US3645171A - Swash plate device - Google Patents

Swash plate device Download PDF

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Publication number
US3645171A
US3645171A US33715A US3645171DA US3645171A US 3645171 A US3645171 A US 3645171A US 33715 A US33715 A US 33715A US 3645171D A US3645171D A US 3645171DA US 3645171 A US3645171 A US 3645171A
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US
United States
Prior art keywords
groove
valve
cylinder block
pressure
swashplate
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US33715A
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English (en)
Inventor
Donald Patterson Mcleod
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dowty Technical Developments Ltd
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Dowty Technical Developments Ltd
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Publication date
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2035—Cylinder barrels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate

Definitions

  • a circular seal is f Cl provided in the valve means to engage a flat surface at the end [58] Field of Search ..91/485489 f the cylinder block whereby to f a seal against escape f liquid from the valve into the aperture
  • a circular groove is [56] References cued formed in the valve or the cylinder block in between the seal UNITED STATES PATENTS and the ports in the valve means and is connected to the lowpressure port whereby liquid at low pressure In the low-pres- 2,543,624 2/1951 Gabriel ..9l/485 ure port provides a low-pressure one within the groove to 2,284J 1 1 1942 prevent centrifuging of air from the aperture over the surface 1 327,740 8/1922 Johnsonm of the seal and into the swashplate pump or motor.
  • the present invention concerns a swashplate device com prising a rotary cylinder block having a plurality of cylinders either parallel to or inclined to the rotation axis, a swashplate adjacent to one end of the cylinder block, pistons in the cylinders reciprocable during block rotation by engagement either directly or indirectly through slippers with the swashplate, a valve means having a flat valve surface at the end of the cylinder block remote from the swashplate to engage a flat block surface at that end of the block, high and low-pressure ports in said valve surface cooperating with cylinder ports opening into the flat block surface, an aperture in the valve means to accommodate a drive
  • the function of the seal during operation is to prevent leakage of liquid into the aperture from the valve and block surfaces. Whilst the seal is effective to prevent such leakage it is possible in practice for the rotary action of the cylinder block to generate a suction zone around the seal which causes air to be drawn into the swashplate device from the aperture. The presence of such air in the hydraulic working liquid can adversely effect the operation of the swashplate device and any other hydraulic device to which it is connected.
  • the object of the present invention is to provide a swashplate device as described which will reduce the possibility of entry of air into the swashplate device over the said seal.
  • the swashplate device described above includes a circular groove formed between the seal and the ports in at least one of the flat surfaces and a connection within the valve means from said groove to the said low-pressure port.
  • Centrifugal means driven by the said cylinder block may be provided to raise the pressure of liquid in the inlet port and in the said circular groove.
  • an inlet groove may at least partially surround the valve surface to feed liquid to the inlet port, and impeller means driven by the cylinder block may rotate over the groove to urge liquid into the inlet port to raise pressure in both the inlet port and the said circular groove.
  • FIG 1 is a cross section through the pump
  • FIG. 2 is a composite elevation and cross section showing in part an elevation of the pump and the part sections on the lines IIA, HE and lIC of FIG. 1,
  • FIG. 3 is an elevation of the end surface of the cylinder block containing the cylinder ports
  • FIG. 4 is an elevation of the structural member showing in particular the flat valve surface
  • FIG. 5 is a developed cross section taken on the circular line V-V in FIG. 4.
  • the structural member of the pump is an aluminum casting and it comprises three integrally formed parts indicated as the valve 1, the casing 2 and the servo cylinder 3.
  • the valve 1 has a flat valve surface 4 which contains a highpressure delivery port 5 of conventional kidney shape connected to a delivery passage 6 which terminates as a screwthreaded connection (not shown) on the outside of the valve 1.
  • a plurality of mounting lugs 8 are provided around the periphery of the valve 1 for securing the pump in its operative position, the pump being correctly located by a cylindrical boss 9 adapted to fit in a corresponding hole on a driving motor or engine.
  • the hollow casing 2 is closed at the end remote from the valve 1 by means of a cover 11 of pressed sheet metal secured in a large circular recess 12 by means of a circlip 13.
  • a rubber seal 14 ensures a liquidtight connection between the casing 2 and the cover ll.
  • a cylinder block 15 of cast iron is arranged for rotation about the axis AA.
  • the cylinder block 15 includes a flat surface 16 hearing against the valve surface 4.
  • Each cylinder 17 includes a cylinder port 18 opening into the surface 16, the ports 18 being arranged to cooperate with the main pressure port 5 during rotation of the cylinder block 15.
  • the cylinder block At a position remote from the surface 16, the cylinder block includes an integrally formed skirt 19 around which is formed a cylindrical bearing surface 21 which effectively surrounds the cylinder block.
  • passages 24 are formed within the cylinder block one between each adjacent pair of cylinders. Each passage opens from the surface of the block remote from the valve surface 4 between the radially directed vanes 25 formed on the cylinder block 15 within the casing 2.
  • a groove 26 is formed in the valve around the valve surface 4, one end of this groove con necting to the low-pressure arcuate inlet port 30 formed in the valve surface 4.
  • the casing 2 remote from the valve includes a pair of integrally formed bosses 27 bored transversely to produce a pair of spaced apertures 28. Between the bosses 27 a swash plate 29 is mounted on a shaft 31 by means of a cylindrical bore 32 extending through the swashplate.
  • the swashplate includes a flat swash surface 33 facing the cylinder block 15.
  • a piston 34 and a compression spring 35 are located, the spring acting to urge its piston outwardly from the cylinder.
  • each piston 34 is formed with a spherical socket 36 into which a ball 37 is secured.
  • the ball 37 is integrally connected to a slipper 38 engaging the swash surface 33.
  • a hydraulic passage 39 within each piston 34 gives access to the socket 36 for lubrication and also connects to passage 41 in the ball which feeds at pressure through a restrictor 42 to a recess 43 in the slipper surface in contact with the swash surface 33.
  • the recess is conventionally arranged so that hydraulic pressure acting in the recess will almost completely balance the hydraulic load acting on the piston.
  • a retaining plate 44 includes five apertures 45 engaged one on each slipper 38. Centrally the retaining plate 44 reacts against a ball 46 carried by a pad 47 slidably mounted in a central bore in the cylinder block, a compression spring 49 reacting between the block 15 and the pad 47 and serving simultaneously to urge the block against the valve surface 4 and to urge the retaining plate 44 to maintain the slippers in contact with the swash surface.
  • a splined aperture 51 is provided centrally within the cylinder block to open into a comparatively large aperture 52 extending through the valve 1.
  • a drive shaft (not shown) may be inserted through the aperture 52 to engage the splined aperture to drive the cylinder block.
  • a sea] 53 may engage between the valve and the cylinder block in the manner disclosed in our copending application No. 32109/68, U.S. Ser. No. 838607. To prevent hydraulic leakage between the bore 48 and the aperture 52 the bore 48 is sealingly closed by means of a plug 54.
  • the servo cylinder 3 has a servo piston 55 slidably mounted therein one end being connected by means of a pivot pin 56 to a link 57 which in turn is connected by by a pivot pin 58 to a lever 59 extending from the swashplate 29.
  • a servo piston 55 slidably mounted therein one end being connected by means of a pivot pin 56 to a link 57 which in turn is connected by by a pivot pin 58 to a lever 59 extending from the swashplate 29.
  • the swash plate is shown at a position of maximum inclination and the servo piston 55 is in a corresponding position.
  • the small diameter bore 61 within the piston 55 receives one end of a rod 62 which extends from the end of the servo cylinder 3 adjacent to the valve 1.
  • the end of the cylinder 3 adjacent to the valve 1 has a plug 63 inserted therein being retained in position by a cap 64 and circlip 65.
  • a central bore 66 through the plug 63 locates the rod 62 for sliding movement, a suitable seal on the rod 62 preventing leakage of liquid.
  • the end of the cylinder 3 adjacent to the valve 1 is formed in an extension 67 from the valve 1 but integral therewith.
  • a rotary controlled spindle 68 is suitably mounted in bearings in the extension 67, the spindle 68 carrying a lever 69 which extends into a chamber 71 within the plug 63 to engage in a recess 72 in the end of the rod 62 such that rotation of the spindle 68 will cause endwise movement of the rod 62.
  • a passage 73 extends in the valve 1 from the delivery passage 6 to intersect the cylinder bore 3.
  • the plug 63 includes a peripheral groove 74 from which a small hole is bored to form the restrictor 75 which connects through passage 76 in plug 63 to the working space 77 between the plug 63 and the piston 55.
  • the end of the rod 62 includes a counter bore 78 from which a pair of radially directed control ports 79 open into the working space 77.
  • the rod 62 is located for limited motion within the piston bore 61 by means of a transverse pin 81 loosely engaging a transverse hole in the rod 62. The movement permitted for the rod 62 relative to the piston will vary the opening of the port 79 over the edge of the bore 61 into the working space 77.
  • the ports 79 and the cooperating edge of the bore 61 form a variable restrictor adjustable by movement of rod 62.
  • the end of the servo bore 3 opposite to the valve 1 is formed as a screw-threaded inlet connection 82 and liquid entering connection 82 may pass into the casing through a cutaway portion 83 through which the lever 59 extends to the link 57.
  • the liquid entering the pump thereby flows firstly over the swashplate 29 before entering the passages 24.
  • FIG. 3 of the accompanying drawings shows the flat end surface 16 of the cylinder block in elevation.
  • the splined central hole 51 is surrounded by the flat block surface 16 which contains the cylinder ports 18, the fiat surface 16 being interrupted by a coaxial circular groove 88 radially located in between the aperture 51 and the cylinder ports 18.
  • the surface 16 is surrounded by an annular fiat surface 89 parallel to but slightly lower than the flat surface 16.
  • the annular surface 89 includes a plurality of shallow recesses 91 which define between them the axially extending vanes 92 for propelling liquid.
  • the annular surface 89 fits over the groove 26 (FIG. 4) formed around the flat valve surface 4.
  • the groove 26 is closed by a wall 93 which extends from the valve surface 4 across the groove 26 and connects to a land 94 to reduce the width of the groove 26 at the end portion thereof adjacent the wall.
  • the groove 26 at its narrowed portion connects to one end of the low-pressure inlet port 30.
  • the groove 26 starts at a shallow depth at the wall 93 and gradually increases in depth around the valve surface 4, maximum depth of the groove being obtained at the position of entry to the inlet port 30.
  • the narrowed part of groove 26 adjacent to the land 94 increases more greatly in depth than the remainder of the groove 26.
  • the seal 53 is seated in an annular recess 95 formed in the center of the valve 1 so that the seal 53 can engage the fiat portion of the block surface 16 between the central aperture 51 and groove 88.
  • the outer edge of the recess 95 is chamfered at 96 so that a portion of the recess 95 radially outwards of the seal 53 makes connection with the annular groove 88in the cylinder block surface 16.
  • a shallow channel 97 in the valve surface 4 connects from the recess 95 into the inlet port 30 whereby liquid at low pressure built up in the inlet port 30 may enter the recess 95 around the seal 53 to retain a low backing pressure at the seal 53 to help to prevent induction of air from the aperture 52 across the seal and into the pump.
  • the cylinder block is rotatably driven by a drive shaft inserted through the aperture 52 into the cylinder block and rotation of the cylinder block causes reciprocation of the pistons in the cylinders by virtue of the fact that the slippers are held by springs 35 and 49 against the swashplate surface.
  • liquid fed from the inlet connection 82 flows around the swashplate and into the passages 24 there being induced by centrifugal pumping action to flow to the groove 26.
  • the rotation of the cylinder block surface 89 over the groove 26 will by virtue of the vanes 92 induce flow of liquid around the groove 26 and into the inlet port 30.
  • vanes 92 acting on the liquid in the groove 26 will do so by virtue of the viscosity of liquid and it will be appreciated that the actual velocity of liquid flowing around the groove 26 will be considerably lower than the velocity of the cylinder block over the groove even when the pistons have their maximum stroke.
  • the total pressure buildup at the inlet port 30 therefore results from the centrifuging action of the passages 24 and vanes 25 of the cylinder block and further from the impelling action of the vanes 92 on liquid in groove 26 by virtue of the viscosity of the liquid.
  • the pressure of liquid in the inlet port 30 whilst still comparatively low will nevertheless provide an adequate boost pressure to assist the entry of liquid into the cylinders 17 during outward movement of the pistons 34.
  • the channel 97 which connects the inlet port 30 to the recess 95 supplies liquid at the pressure in the inlet port 30 to the recess 95 and will increase the pressure in the recess to a small extent and prevent the tendency for air to be induced to enter into the pump between the seal 53 and the cylinder block surface 16.
  • Movement of the rod 62 will adjust the variable restrictor formed by port 79 to control the pressure developed within the working space 77 by virtue of the series connection of the fixed restrictor 75 with the variable restrictor between the high pressure connection 76 and the low pressure interiorly of the casing 2.
  • the pressure within the working space 77 urges the swash plate towards its maximum inclination while the torque developed on the swashplate itself urges it to the minimum inclination.
  • Simple adjustment of the spindle 68 will therefore control pressure in the working space 77 to cause the swashplate to take up an angular position which is in proportion to the angular setting of the spindle 68.
  • the passage 73 is formed by drilling from the exterior of the casing and in use the plug closes the outer end of the passage 73.
  • the passage 73 connects high pressure only to the groove 74 of plug 63.
  • the grade of aluminum alloy selected for the structural member forming the casing, the valve, the bosses and the servo cylinder is chosen to have the necessary strength to cater for the intended operating pressures of the pump.
  • the design of the ports 5 and 30 in the valve in combination with the cross-sectional areas of the pistons is such that the cylinder block in operation presses only very lightly against the valve surface 4, the principle force holding the block on this surface being that provided by the springs 35 and 49.
  • a swashplate device comprising a rotary cylinder block having a plurality of cylinders either parallel to or inclined to the rotation axis, a swashplate adjacent to one end of the cylinder block, pistons in the cylinders reciprocable during block rotation by engagement either directly or indirectly through slippers with the swashplate, a valve means having a flat valve surface at the end of the cylinder block remote from the swashplate to engage a flat block surface at that end of the block, high and low-pressure ports in the said valve surface cooperating with cylinder ports opening into the said block surface, boost pump means to supply liquid at low pressure to said low-pressure port, an aperture in the valve to accommodate a drive shaft for the cylinder block, a seal acting between the valve means and the cylinder block around the aperture radially inwards of said ports, a circular groove formed between the seal and the ports in at least one of the flat surfaces, and a connection within the valve means from the said groove to the said low-pressure port.
  • a swashplate device as claimed in claim 1 including centrifugal means driven by said cylinder block.
  • a swashplate device as claimed in claim 1 including an inlet groove at least partially around the valve surface and adapted to feed liquid to the inlet port, and impeller means driven by the block rotating over the groove to urge liquid into the inlet port and to raise liquid pressure in the inlet port and the said circular groove.
  • a swashplate device as claimed in claim 1 including a recess in the valve opening into the valve surface and containing the seal, a circular space being provided in the recess around the seal to form a circular groove in the valve surface from which the said connecting groove extends to the inlet port.
  • a swashplate device as claimed in claim 1 including an inlet groove at least partially around the valve surface adapted to feed liquid to the inlet port, an impeller device driven by the block rotating over the groove to urge liquid into the inlet port to, raise pressure in both inlet port and said circular port, and centrifugal means driven by said cylinder block to raise the pressure of liquid in said inlet groove whereby the pressure of liquid in the inlet port and the circular groove is raised by pumping action at both the inlet groove and the centrifugal means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
US33715A 1970-03-14 1970-05-01 Swash plate device Expired - Lifetime US3645171A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB1235670 1970-03-14

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US3645171A true US3645171A (en) 1972-02-29

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US33715A Expired - Lifetime US3645171A (en) 1970-03-14 1970-05-01 Swash plate device

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US (1) US3645171A (enrdf_load_stackoverflow)
JP (1) JPS5125921B1 (enrdf_load_stackoverflow)
GB (1) GB1304102A (enrdf_load_stackoverflow)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5341913U (enrdf_load_stackoverflow) * 1976-09-14 1978-04-11

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1427740A (en) * 1921-11-01 1922-08-29 Robert H Johnson Pump
US2284111A (en) * 1939-06-28 1942-05-26 Vickers Inc Hydraulic pump or motor
US2543624A (en) * 1946-07-24 1951-02-27 Acme Ind Hydraulics Inc Pump
US2847938A (en) * 1955-12-01 1958-08-19 John T Gondek Hydraulic pump
FR1224344A (fr) * 1958-03-05 1960-06-23 Dba Sa Perfectionnements aux pompes à barillet
US3036434A (en) * 1960-12-29 1962-05-29 Massey Ferguson Inc Thrust bearings for hydrostatic transmissions
US3170297A (en) * 1963-09-30 1965-02-23 Bendix Corp Hydrostatic thrust bearing device

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1427740A (en) * 1921-11-01 1922-08-29 Robert H Johnson Pump
US2284111A (en) * 1939-06-28 1942-05-26 Vickers Inc Hydraulic pump or motor
US2543624A (en) * 1946-07-24 1951-02-27 Acme Ind Hydraulics Inc Pump
US2847938A (en) * 1955-12-01 1958-08-19 John T Gondek Hydraulic pump
FR1224344A (fr) * 1958-03-05 1960-06-23 Dba Sa Perfectionnements aux pompes à barillet
US3036434A (en) * 1960-12-29 1962-05-29 Massey Ferguson Inc Thrust bearings for hydrostatic transmissions
US3170297A (en) * 1963-09-30 1965-02-23 Bendix Corp Hydrostatic thrust bearing device

Also Published As

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DE2112077B2 (de) 1975-03-27
JPS5125921B1 (enrdf_load_stackoverflow) 1976-08-03
DE2112077A1 (de) 1971-10-07
GB1304102A (enrdf_load_stackoverflow) 1973-01-24

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