49 in the cam element 3 are connected to the channels 50 and 52 of the side plate 12, so the entire output flow from the working chambers accumulates in the chamber 54, and the pressure in this chamber is the output pressure of the pump.
    The entire flow from chamber 54 is directed through the arcuate groove 55 in the side plate 12 into the pump outlet 17, from where it knocks into the inner space of the tubular element 56, then into the throttling hole 14 and further into the bushing channel 16 and the outlet axial hole 18 of the housing.
    The pressure in the control chamber 10 is controlled by a servo valve 21, which includes a housing 57 movably mounted in the bore 58 of the cam element 3 and the spring-loaded spring
    452664
    59 relative to the element 60 installed in the cam element 3 and the side plate 12 and having an axial channel 61 for supplying pressure 5 to the end 19 of the servovalve, communicated with the channel 62 in the side plate 12, the channel 62 via channel 63 in the conical element 15 communicating with an outlet axial bore 18) 0 ca 1. A safety valve is integrated into the housing 57 of the servovalve, which includes a bolt 64 and a spring 65.
    The pressure to the end surface 20 of the servovalve is supplied through an arc 15 different channel 66, which is connected to the channel 44. In the cam element 3, channels 67, 68, 69 and 70 are made, while channel 67 is tubular, element 71 communicates with camera 10 of control , the channel 68 enters the bore 58 of the cam element 3, and the channels 67 and 70 are connected to an annular chamber 25. On the surface of the casing 57 of the servovalve in the exit zone
    25, channel 68 is provided with an annular discharge groove 72 and a tapered annular groove 73. Channels 68, 69 and 70 are displaced one relative to the other along the axis of the bore 58, and the entrance to
    30, channel 68 is plugged with plug 74. Pressure in chamber 54 is transmitted through throttle channel 75 to control chamber 10.
    The vane pump works as follows.
    When the wired shaft 6 rotates, the rotor element 2 associated with it rotates relative to the cam element 3, which causes
     About to periodically increasing and decreasing the volume of the working chambers 7. When the volume of the working chambers 7 increases, the working fluid from the annular chamber 25 through the channels 32, 33, 34, 35, 38, 39, 40
    5 and 41 enters these working chambers — a suction stroke occurs. When the volume of the working chambers 7 is reduced, the working fluid is displaced from them into the channels 42, 43, 44, 45 of the lid 13 and
    50 further along the channels 48 and 49 in the cam element 3 to the corresponding output channels 50, 51, 52, 53 in the side plate 12, from where it enters the chamber 54 in the side plate 12. From the gauge 54 of the measure 54 through the arcuate groove 55 the working fluid through the outlet 17 and the taller hole 14 is forced out into the axial hole 18 and further into the 1st pipeline. When the pump operates at a pressure below a predetermined level, the side plate 2 is pressurized in the control chamber 10 and the force of the spring II is pressed against the cam 3 and the rotor 2 elements, sealing the working chambers 7, which corresponds to the closed position of the servo valve 21. With increasing pressure servok lancer 21, having overcome having strengthened the springs 59 and the fluid pressure acting on the end of 1.9 of its body. 57 is shifted to the right, as shown in FIG. 15, which leads to the communication channels 68 and 69, in which the liquid from the control chamber 10 through the tubular element 71 flows through the channel 67 into the channel 68 and further. along the annular conical groove 73 into the channel 69, from where it is discharged into the annular chamber 25 having a low pressure, which leads to a pressure drop in the control chamber 10. The pressure drop in the control chamber 10 leads to the withdrawal of the plate I2 from the rotor 2 and cam 3 elements and the working chambers 7 to communicate with each other by transferring liquid from the pressure chambers to the suction. After moving the housing 57 of the servovalve 21 to the position shown in FIG. 15, it may be slightly shifted or modulated near this position in order to precisely control the flow of fluid being pumped into the system. So, if the fluid pressure in the system increases, there is an immediate decrease in flow through the throttling opening 14, this leads to the fact that the pressure difference acting on the opposite ends 19 and 20 of the servo valve 21 decreases, the latter entails a displacement of the body 57 servovalves to the left in the position shown in the -fig. 14. Such an offset of the servo valve results in a decrease in the discharge of fluid from the control chamber 10 and an increase in pressure therein. As a result of the pressure being applied in the control chamber 10, the side plate 12 is mixed to a position closer to the rotor 2 and cam 3 elements and an immediate increase in flow to the system occurs.
    When increasing the rate of heating of the fluid in the system flow
    the throttling orifice 14 will also increase, leading to an increase in the pressure differential in this orifice, while the pressure difference acting on the opposite ends 19 and 20 will also increase, and the housing 57 of the servo valve 21 will shift to the right, as shown in FIG. 15 in order to release pressure in the control chamber 10. The pressure drop in the control chamber 10 will cause the side plate 12 to move to the right with a large amount of fluid passing from the injection chambers to the suction.
    Further cycles are repeated.
    When the pressure in the system exceeds a predetermined level, a safety valve is triggered, which is built into the servo valve 21, while
    the shutter 64 overcoming the force of the spring 65. moves away from the saddle and moves the fluid from the channel 62 to the annular chamber 25, which will cause the side plate 12 to move to the right.
    Thus, the use of the invention allows to reduce the size of the pump and to reduce the volumetric flow of fluid into the hydraulic system at pumping rates exceeding a predetermined speed.
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    权利要求:
    Claims (3)
    [1]
    '(54) (5 7) 1. VAN PUMP for supplying fluid to a hydraulic system containing rotary and cam elements located in the housing with means for their relative rotation around the pump axis, the rotor element having radial 'grooves with cavities that can be contacted for relative rotation with the cam element and with the formation of working chambers of variable volume, alternately communicating with the inlet and outlet openings of the pump, means for regulating the volumetric flow rate of the pump, including Assumption perpendicular to the axis of rotation and mounted for axial movement in the control chamber, and preloaded by a spring to one side of the rotor and the cam elements of the side plate to isolate working chambers and messages among themselves, the means defining the throttle bore between the inlet port. the pump and the discharge pipe associated with the hydraulic system, the outlet, the pump and the discharge pipe using channels communicated with the end surfaces of the servo valve to relieve pressure in the chamber controlling the position of the side plate upon reaching a predetermined level of overpressure in the discharge pipe, characterized in that, in order to reduce dimensions and reduce the flow of fluid into the hydraulic system at discharge speeds exceeding a predetermined, means that determine the regulation my control throttling hole includes a conical element connected to the side plate and entering the throttling hole to control the cross section of the control throttling hole when moving the plate, and the conical element is installed with the possibility of reducing the hole cross section when removing the plate from the cam and rotor elements
    [2]
    2. Pump pop. ^ characterized in that the control throttling hole is made in the sleeve, mounted in the housing in front of the discharge pipe.
    [3]
    3. The pump according to paragraphs. 1 and 2, characterized in that one of the channels for supplying pressure from the discharge pipe to the end surface of the servo valve is made in a conical element.
    SU „„ 1245266
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    GB1179223A|1970-01-28|Improvements in or relating to Fluid Steering Systems.
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    CA1134202A|1982-10-26|Hydraulic pump
    同族专利:
    公开号 | 公开日
    BR8202587A|1983-04-19|
    ES8308396A1|1983-08-16|
    EP0065653A3|1983-01-26|
    DE3265194D1|1985-09-12|
    JPS639114B2|1988-02-25|
    CA1177327A|1984-11-06|
    US4420290A|1983-12-13|
    ES511977A0|1983-08-16|
    EP0065653B1|1985-08-07|
    JPS5825596A|1983-02-15|
    AU8307782A|1982-11-11|
    EP0065653A2|1982-12-01|
    AU547695B2|1985-10-31|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3207077A|1963-05-27|1965-09-21|Gen Motors Corp|Pump|
    US3415194A|1966-09-16|1968-12-10|Eaton Yale & Towne|Pump|
    US3679329A|1970-06-08|1972-07-25|Trw Inc|Flat side valve for a pump|
    US3671143A|1970-11-05|1972-06-20|Trw Inc|Flat side valve for pressure balanced power steering pump with improved aspirator action|
    US3728046A|1971-10-06|1973-04-17|Trw Inc|Power steering pump|
    US3822965A|1972-11-02|1974-07-09|Trw Inc|Pumps with servo-type actuation for cheek plate unloading|
    IT1026478B|1974-02-06|1978-09-20|Daimler Benz Ag|VANE CAPSULISM IN PARTICULAR VANE PUMP FOR LIQUIDS|
    US3930759A|1974-06-03|1976-01-06|Trw Inc.|Integral housing pump with servo controlled cheek plate|
    US4014630A|1974-06-03|1977-03-29|Trw Inc.|Power steering pump|
    GB1513996A|1976-11-15|1978-06-14|Kayaba Industry Co Ltd|Power-steering pump|JPH059313B2|1984-03-29|1993-02-04|Honda Motor Co Ltd|
    US5147183A|1991-03-11|1992-09-15|Ford Motor Company|Rotary vane pump having enhanced cold start priming|
    US5171131A|1991-05-14|1992-12-15|Vickers, Incorporated|Power transmission|
    JPH07124809A|1993-11-01|1995-05-16|Yunika Kk|Core drill provided with cutting chip discharge hole|
    US8191974B2|2006-05-05|2012-06-05|Ford Global Technologies, Llc|System and method to control hydraulic pump to provide steering and braking assist|
    US7556479B2|2006-08-15|2009-07-07|Ford Motor Company|Power steering pump relief system filter|
    CN102330673B|2011-07-19|2016-01-06|大连液压件有限公司|Pressure withstanding outflow type power-assisted steering pump|
    JP1546565S|2015-08-19|2016-03-28|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US06/261,645|US4420290A|1981-05-07|1981-05-07|Power steering pump|
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